Compressor

Abstract

This compressor is provided with a housing (6) and a compression mechanism (14). A discharge section (63) is formed in the housing (6). The compression mechanism (14) is provided with a second boss (37b) in addition to a compression chamber (12). A discharge engagement hole (37d) is formed in the second boss (37b). In the compressor, as the second boss (37b) rotates, the phase position of the discharge part (63) and the discharge connection hole (37d) changes, and the discharge side flow resistance changes. Furthermore, the discharge section (63) and the discharge connection hole (37d) are in a phase at which the discharge-side flow resistance increases as the flow rate of the fluid discharged from the compression chamber (12) to the discharge chamber (8) approaches to the maximum.

Description

Technical Field

[0001] This invention relates to compressors. Background Technology

[0002] Patent Document 1 discloses a conventional compressor. This compressor includes a housing and a compression mechanism. The housing has a discharge section for discharging fluid to the outside, an intake section for drawing fluid from the outside, and an intake chamber communicating with the intake section.

[0003] The compression mechanism is housed within the housing. More specifically, the compression mechanism has a driving scroll and a driven scroll. The driving scroll is rotatable about a rotation axis. The driving scroll has a driving end plate and a driving scroll body integral with the driving end plate and projecting in a scroll shape toward the driven scroll.

[0004] The driven scroll member is opposite to the driving scroll member. The driven scroll member rotates around a driven axis while being eccentric relative to the driving scroll member, via the driving scroll member and the driven mechanism. Furthermore, a compression chamber is formed between the driven scroll member and the driving scroll member. The driven scroll member has a driven end plate and a driven scroll body integral with the driven end plate and protruding in a scroll shape toward the driving scroll member. Moreover, a discharge chamber is formed in the driven scroll member. The discharge chamber communicates with the compression chamber and with the discharge section.

[0005] In this compressor, fluid is drawn into the suction chamber from outside the housing through the suction section. Furthermore, in this compression mechanism, the volume of the compression chamber changes with the rotation of the driving scroll member and the driven scroll member. Thus, in this compressor, fluid is drawn from the suction chamber into the compression chamber, and the fluid is compressed within the compression chamber as its volume decreases. The compressed fluid is then discharged from the compression chamber to the discharge chamber, and from the discharge section to the outside of the housing.

[0006] Existing technical documents

[0007] Patent documents

[0008] Patent Document 1: Japanese Patent Application Publication No. 2002-310073 Summary of the Invention

[0009] The problem that the invention aims to solve

[0010] In such compressors, it is required to reduce noise caused by discharge and intake pulsations during operation. Therefore, in the aforementioned conventional compressors, the reduction of discharge pulsations is sought by increasing the volume of the discharge chamber to enhance its noise reduction effect. However, in this case, the increased volume of the discharge chamber necessitates a larger compression mechanism. Consequently, the casing, and consequently the compressor, becomes larger. The same applies when increasing the volume of the intake chamber to reduce intake pulsations; the larger casing leads to a larger compressor.

[0011] The present invention was made in view of the above-mentioned conventional realities, and aims to provide a compressor that can suppress large size while achieving high quietness.

[0012] Technical solutions for solving the problem

[0013] The first compressor of the present invention is characterized by comprising:

[0014] The outer casing has a discharge section for discharging fluid to the outside; and

[0015] A compression mechanism is disposed within the housing.

[0016] The compression mechanism includes a compression chamber that compresses the fluid while reducing its volume, and a rotating shaft supported by the housing that is rotatable about a rotation axis.

[0017] The outer casing or the compression mechanism has a discharge chamber that communicates with the compression chamber and allows the fluid compressed in the compression chamber to be discharged.

[0018] A discharge connection portion is formed in the rotating shaft portion to allow fluid discharged into the discharge chamber to flow into the discharge portion.

[0019] As the rotating shaft rotates, the phase between the discharge section and the discharge connection section changes, thereby changing the flow resistance of the fluid flowing from the discharge connection section to the discharge section, i.e., the discharge-side flow resistance.

[0020] The discharge section and the discharge connection section are in a phase in which the flow resistance on the discharge side increases as the flow rate of the fluid discharged from the compression chamber to the discharge chamber approaches its maximum.

[0021] In the first compressor of the present invention, a discharge connection portion is formed on the rotating shaft portion of the compression mechanism, which allows fluid discharged to the discharge chamber to flow to the discharge portion. Thus, in this compressor, fluid compressed in the compression chamber and discharged to the discharge chamber reaches the discharge portion from the discharge connection portion. Furthermore, in this compressor, the phase between the discharge portion and the discharge connection portion changes with the rotation of the rotating shaft portion. Moreover, the change in phase between the discharge portion and the discharge connection portion causes a change in the discharge-side flow resistance.

[0022] Here, in this compressor, pulsations are generated due to the discharge-side flow resistance, and the magnitude of these pulsations changes as the discharge-side flow resistance changes. Furthermore, in this compressor, the discharge section and the discharge connection section are in a phase where the discharge-side flow resistance increases as the flow rate of fluid discharged from the compression chamber approaches its maximum. Therefore, in this compressor, the pulsations generated due to the discharge-side flow resistance function to counteract the discharge pulsations generated when fluid is discharged from the compression chamber to the discharge chamber. As a result, the compressor can reduce discharge pulsations.

[0023] In this way, the discharge chamber does not need to be made too large when reducing discharge pulsation in the compressor, and the compression mechanism and housing are not easily enlarged.

[0024] Therefore, the first compressor of the present invention can achieve high quietness while suppressing large size.

[0025] In the first compressor of the present invention, preferably, the discharge section and the discharge connection section are connected radially in the outer casing. In this case, the outer casing, and thus the compressor as a whole, can be miniaturized in the direction of the rotation axis of the rotating shaft section.

[0026] Furthermore, in the first compressor of the present invention, it is preferable that the discharge section and the discharge connection section are connected in the direction of the rotation axis. In this case, the housing, and thus the compressor as a whole, can be miniaturized in the radial direction of the housing.

[0027] Alternatively, in this case, the discharge portion may be formed on the housing while being eccentrically positioned relative to the rotation axis. Furthermore, it is preferable that the discharge connection portion is formed on the rotation axis portion while being eccentrically positioned relative to the rotation axis. This allows for a suitable change in the phase between the discharge portion and the discharge connection portion.

[0028] In the first compressor of the present invention, preferably, when the flow rate of the fluid discharged from the compression chamber to the discharge chamber is minimal, the discharge section and the discharge connection section are positioned to minimize the flow resistance on the discharge side.

[0029] Furthermore, in the first compressor of the present invention, preferably, when the flow rate of the fluid discharged from the compression chamber to the discharge chamber is at its maximum, the discharge section and the discharge connection section are in a phase that maximizes the flow resistance on the discharge side.

[0030] In these cases, the pulsations caused by the flow resistance on the discharge side function in a way that more appropriately counteracts the discharge pulsations, thus enabling a more appropriate reduction in discharge pulsations. Furthermore, the phrase "the flow rate of fluid discharged from the compression chamber to the discharge chamber is minimal" includes not only the case where a small amount of fluid is discharged from the compression chamber to the discharge chamber, but also the case where the flow rate of fluid discharged from the compression chamber to the discharge chamber is zero.

[0031] Alternatively, the compression mechanism may be equipped with a discharge valve that allows fluid to flow from the compression chamber to the discharge chamber while preventing fluid from flowing from the discharge chamber to the compression chamber. Furthermore, preferably, the discharge connection is located downstream of the discharge valve in the direction of fluid flow.

[0032] In this case, it is possible to appropriately prevent the generation of pulsations caused by fluid flowing from the discharge chamber to the compression chamber. In addition, the flow of fluid from the discharge connection to the discharge passage can assist in the opening of the discharge valve.

[0033] The second compressor of the present invention is characterized by comprising:

[0034] The outer casing has 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

[0035] A compression mechanism is disposed within the housing.

[0036] The compression mechanism includes a compression chamber that compresses the fluid while reducing its volume, and a supported portion supported by the housing that is rotatable about a rotation axis.

[0037] The supported portion has an intake connection portion that allows fluid in the intake passage to flow into the compression chamber.

[0038] As the supported portion rotates, the phase between the suction passage and the suction connector changes, thereby changing the flow resistance of the fluid flowing from the suction passage to the suction connector, i.e., the suction-side flow resistance.

[0039] The suction passage and the suction connection portion are in a phase where the flow resistance on the suction side increases as the volume of the compression chamber decreases relative to its maximum.

[0040] In the second compressor of the present invention, a suction connection is formed in the supported portion of the compression mechanism, which allows fluid in the suction passage to flow into the compression chamber. Thus, in this compressor, fluid drawn into the suction chamber from the suction connection port is drawn into the compression chamber from the suction passage through the suction connection. Furthermore, since the suction connection is formed in the supported portion, the phase between the suction connection and the suction passage changes with the rotation of the supported portion. Moreover, the change in phase between the suction passage and the suction connection causes a change in the suction-side flow resistance.

[0041] Here, in this compressor, pulsations are generated due to the flow resistance of the fluid flowing from the suction passage to the suction connection, i.e., the suction-side flow resistance. The magnitude of these pulsations varies as the suction-side flow resistance changes. Furthermore, in this compressor, the suction passage and the suction connection are in a phase where the suction-side flow resistance increases as the volume of the compression chamber decreases to its maximum. Therefore, in this compressor, the pulsations generated by the suction-side flow resistance function to counteract the suction pulsations generated when fluid is drawn into the compression chamber. As a result, the compressor can reduce suction pulsations.

[0042] In this way, the suction chamber does not need to be made too large when reducing suction pulsation in the compressor, and the outer casing is not easily enlarged.

[0043] Therefore, the second compressor of the present invention can achieve high quietness while suppressing large size.

[0044] In the second compressor of the present invention, preferably, the suction passage and the suction connection are connected radially in the housing. In this case, the housing, and thus the compressor as a whole, can be miniaturized in the direction of the rotation axis of the rotating shaft.

[0045] In the second compressor of the present invention, preferably, when the volume of the compression chamber is at its maximum, the suction passage and the suction connection portion are positioned at a phase that minimizes the flow resistance on the suction side.

[0046] Furthermore, in the second compressor of the present invention, preferably, when the flow rate of the fluid drawn into the compression chamber is at its maximum, the suction passage and the suction connection portion are positioned at a phase that maximizes the flow resistance on the suction side.

[0047] In these cases, the pulsations caused by the inhalation-side flow resistance function in a way that more appropriately counteracts the inhalation pulsations, thus enabling a more appropriate reduction in inhalation pulsations.

[0048] In the first compressor or the second compressor of the present invention, the compression mechanism may include: a driving scroll member capable of rotating about a rotation axis; and a driven scroll member opposite to the driving scroll member, which rotates about a driven axis via the driving scroll member and the driven mechanism while being eccentric relative to the driving scroll member, thereby forming a compression chamber between the driven scroll member and the driving scroll member. Alternatively, the driving scroll member may have a driving end plate and a driving scroll body integral with the driving end plate and protruding in a scroll shape toward the driven scroll member. Preferably, the driven scroll member has a driven end plate and a driven scroll body integral with the driven end plate and protruding in a scroll shape toward the driving scroll member.

[0049] In this case, the configuration of the compression mechanism can be simplified.

[0050] The third compressor of the present invention is characterized by comprising:

[0051] The outer casing has a suction chamber and a suction section for drawing in fluid from the outside;

[0052] A drive shaft, disposed within the suction chamber, is rotatable about a rotational axis; and

[0053] A compression mechanism, disposed within the housing, is connected to the drive shaft.

[0054] The drive shaft has an intake connection portion that communicates with the intake section in the direction of the rotation axis and allows fluid to flow from the intake section to the intake chamber.

[0055] The compression mechanism includes a compression chamber that compresses the fluid while reducing its volume, and an intake port that draws the fluid from the intake chamber into the compression chamber.

[0056] As the drive shaft rotates, the phase between the suction section and the suction connection section changes, thereby changing the flow resistance of the fluid flowing from the suction section to the suction connection section, i.e., the suction-side flow resistance.

[0057] The suction section and the suction connection section are in a phase where the flow resistance on the suction side increases as the volume of the compression chamber decreases relative to its maximum.

[0058] The third compressor, like the second compressor, can also reduce suction pulsation. Therefore, in this compressor, it is not necessary to make the suction chamber too large when reducing suction pulsation, and the compression mechanism and casing are not easily enlarged.

[0059] Therefore, the third compressor of the present invention can achieve high quietness while suppressing large size.

[0060] In the third compressor, the suction section may be formed on the housing while being eccentrically positioned relative to the rotation axis. Furthermore, preferably, the suction connection section is formed on the drive shaft while being eccentrically positioned relative to the rotation axis. In this case, the phase of the suction section and the suction connection section can be appropriately varied.

[0061] In the third compressor, preferably, when the volume of the compression chamber is at its maximum, the suction section and the suction connection section are positioned at a phase that minimizes the flow resistance on the suction side.

[0062] Furthermore, in the third compressor, preferably, when the flow rate of the fluid drawn into the compression chamber is at its maximum, the suction section and the suction connection section are positioned at the phase where the flow resistance on the suction side is at its maximum.

[0063] In these cases, the pulsations caused by the inhalation-side flow resistance function in a way that more appropriately counteracts the inhalation pulsations, thus enabling a more appropriate reduction in inhalation pulsations.

[0064] Invention Effects

[0065] The first compressor of the present invention can achieve high quietness while suppressing large size. Furthermore, the second compressor of the present invention can achieve high quietness while suppressing large size. Furthermore, the third compressor of the present invention can achieve high quietness while suppressing large size. Attached Figure Description

[0066] Figure 1 This is a cross-sectional view of the compressor in Example 1.

[0067] Figure 2 The compressor relating to Embodiment 1 is shown in an enlarged cross-sectional view of its main parts, including the first support, the suction passage, the first insertion hole, and the suction connection.

[0068] Figure 3 The compressor relating to Embodiment 1 is shown in an enlarged cross-sectional view of the main parts, including the discharge connection, the second insertion hole, and the discharge passage.

[0069] Figure 4 The compressor of Embodiment 1 is illustrated by a graph showing the relationship between the changes in the rotational phase of the first and second scroll members and the changes in the volume of the compression chamber.

[0070] Figure 5 The compressor of Embodiment 1 is shown in a graph illustrating the relationship between the changes in the rotational phase of the first and second scroll members and the changes in pressure within the compression chamber.

[0071] Figure 6 The compressor relating to Embodiment 1 is shown when the rotational phases of the first and second scroll members are phase X1. Figure 1 A sectional view of section AA.

[0072] Figure 7 The compressor relating to Embodiment 1 is shown when the rotational phases of the first and second scroll members are phase X1. Figure 1 Enlarged sectional view of the main part of the BB section.

[0073] Figure 8 The compressor relating to Embodiment 1 is shown when the rotational phase of the first scroll member and the second scroll member is phase X2. Figure 1 A sectional view of section AA.

[0074] Figure 9 The compressor relating to Embodiment 1 is shown when the rotational phase of the first scroll member and the second scroll member is phase X2. Figure 1 Enlarged sectional view of the main part of the BB section.

[0075] Figure 10 The compressor relating to Embodiment 1 is shown when the rotational phase of the first scroll member and the second scroll member is phase X3. Figure 1 A sectional view of section AA.

[0076] Figure 11 The compressor relating to Embodiment 1 is shown when the rotational phase of the first scroll member and the second scroll member is phase X3. Figure 1 Enlarged sectional view of the main part of the BB section.

[0077] Figure 12 The compressor of Embodiment 1 is shown in a graph illustrating the waveform of the suction pulsation during operation and the waveform of the first elimination of pulsation.

[0078] Figure 13 The compressor relating to Embodiment 1 is shown when the rotational phases of the first and second scroll members are phase X4. Figure 1 A sectional view of section AA.

[0079] Figure 14 The compressor relating to Embodiment 1 is shown when the rotational phases of the first and second scroll members are phase X4. Figure 1 Enlarged sectional view of the main part of the CC section.

[0080] Figure 15 The compressor relating to Embodiment 1 is shown when the rotational phase of the first scroll member and the second scroll member is phase X5. Figure 1 A sectional view of section AA.

[0081] Figure 16 The compressor relating to Embodiment 1 is shown when the rotational phase of the first scroll member and the second scroll member is phase X5. Figure 1 Enlarged sectional view of the main part of the CC section.

[0082] Figure 17 The compressor of Embodiment 1 is shown in a graph illustrating the waveform of discharge pulsation during operation and the waveform of the second pulsation elimination.

[0083] Figure 18 This is a cross-sectional view of the compressor in Example 2.

[0084] Figure 19 (A) to (D) relate to the compressor of Embodiment 2, and are shown from Figure 18 A schematic diagram showing the phase change of the discharge section and discharge connector when viewed from the D1 direction, accompanied by the rotation of the drive vortex member. Figure 19 (A) shows the phase of the discharge section and the discharge connection section when the rotation angle of the drive vortex is zero degrees. Figure 19 (B) shows from Figure 19 The phase of the discharge section and the discharge connection section when the state shown in (A) is such that the drive vortex has rotated about 90°. Figure 19 (C) shows from Figure 19 The phase of the discharge section and the discharge connection section when the drive vortex component has rotated approximately 90°, as shown in (B). Figure 19 (D) shows from Figure 19 The phase of the discharge section and the discharge connection section when the drive vortex component has rotated approximately 90°, as shown in (C).

[0085] Figure 20 This is an enlarged cross-sectional view of the main part of the compressor in Example 3.

[0086] Figure 21 This is a cross-sectional view of the compressor in Example 4.

[0087] Figure 22 This is an enlarged cross-sectional view of the main part of the compressor in Example 5. Detailed Implementation

[0088] Hereinafter, embodiments 1 to 5, which embody the present invention, will be described with reference to the accompanying drawings. Specifically, the compressors in embodiments 1 to 3 are dual-rotary scroll-type electric compressors. Specifically, the compressors in embodiments 4 and 5 are scroll-type electric compressors. These compressors are mounted in vehicles (not shown) and constitute the vehicle's air conditioning system.

[0089] Example 1

[0090] like Figure 1 As shown, the compressor of Embodiment 1 includes a housing 6, an electric motor 10, and a compression mechanism 14.

[0091] In this embodiment, by Figure 1 The solid arrow shown indicates the compressor's forward and backward direction. Furthermore, in Figure 2 Later, with Figure 1 The compressor's front-to-back direction is shown accordingly. However, the front-to-back direction is only an example for illustrative purposes; the compressor can adjust its orientation appropriately depending on the vehicle it is mounted on.

[0092] like Figure 1 As shown, the outer casing 6 consists of an outer casing body 60 and an outer casing cover 62. These outer casing bodies 60 and outer casing covers 62 are made of aluminum alloy.

[0093] The outer casing 60 is a bottomed cylindrical component having an outer peripheral wall 60a and a rear wall 60b. The outer peripheral wall 60a is formed into a cylinder centered on the rotation axis O1 of the rotation shaft. The rotation axis O1 is parallel to the front-rear direction.

[0094] Additionally, a suction port 68 is formed on the outer peripheral wall 60a. The suction port 68 extends radially along the outer casing body 60. The suction port 68 is connected to the evaporator (not shown) via a pipe (not shown).

[0095] The rear wall 60b is located at the rear end of the outer casing body 60. The rear wall 60b is orthogonal to the rotation axis O1 and extends in a generally circular flat plate shape. The outer periphery of the rear wall 60b is connected to the rear end of the outer peripheral wall 60a. In addition, the aforementioned suction port 68 may also be formed on the rear wall 60b.

[0096] 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. A suction passage 15 and a pin hole 4 are formed in the first support portion 64.

[0097] The suction passage 15 is composed of a passage body 15a, a first aperture 15b, and a second aperture 15c. The passage body 15a extends within the first support portion 64 in the direction of the rotation axis O1. Furthermore, the passage body 15a opens at the rear end of the first support portion 64, i.e., 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 way, the first support portion 64 is formed into a generally cylindrical shape centered on the rotation axis O1.

[0098] In addition, a sealing member 150 is provided at the opening of the passage body 15a into the rear wall 60b. As a result, the passage body 15a is not in communication with the outside of the outer casing 6.

[0099] A first radial hole 15b is formed at the rear of the first support portion 64. The first radial hole 15b opens on the outer peripheral surface of the first support portion 64 and extends radially along the first support portion 64, communicating with the rear of the passage body 15a. A second radial hole 15c is formed at the front of the first support portion 64. Thus, the first radial hole 15b and the second radial hole 15c are separated in the front-rear direction. The second radial hole 15c opens on the outer peripheral surface of the first support portion 64 and extends radially along the first support portion 64, communicating with the front of the passage body 15a.

[0100] The pin hole 4 is cylindrical, opening at the front end face of the first support portion 64 and extending linearly rearward within the first support portion 64. The pin hole 4 does not penetrate the first support portion 64 in the front-rear direction. Therefore, the pin hole 4 is not connected to the suction passage 15, which includes the passage body 15a.

[0101] Furthermore, a first sliding bearing 51 is provided on the outer peripheral surface of the first support portion 64. The first sliding bearing 51 is formed into a cylindrical shape with a diameter larger than that of the first support portion 64. The first sliding bearing 51 is disposed in the outer peripheral surface of the first support portion 64 at a position between the first radial bore 15b and the second radial bore 15c. Alternatively, a ball bearing may be provided instead of the first sliding bearing 51.

[0102] The outer casing 62 is disposed in front of the outer casing body 60. The outer casing 62 is formed in a generally disk shape centered on the rotation axis O1. The outer casing 62 has a front surface 62a facing forward, a rear surface 62b located on the opposite side of the front surface 62a and facing rearward, and an outer peripheral surface 62c connecting the front surface 62a and the rear surface 62b and located between the front surface 62a and the rear surface 62b.

[0103] In addition, a second support portion 66, a second insertion hole 61, and a discharge portion 63 are formed in the outer casing 62.

[0104] 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 through hole 61 is formed into a cylindrical shape centered on the rotation axis O1 and extends within the outer casing 62 in the direction of the rotation axis O1. Furthermore, the rear end of the second through hole 61 opens at the rear end of the second support portion 66, i.e., the rear end of the outer casing 62. By forming the second through hole 61 in this way, the second support portion 66 forms a cylindrical shape centered on the rotation axis O1.

[0105] On the other hand, the front end of the second insertion hole 61 does not open at the front end of the outer casing 62. Furthermore, a second sliding bearing 52 is provided inside the second insertion hole 61. The second sliding bearing 52 is cylindrical and positioned at the front of the second insertion hole 61. Alternatively, a ball bearing may be used instead of the second sliding bearing 52.

[0106] The discharge section 63 consists of a discharge port 69 and a discharge passage 67. The discharge port 69 is formed on the outer peripheral surface 62c. The discharge port 69 opens outward from the outer peripheral surface 62c in the radial direction of the outer casing 62. The discharge port 69 is connected to the condenser (not shown) via a pipe (not shown).

[0107] A discharge passage 67 is formed within the outer casing 62. The discharge passage 67 extends radially within the outer casing 62. Furthermore, the discharge passage 67 is connected at one end to the discharge connection port 69 and at the other end to the second insertion hole 61. Thus, the discharge passage 67 communicates with both the discharge connection port 69 and the second insertion hole 61, while simultaneously connecting the second insertion hole 61 to the discharge connection port 69.

[0108] In the outer casing 6, the outer casing cover 62 is positioned in front of the outer casing body 60, with its rear surface 62b abutting against the front end of the outer peripheral wall 60a of the outer casing body 60. Furthermore, multiple bolts (not shown) are inserted into the outer casing cover 62 abutting against the front end of the outer peripheral wall 60a, thus securing the outer casing cover 62 to the outer casing body 60. In this way, the outer casing body 60 and the outer casing cover 62 are integrated into the outer casing 6.

[0109] Furthermore, in the outer casing 6, the front of the outer casing body 60 is closed by the outer casing cover 62, thereby forming an intake chamber 65 within the outer casing body 60. The intake chamber 65 is connected to the intake connection port 68. Thus, refrigerant gas is drawn into the intake chamber 65 from the outside of the outer casing 6 through the intake connection port 68. The refrigerant gas is an example of a "fluid" in this invention. Additionally, the intake chamber 65 is also connected to the intake passage 15. Therefore, the refrigerant gas in the intake chamber 65 is drawn into the passage body 15a through the first aperture 15b.

[0110] The electric motor 10 is housed within the intake chamber 65. Thus, the intake chamber 65 also serves as the motor chamber for housing the electric motor 10.

[0111] The electric motor 10 consists of a stator 17 and a rotor 11. The stator 17 is cylindrical with a rotation axis O1 as its center and has a winding 17a. The stator 17 is fixed to the outer casing 60 and then to the outer casing 6 by being embedded in the inner circumferential surface of the outer peripheral wall 60a.

[0112] The rotor 11 is cylindrical around the rotation axis O1 and is disposed inside the stator 17. Although detailed drawings are omitted, the rotor 11 is composed of a plurality of permanent magnets corresponding to the stator 17 and stacked steel plates that fix each permanent magnet.

[0113] The compression mechanism 14 is disposed inside the housing 6. The compression mechanism 14 consists of a driving scroll 30, a driven scroll 40, and a driven mechanism 20.

[0114] The driving scroll member 30 is made of aluminum alloy. The driving scroll member 30 has a driving end plate 31, a driving peripheral wall 32, a driving scroll body 33, a first cover 35, and a second cover 37. The first cover 35 is an example of the "supported part" in this invention.

[0115] The drive end plate 31 extends in a generally disk-shaped manner, orthogonal to the rotation axis O1 and the driven axis O2. The driven axis O2 extends parallel to the rotation axis O1 while being eccentric relative to it. That is, the driven axis O2 is also parallel to the front-rear direction. In addition, the drive end plate 31 has a front surface 311 opposite to the second cover 37 and a rear surface 312 located on the opposite side of the front surface 311.

[0116] Furthermore, in addition to the recess 38, a discharge port 39 is formed on the drive end plate 31. 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 within the portion that is within the recess 38, and extends through the drive end plate 31 in the front-rear direction. Additionally, at the recess 38, the discharge reed valve 57 and the retainer 58 are fixed to the drive end plate 31 by fixing bolts 59. The discharge reed valve 57 is an example of a "discharge valve" in this invention.

[0117] The discharge reed valve 57 opens by elastic deformation, thereby allowing refrigerant gas in the compression chamber 12 to be discharged into the discharge chamber 8 through the discharge port 39. Conversely, the discharge reed valve 57 closes by elastic deformation, thereby preventing the refrigerant gas in the compression chamber 12 from being discharged into the discharge chamber 8 through the discharge port 39. Furthermore, the closed discharge reed valve 57 prevents refrigerant gas in the discharge chamber 8 from flowing into the compression chamber 12 through the discharge port 39. The retainer 58 allows adjustment of the opening degree of the discharge reed valve 57. Further details regarding the compression chamber 12 and the discharge chamber 8 will be described later.

[0118] The drive peripheral wall 32 is integral with the drive end plate 31, and extends in a cylindrical shape from the outer periphery of the drive end plate 31 toward the rear, i.e. toward the driven scroll member 40. At this time, the drive peripheral wall 32 extends parallel to the rotation axis O1 and the driven axis O2.

[0119] The driving scroll body 33 is integral with the driving end plate 31 and is disposed on the inner side of the driving peripheral wall 32. The driving scroll body 33 protrudes from the rear surface 312 of the driving end plate 31, parallel to the driving peripheral wall 32, toward the driven scroll member 40. Figure 6 As shown, the driving vortex body 33 extends in a vortex shape from the center of the driving end plate 31 outwards in a vortex-like manner, with the center side of the driving end plate 31 as the vortex center. Furthermore, the outer peripheral end of the driving vortex body 33 is connected to the driving peripheral wall 32. Additionally, in Figure 6 For ease of explanation, the illustration of electric motor 10 has been omitted. (The following section discusses...) Figure 8 , Figure 10 , Figure 13 as well as Figure 15 The same applies.

[0120] like Figure 1 As shown, the first cover 35 extends in a generally disk-shaped manner, orthogonal to the rotation axis O1 and the driven axis O2. The first cover 35 has a front surface 35a facing forward and a rear surface 35b located on the opposite side of the front surface 35a.

[0121] Additionally, the first cover 35 has a first boss 35c, a first insertion hole 35d, and a suction connection hole 35e. The suction connection hole 35e is an example of a "suction connection part" in this invention. The first boss 35c is integrally formed in the center of the rear surface 35b and protrudes rearward in the direction of the rotation axis O1 and the driven axis O2.

[0122] The first through hole 35d passes through the first cover 35, including the first boss 35c, in the direction of the rotation axis O1. Thus, the first boss 35c forms a cylindrical shape centered on the rotation axis O1.

[0123] like Figure 2 As shown, the first through 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 forms the rear portion of the first through hole 35d. The second hole portion 352 is located between the first hole portion 351 and the third hole portion 353, forming the central portion of the first through hole 35d. The third hole portion 353 forms the rear portion of the first through hole 35d.

[0124] 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 an inner diameter larger than that of the third hole portion 353. Thus, the inner diameter of the first through 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.

[0125] like Figure 1 As shown, a suction connection hole 35e is formed within the first boss 35c. The suction connection hole 35e extends obliquely from the radially outer side to the inner side of the first boss 35c, moving from the front to the rear. The front end of the suction connection hole 35e opens on the front surface 35a. Furthermore, the rear end of the suction connection hole 35e opens at the second hole portion 352 of the first insertion hole 35d.

[0126] Furthermore, in the first cover 35, four rings 22 are provided on the front surface 35a. The rings 22 are arranged at equal intervals along the circumference of the first cover 35. Additionally, in... Figure 1 The diagram shows two of the four rings in ring 22.

[0127] The second cover 37 has a cover body 37a and a second boss 37b. The second boss 37b is an example of a "rotation axis" in this invention. The cover body 37a extends in a generally disk-shaped manner, orthogonal to the rotation axis O1 and the driven axis O2. Furthermore, the cover body 37a is formed to have almost the same diameter as the drive end plate 31. The second boss 37b is integrally formed on the cover body 37a and protrudes forward from the cover body 37a in the directions of the rotation axis O1 and the driven axis O2.

[0128] like Figure 3 As shown, 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 forms 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, forming the central portion of the second boss 37b. The third diameter portion 373 forms the front portion of the second boss 37b.

[0129] 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 an outer diameter larger than that of the third diameter portion 373. Thus, 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.

[0130] In addition, such as Figure 1 As shown, a connecting passage 37c and a discharge connection hole 37d are formed in the second cover 37. The discharge connection hole 37d is an example of a "discharge connection part" in this invention. The connecting passage 37c passes through the second cover 37, including the second boss 37b, in the direction of the rotation axis O1. Thus, the second boss 37b is formed into a cylindrical shape centered on the rotation axis O1.

[0131] The discharge connection hole 37d connects to the connection passage 37c and extends radially within the second boss 37b. Furthermore, the discharge connection hole 37d opens on the outer peripheral surface of the second boss 37b, more specifically, on the outer peripheral surface of the second radial portion 372. In other words, the discharge connection hole 37d is formed in the second boss 37b.

[0132] In the drive scroll member 30, the cover body 37a of the second cover 37 abuts against the front surface 311 of the drive end plate 31, and the rear end of the drive peripheral wall 32 abuts against the front surface 35a of the first cover 35. Furthermore, in this state, the second cover 37, the drive end plate 31, the drive peripheral wall 32, and the first cover 35 are connected by multiple bolts 50. Thus, in the drive scroll member 30, the drive end plate 31, the drive peripheral wall 32, the first cover 35, and the second cover 37 are integrated. Furthermore, in... Figure 1 The image shows two of the multiple bolts 50.

[0133] Furthermore, in the second cover 37, the cover body 37a covers the recess 38 of the drive end plate 31 from the front. Thus, the connecting passage 37c communicates with the recess 38 from the front. In this way, the discharge chamber 8 is formed in the drive vortex member 30 by the recess 38 and the connecting passage 37c.

[0134] Furthermore, in the drive scroll member 30, the drive peripheral wall 32 is fixed to the rotor 11 while being brought into the rotor 11. Thus, the drive scroll member 30 is fixed to the rotor 11 and integrated with the rotor 11.

[0135] The driven scroll member 40 is also made of aluminum alloy. The driven scroll member 40 is housed within the driving scroll member 30. The driven scroll member 40 has a driven end plate 41 and a driven scroll body 43.

[0136] Driven end plate 41 extends in a generally disk-shaped manner, orthogonal to the rotation axis O1 and driven axis O2. Driven end plate 41 has a front surface 411 and a rear surface 412. The front surface 411 is opposite to the rear surface 312 of the drive end plate 31 within the drive scroll member 30. The rear surface 412 is located on the opposite side of the front surface 411 and is opposite to the front surface 35a of the first cover 35.

[0137] Additionally, a receiving portion 71 is formed in the driven end plate 41. The receiving portion 71 is cylindrically recessed from the rear surface 412 of the driven end plate 41 towards the front. A bushing 53 is housed within the receiving portion 71. Furthermore, a driven pin 55 is inserted into the bushing 53. More specifically, the driven pin 55 is inserted into the bushing 53 at a position off-center from the center of the bushing 53. The driven pin 55 is cylindrical and protrudes rearward from the bushing 53 and further from the driven end plate 41 toward the first support portion 64. Alternatively, the bushing 53 may also be housed within the receiving portion 71 via a bearing such as a sliding bearing.

[0138] Additionally, four rotation-stopping pins 21 are fixed to the rear surface 412. Each rotation-stopping pin 21 is positioned in the rear surface 412 at a location closer to the outer periphery of the receiving portion 71 and opposite to each ring 22. Each rotation-stopping pin 21 protrudes rearward from the rear surface 412. Furthermore, in Figure 1 The diagram shows two of the four rotation-stopping pins 21.

[0139] The driven scroll 43 is integral with the driven end plate 41, extending from the front surface 411 of the driven end plate 41 toward the driving scroll 30, parallel to the rotation axis O1 and the driven axis O2. Figure 6 As shown, the driven vortex body 43 extends outward in a vortex shape with the center side of the driven end plate 41 as the vortex center.

[0140] Figure 1The driven mechanism 20 shown consists of four rotation-stopping pins 21 and four rings 22. Here, it is sufficient to have three or more rotation-stopping pins 21 and rings 22, and their number can be designed appropriately.

[0141] In the compression mechanism 14, with the driven scroll member 40 housed within the driving scroll member 30, the driving scroll body 33 of the driving scroll member 30 is engaged with the driven scroll body 43 of the driven scroll member 40. Furthermore, the respective rotation stop pins 21 are inserted into the respective rings 22. In this way, the driving scroll member 30 and the driven scroll member 40 are assembled in the front-rear direction. Moreover, strictly speaking, after the driving scroll body 33 and the driven scroll body 43 are engaged and the respective rotation stop pins 21 are inserted into the respective rings 22, the second cover 37, the driving end plate 31, the driving peripheral wall 32, and the first cover 35 are connected within the driving scroll member 30 by bolts 50.

[0142] Furthermore, after assembling the driving scroll member 30 and the driven scroll member 40, the first sliding bearing 51 is inserted into the first through hole 35d of the first cover 35 in the driving scroll member 30. More specifically, as... Figure 2 As shown, the first sliding bearing 51 is inserted into the first hole 351 of the first insertion hole 35d. Furthermore, the first sliding bearing 51 abuts against the height difference formed between the first hole 351 and the second hole 352 due to the difference in their inner diameters, thereby holding the first sliding bearing 51 in place. Thus, the first boss 35c, and consequently the first cover 35, is supported by the first support 64 via the first sliding bearing 51 and is rotatable. Here, the inner diameter of the second hole 352 of the first insertion hole 35d is larger than the outer diameter of the first support 64. Therefore, when the first cover 35 is supported by the first support 64, the first cover 35 is radially separated from the first support 64 in the second hole 35, and the first cover 35 does not contact the first support 64.

[0143] Furthermore, supported by the first support portion 64 via the first cover 35, the second radial hole 15c faces the second hole portion 352 in the suction passage 15. As a result, the second radial hole 15c communicates with the suction connection hole 35e through the second hole portion 352. That is, the suction passage 15 and the suction connection hole 35e are connected radially in the first support portion 64, i.e., radially in the outer casing 6, via the first insertion hole 35d.

[0144] In addition, such as Figure 1 As shown, in the driving vortex component 30, the second boss 37b of the second cover 37 is inserted into the second insertion hole 61. Thus, as... Figure 3As shown, the third diameter portion 373 of the second boss 37b is inserted into the second sliding bearing 52. Furthermore, while the second sliding bearing 52 abuts against the height difference between the third diameter portion 373 and the second diameter portion 372 formed by the difference in their outer diameters, the second sliding bearing 52 is held in place by the second insertion hole 61. Thus, the second boss 37b, and consequently the second cover 37, is supported by the second support portion 66 via the second sliding bearing 52, allowing it to rotate. In this way, as... Figure 1 As shown, the drive scroll member 30 is supported on the housing 6 by both the first support portion 64 and the second support portion 66 in a manner that allows it to rotate about the rotation axis O1. As a result, the second boss 37b can rotate about the rotation axis O1 within the second through hole 61.

[0145] Here, as Figure 3 As shown, the second diameter 372 of the second boss 37b is formed to be smaller than the diameter of the second through hole 61. Therefore, when the second boss 37b is supported by the second support portion 66, the second diameter 372 is radially separated from the inner circumferential surface of the second through hole 61. Thus, the inner circumferential surface of the second through hole 61 does not contact the second diameter 372. Furthermore, because the second boss 37b is supported by the second support portion 66, the discharge connection hole 37d faces the inside of the second through hole 61. As a result, the discharge connection hole 37d communicates with the discharge passage 67 of the discharge section 63 through the second through hole 61. In this way, in this compressor, the discharge passage 67 and the discharge connection hole 37d, and further, the discharge section 63 and the discharge connection hole 37d, are radially connected in the outer casing 6. That is, the discharge connection hole 37d allows refrigerant gas discharged into the discharge chamber 8 to flow into the discharge section 63.

[0146] like Figure 1 As shown, in the driven scroll member 40, the driven pin 55 is inserted into the pin hole 4 of the first support portion 64. Thus, the driven scroll member 40 is supported by the first support portion 64 via the driven pin 55, enabling it to rotate about the driven axis O2. In other words, unlike the driving scroll member 30, the driven scroll member 40 is supported on the housing 6 solely by the first support portion 64 in a manner that allows it to rotate about the driven axis O2.

[0147] Furthermore, in the compression mechanism 14, the driving scroll member 30 and the driven scroll member 40 are assembled in the front-to-back direction, such as... Figure 6 As shown, two compression chambers 12 are formed between the driving scroll body 33 of the driving scroll member 30 and the driven scroll body 43 of the driven scroll member 40. Additionally, as... Figure 1As shown, a suction space 30a is formed within the drive peripheral wall 32 by assembling the driving scroll member 30 and the driven scroll member 40 in the front-rear direction. The suction space 30a communicates with the front end of the suction connection hole 35e and can also communicate with each compression chamber 12 through the operation of the compressor. Each compression chamber 12 and the suction space 30a are separated from the suction chamber 65 by the driving scroll member 30 and the driven scroll member 40.

[0148] In the compressor configured as described above, such as Figure 1 As shown by the dashed arrow, the low-temperature, low-pressure refrigerant gas after passing through the evaporator is drawn into the suction chamber 65 through the suction inlet 68. Furthermore, if the electric motor 10 operates and the rotor 11 rotates, the drive scroll 30 is driven to rotate around the rotation axis O1 within the suction chamber 65. That is, the drive scroll 30 rotates integrally with the rotor 11. At this time, in the driven mechanism 20, each rotation stop pin 21 slides in contact with the inner circumferential surface of each ring 22, causing each ring 22 to rotate relative to the center of its respective rotation stop pin 21. In this way, the driven mechanism 20 transmits the torque driving the scroll 30 to the driven scroll 40.

[0149] As a result, the driven scroll member 40 rotates around the driven axis O2 while being eccentric relative to the driving scroll member 30, driven by both the driving scroll member 30 and the driven mechanism 20. At this time, the driven mechanism 20 restricts the rotation of the driven scroll member 40. Thus, the driven scroll member 40 revolves relative to the driving scroll member 30 around the driven axis O2. Here, in this compressor, the driving scroll member 30 and the driven scroll member 40... Figure 6 Rotate in the direction R1 as shown.

[0150] Additionally, the vortex component 30 is driven to rotate around the rotation axis O1, as follows: Figure 7 , Figure 9 as well as Figure 11 As shown, the suction connection hole 35e rotates relative to the second diameter hole 15c of the suction passage 15 in the rotation direction R1. Furthermore, this is achieved by driving the vortex member 30 to rotate around the rotation axis O1, as... Figure 14 and Figure 16 As shown, the discharge connection hole 37d rotates relative to the discharge passage 67 in the rotation direction R1.

[0151] In this way, the phase (hereinafter, the phase between the driving scroll 30, which rotates around the rotation axis O1, and the driven scroll 40, which rotates around the driven axis O2, is referred to as the rotation phase) changes, causing a change in the volume of each compression chamber 12. Thus, as... Figure 1As shown by the dashed arrow, the refrigerant gas in the suction chamber 65 is drawn into the passage body 15a, i.e., the suction passage 15, through the first aperture 15b. Moreover, the refrigerant gas in the passage body 15a is drawn into each compression chamber 12 through the second aperture 15c, the second hole 352 of the first insertion hole 35d, the suction connection hole 35e, and the suction space 30a.

[0152] Furthermore, the refrigerant gas drawn into each compression chamber 12 is compressed within each compression chamber 12 as it flows from the outer periphery of the vortex of the driving vortex body 33 and the driven vortex body 43 toward the center of the vortex. 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.

[0153] The refrigerant gas discharged into the discharge chamber 8 flows through the discharge connection hole 37d, the second insertion hole 61, and the discharge passage 67, and is discharged from the discharge connection port 69 toward the condenser (outside the housing). In this way, air conditioning is performed based on the vehicle air conditioning system.

[0154] In this compressor, intake pulsation is inevitably generated due to the intake of refrigerant gas from the intake chamber 65 into each compression chamber 12, and discharge pulsation is inevitably generated due to the discharge of refrigerant gas from each compression chamber 12 into the discharge chamber 8.

[0155] In this respect, the compressor can appropriately reduce both intake and exhaust pulsations. The effects of this operation will be explained in detail below. Furthermore, the following explanation will focus on one of the two compression chambers 12.

[0156] like Figure 4 As shown, by changing the rotational phase of the driving scroll member 30 and the driven scroll member 40, the volume of the compression chamber 12 gradually increases from its minimum state. Furthermore, after the volume of the compression chamber 12 reaches its maximum, by changing the rotational phase of the driving scroll member 30 and the driven scroll member 40, the volume of the compression chamber 12 gradually decreases. And, during the process of the volume of the compression chamber 12 increasing from its minimum to its maximum, refrigerant is drawn into the compression chamber 12. That is, as described above, the refrigerant gas in the suction chamber 65 is drawn into the compression chamber 12 from the suction passage 15 through the second hole 352 of the first through hole 35d, the suction connection hole 35e, and the suction space 30a.

[0157] Furthermore, 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 become... Figure 6The state shown is as follows. Furthermore, as the volume of the compression chamber 12 increases from its minimum to its maximum, the flow rate of refrigerant drawn into the compression chamber 12 changes. 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 reaches its maximum. Additionally, when the rotational phase between the driving scroll 30 and the driven scroll 40 is phase X1, the compression chamber 12 is in the process of increasing its volume towards its maximum, and the volume of the compression chamber 12 has not yet reached its maximum.

[0158] Here, in this compressor, a suction connection hole 35e is formed in the first housing 35. Therefore, accompanied by the rotational drive of the drive scroll 30, as... Figure 7 , Figure 9 as well as Figure 11 As shown, the suction connection hole 35e, while facing the second diameter hole 15c, rotates around the rotation axis O1 in the rotation direction R1 around the second diameter hole 15c. That is, by driving the vortex member 30 to rotate, the phase of the second diameter hole 15c and the suction connection hole 35e will change. That is, with the rotation of the first cover 35, the phase of the suction passage 15 and the suction connection hole 35e will change.

[0159] Furthermore, because the phase between the second aperture 15c and the suction connection hole 35e changes in this way, the flow resistance of the refrigerant gas flowing from the second aperture 15c and then from the suction passage 15 to the suction connection hole 35e, i.e., the suction-side flow resistance, changes in this compressor. Additionally, in this compressor, a pulsation different from the suction pulsation and the discharge pulsation is generated due to the suction-side flow resistance (hereinafter, this pulsation is referred to as the "first elimination pulsation"). Moreover, the magnitude of the first elimination pulsation changes due to the change in the suction-side flow resistance.

[0160] Here, when the rotational phase between the driving scroll member 30 and the driven scroll member 40 is phase X1, as follows: Figure 7 As shown, the suction connection hole 35e is located on the opposite side of the rotation direction R1, separated from the second diameter hole 15c by the rotation axis O1. Therefore, as Figure 7 As shown by the dashed arrow, when refrigerant gas is drawn into the compression chamber 12, the refrigerant gas flows from the second diameter hole 15c, around the second hole portion 352 of the first through hole 35d in the rotational direction R1, and then flows through the suction connection hole 35e. Thus, the phase between the second diameter hole 15c and the suction connection hole 35e is... Figure 7In the state shown, that is, when the rotational phase of the driving scroll 30 and the driven scroll 40 is phase X1, the suction-side flow resistance becomes maximum. In other words, in this compressor, the suction connection hole 35e is formed in the first housing 35 in such a way 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 drawn into the compression chamber 12 is maximum, the second diameter hole 15c and the suction connection hole 35e are at the phase that maximizes the suction-side flow resistance.

[0161] Then, as Figure 4 As shown, by making the rotational phase of the driving scroll 30 and the driven scroll 40 a phase X2 that is larger than phase X1, the volume of the compression chamber 12 becomes the maximum (refer to...). Figure 8 Here, when the volume of the compression chamber 12 is at its maximum, the driving vortex 33 and the driven vortex 43 prevent the compression chamber 12 from communicating with the intake space 30a. Therefore, since the volume of the compression chamber 12 is at its maximum, refrigerant gas is no longer drawn into the compression chamber 12, and the refrigerant gas in the compression chamber 12 is sealed inside the compression chamber 12.

[0162] Additionally, when the volume of compression chamber 12 is at its maximum, such as Figure 9 As shown, the suction connection hole 35e is located almost directly opposite the second diameter hole 15c. Therefore, as... Figure 9 As shown by the dashed arrow, when refrigerant gas is drawn into the compression chamber 12, the refrigerant gas can flow almost directly from the second diameter hole 15c to the suction connection hole 35e. Therefore, the second diameter hole 15c and the suction connection hole 35e are in phase... Figure 9 In the state shown, 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 diameter hole 15c and the suction connection hole 35e are in a phase that minimizes the suction-side flow resistance.

[0163] Then, as Figure 4 As shown, by making the rotational phase of the driving scroll 30 and the driven scroll 40 a phase X3 that is larger than phase X2, the volume of the compression chamber 12 becomes smaller than the maximum (refer to...). Figure 10 Therefore, the refrigerant gas in the compression chamber 12 begins to be compressed as the volume of the compression chamber 12 becomes smaller than its maximum.

[0164] Furthermore, when the rotational phase between the driving scroll member 30 and the driven scroll member 40 is phase X3, such as Figure 11 As shown, the suction connection hole 35e and the second diameter hole 15c, which were almost directly opposite each other, begin to deviate again in the rotational direction R1. Therefore, as Figure 9As shown by the dashed arrow, when refrigerant gas is drawn into the compression chamber 12, compared to the case where the suction port 35e and the second diameter port 15c are almost directly opposite each other, the refrigerant gas becomes more difficult to reach the suction port 35e from the second diameter port 15c. In other words, when the second diameter port 15c and the suction port 35e are in phase... Figure 11 At the position shown, the suction-side flow resistance becomes greater than its minimum. As a result, in this compressor, as the volume of the compression chamber 12 decreases compared to its maximum, the suction-side flow resistance increases compared to its minimum. Thus, in this compressor, the second diameter hole 15c and the suction connection hole 35e are in a phase where the suction-side flow resistance increases as the volume of the compression chamber 12 decreases compared to its maximum.

[0165] Thus, in this compressor, the change in phase between the second diameter hole 15c and the suction connection hole 35e causes a change in the suction-side flow resistance, and this change in suction-side flow resistance causes a change in the magnitude of the first pulsation elimination. Furthermore, as... Figure 12 As shown, in this compressor, the first pulsation elimination waveform is the opposite phase waveform to the suction pulsation waveform. As a result, although suction pulsation is inevitably generated in this compressor due to the intake of refrigerant gas from the suction chamber 65 to each compression chamber 12, the suction pulsation can be reduced because the first pulsation elimination works to counteract the suction pulsation.

[0166] In addition, such as Figure 5 As shown, as the rotational phase of the driving scroll 30 and the driven scroll 40 becomes larger than phase X3, the refrigerant gas in the compression chamber 12 is compressed and propelled, increasing the pressure within the compression chamber 12. Then, by changing the rotational phase of the driving scroll 30 and the driven scroll 40 to phase X4, as... Figure 13 As shown, the compression chamber 12 begins to connect with the discharge port 39. However, at this time, the discharge reed valve 57 is still in the closed state.

[0167] Then, as Figure 5 As shown, by aligning the rotational phases of the driven scroll 30 and the driven scroll 40 to phase X5, the compression of the refrigerant gas in the compression chamber 12 is further advanced. Consequently, the pressure within the compression chamber 12 becomes higher than the pressure within the discharge chamber 8, thus opening the discharge reed valve 57. This initiates the discharge of refrigerant gas from the compression chamber 12 into the discharge chamber 8.

[0168] Here, in this compressor, a discharge connection hole 37d is formed on the second boss 37b of the second cover 37. Therefore, by driving the scroll member 30 to rotate, as... Figure 14 and Figure 16As shown, the discharge connection hole 37d rotates about the rotation axis O1 in the rotation direction R1 within the second insertion hole 61. Therefore, by driving the vortex member 30 to rotate, the phase between the discharge passage 67 and the discharge connection hole 37d will change. That is, the phase between the discharge passage 67 and the discharge connection hole 37d will change with the rotation of the second boss 37b.

[0169] Furthermore, because the phase between the discharge passage 67 and the discharge connection hole 37d changes in this way, the flow resistance of the refrigerant gas flowing from the discharge connection hole 37d to the discharge passage 67, i.e., the discharge-side flow resistance, changes in this compressor. Additionally, due to the discharge-side flow resistance, a pulsation different from the discharge pulsation, suction pulsation, and the first elimination pulsation (hereinafter referred to as the "second elimination pulsation") is generated in this compressor. Moreover, the magnitude of the second elimination pulsation changes along with the change in the discharge-side flow resistance.

[0170] Here, when the rotational phase between the driving scroll member 30 and the driven scroll member 40 is phase X4, as follows: Figure 14 As shown, the discharge connection hole 37d is located almost directly opposite the discharge passage 67. Therefore, as... Figure 14 As shown by the dashed arrow, the refrigerant gas discharged into the discharge chamber 8 can flow almost directly from the discharge connection hole 37d to the discharge passage 67. That is, the discharge passage 67 and the discharge connection hole 37d are in phase... Figure 14 In the state shown, the discharge-side flow resistance is minimized. In other words, in this compressor, the discharge connection hole 37d is formed on the second boss 37b in such a way that the discharge-side flow resistance is minimized when the rotational phase of the driving scroll 30 and the driven scroll 40 is phase X4. Here, as described above, when the rotational phase of the driving scroll 30 and the driven scroll 40 is phase X4, the discharge reed valve 57 is in a closed state. Therefore, the flow rate of refrigerant gas discharged from the compression chamber 12 to the discharge chamber 8 is minimal, reaching 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 minimal, the discharge passage 67 and the discharge connection hole 37d are at a phase that minimizes the discharge-side flow resistance.

[0171] Then, as Figure 5 As shown, when the rotational phase of the driving scroll 30 and the driven scroll 40 becomes phase X5, which is larger than phase X4, the pressure in the compression chamber 12 reaches the discharge pressure, and the discharge reed valve 57 opens. Thus, refrigerant gas is discharged from the compression chamber 12 to the discharge chamber 8. Furthermore, at this time, the flow rate of the refrigerant gas discharged from the compression chamber 12 to the discharge chamber 8 is at its maximum. Additionally, when the rotational phase of the driving scroll 30 and the driven scroll 40 is phase X5, as... Figure 15 As shown, the two compression chambers 12 are integrated with each other.

[0172] Here, when the rotational phase between the driving scroll member 30 and the driven scroll member 40 is phase X5, as follows: Figure 16 As shown, the discharge connection hole 37d is located on almost the opposite side of the rotation direction R1, separated from the discharge passage 67 by the rotation axis O1. Therefore, as Figure 16 As shown by the dashed arrow, the refrigerant gas in the discharge chamber 8 flows from the discharge connection hole 37d, around the second insertion hole 61 in the rotational direction R1, and flows through the discharge passage 67.

[0173] Therefore, the phase of the discharge passage 67 and the discharge connection hole 37d is... Figure 16 In the state shown, the discharge-side flow resistance is at its maximum. 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 its maximum, the discharge passage 67 and the discharge connection hole 37d are in a phase that maximizes the discharge-side flow resistance.

[0174] Thus, in this compressor, discharge passage 67 and discharge connection hole 37d are connected from an almost directly opposite position (see reference). Figure 14 As the refrigerant gas deviates in the direction of rotation R1, it becomes difficult for the refrigerant gas to flow from the discharge connection hole 37d to the discharge passage 67. Therefore, the discharge-side flow resistance becomes greater than its minimum. Thus, in this compressor, the discharge passage 67 and the discharge connection hole 37d are in a phase where the discharge-side flow resistance increases as the flow rate of the refrigerant gas discharged from the compression chamber 12 to the discharge chamber 8 approaches 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 where the flow rate of the refrigerant gas discharged to the discharge chamber 8 becomes maximum, the discharge passage 67 and the discharge connection hole 37d of the discharge section 63 become a phase where the discharge-side flow resistance increases.

[0175] Thus, in this compressor, the discharge-side flow resistance changes due to the phase change between the discharge passage 67 and the discharge connection hole 37d, and further through the phase change between the discharge section 63 and the discharge connection hole 37d. This change in discharge-side flow resistance then alters the magnitude of the second pulsation elimination. Furthermore, as... Figure 17 As shown, in this compressor, the second pulsation elimination waveform is the opposite phase waveform to the discharge pulsation waveform. As a result, although discharge pulsation is inevitably generated in this compressor due to the discharge of refrigerant gas from each compression chamber 12 to the discharge chamber 8, the discharge pulsation can be reduced because the second pulsation elimination works to counteract the discharge pulsation.

[0176] In this way, in this compressor, suction pulsation can be reduced by changing the flow resistance on the suction side, and discharge pulsation can be reduced by changing the flow resistance on the discharge side. Therefore, in this compressor, it is not necessary to excessively enlarge the suction chamber 65 to reduce suction pulsation, nor is it necessary to excessively enlarge 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 enlarge the outer casing 6, and also difficult to enlarge the drive scroll member 30, and consequently the compression mechanism 14.

[0177] Therefore, the compressor of Example 1 is able to achieve high quietness while suppressing large size.

[0178] In particular, in this compressor, the compression mechanism 14 is composed of a driving scroll member 30, a driven scroll member 40, and a driven mechanism 20, making the compression mechanism 14 a dual-rotation scroll compression mechanism. Furthermore, a suction connection hole 35e is formed in the first housing 35, and a discharge connection hole 37d is formed in the second boss 37b of the second housing 37. Thus, in this compressor, both the suction connection hole 35e and the discharge connection hole 37d can be formed in the driving scroll member 30, thereby facilitating the formation of both the suction connection hole 35e and the discharge connection hole 37d.

[0179] Furthermore, since the compression mechanism 14 is a dual-rotation scroll compressor, the generation of intake pulsation and discharge pulsation in this compressor is less complicated, and intake pulsation and discharge pulsation can be appropriately reduced by varying the flow resistance on the intake side and the flow resistance on the discharge side.

[0180] Furthermore, in this compressor, a discharge reed valve 57 is provided on the drive scroll member 30. The discharge reed valve 57 allows refrigerant gas to be discharged from each compression chamber 12 to the discharge chamber 8, while simultaneously preventing refrigerant gas from flowing from the discharge chamber 8 to each compression chamber 12. Therefore, in this compressor, the generation of pulsations caused by the backflow of refrigerant gas from the discharge chamber 8 to each compression chamber 12 is appropriately prevented. Additionally, a discharge connection hole 37d is formed on the second boss 37b, and the discharge connection hole 37d is located downstream of the discharge reed valve 57 in the refrigerant gas flow direction. Therefore, in this compressor, the pressure variation when refrigerant gas flows from the discharge connection hole 37d to the discharge passage 67 can assist in opening the discharge reed valve 57. As a result, the opening and closing of the discharge reed valve 57 can be appropriately performed in this compressor.

[0181] Furthermore, in this compressor, the discharge section 63 has a discharge passage 67 and a discharge connection port 69, with the discharge passage 67 and the discharge connection port 37d communicating radially in the housing 6. Also, the suction passage 15 and the suction connection port 35e communicate radially in the housing 6. Therefore, compared to a configuration where the discharge passage 67 and the discharge connection port 37d are connected in the direction of the rotation axis O1, and the suction passage 15 and the suction connection port 35e are connected in the direction of the rotation axis O1, this compressor allows for miniaturization of the entire compressor in the direction of the rotation axis O1 by incorporating the housing 6 internally.

[0182] Example 2

[0183] like Figure 18 As shown, in the compressor of Embodiment 2, the outer casing 6 is composed of an outer casing body 60 and an outer casing cover 70. Furthermore, in this compressor, the drive scroll member 30 has a third cover 81 instead of a second cover 37. Also, in this compressor, a discharge chamber 83 is formed on the drive end plate 31 instead of a recess 38.

[0184] The outer casing 70 is also made of aluminum alloy. The outer casing 70 is positioned at the front of the outer casing body 60. The outer casing 70 is formed in a generally disc-shaped configuration centered on a rotation axis O1. The outer casing 70 has a front surface 70a facing forward, a rear surface 70b located opposite the front surface 70a and facing rearward, and an outer peripheral surface 70c connecting the front surface 70a and the rear surface 70b and located between the two surfaces. The outer casing 70 is fixed to the outer casing body 60 in the same manner as the outer casing 62 in the compressor of Embodiment 1.

[0185] Furthermore, a second insertion hole 72 and a discharge connection port 73 are formed in the outer casing 70. The discharge connection port 73 is an example of the "discharge section" in this invention.

[0186] The second through-hole 72 is formed in a cylindrical shape centered on the rotation axis O1, extending within the outer casing 70 along the direction of the rotation axis O1. The rear end of the second through-hole 72 opens on the rear surface 70b. A second sliding bearing 52 is provided within the second through-hole 72, similar to that in the compressor of Embodiment 1.

[0187] The discharge port 73 penetrates the outer casing 70 in the direction of the rotation axis O1. Therefore, the front end of the discharge port 73 opens on the front surface 70a, and the rear end communicates with the second insertion hole 72. Figure 19 As shown in (A) to (D), the discharge port 73 is formed as a cylinder eccentric to the rotation axis O1. That is, the discharge port 73 is formed on the outer casing 70 at a position eccentric to the rotation axis O1. The discharge port 73 is connected to the condenser (not shown) via piping (not shown).

[0188] like Figure 18 As shown, the third cover 81 has a cover body 81a and a second boss 81b. The second boss 81b is also an example of a "rotation shaft portion" in this invention. The cover body 81a has the same configuration as the cover body 37a in the compressor of Embodiment 1. The second boss 81b is integrally formed on the cover body 81a and protrudes forward from the center of the cover body 81a in the direction of the rotation axis O1 and the driven axis O2. Thus, the center of the second boss 81b is coaxial with the rotation axis O1.

[0189] Furthermore, a connecting passage 81c is formed in the third cover 81. The connecting passage 81c is an example of a "discharge connector" in this invention. The connecting passage 81c extends through the third cover 81, including the second boss 81b, in the direction of the rotation axis O1. That is, the connecting passage 81c is formed in the second boss 81b. Figure 18 and Figure 19 As shown in (A) to (D), the connecting passage 81c is formed as a cylinder eccentric to the rotation axis O1. That is, the connecting passage 81c is formed on the third cover 81 at a position eccentric to the rotation axis O1. Furthermore, the connecting passage 81c is formed with a diameter smaller than the discharge port 73. Additionally, in Figure 19 For ease of explanation, in addition to simplifying the illustration of the discharge port 73 and the connection passage 81c, the illustration of the second boss 81b and the like is also omitted.

[0190] Figure 18 The discharge chamber 83 shown 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 from the front surface 311 of the drive end plate 31 toward the rear and communicates with the discharge port 39. In addition, the discharge reed valve 57 and the retainer 58 are fixed in the discharge chamber 83 by fixing bolts 59.

[0191] like Figure 18 As shown, in this compressor, similar to the compressor of Embodiment 1, the third housing 81, drive end plate 31, drive peripheral wall 32, and first housing 35 are connected by multiple bolts 50. Thus, in the third housing 81, the housing body 81a covers the discharge chamber 83 of the drive end plate 31 from the front. In this way, the connecting passage 81c communicates with the discharge chamber 83 from the front. Furthermore, the connecting passage 81c is located downstream of the discharge reed valve 57 in the refrigerant gas flow direction.

[0192] In this compressor, the second boss 81b is inserted into the second insertion hole 72. Thus, the second boss 81b is supported by the second sliding bearing 52 within the second insertion hole 72 and is rotatable. Furthermore, the discharge port 73 and the connecting passage 81c are connected in the direction of the rotation axis O1. Other components of this compressor are the same as those of the compressor in Embodiment 1; for the same components, the same reference numerals are used, and detailed descriptions related to the components are omitted.

[0193] In this compressor, the refrigerant gas compressed in the compression chamber is discharged from the outlet 39 into the discharge chamber 83. Furthermore, the refrigerant gas discharged into the discharge chamber 83 flows through the connection passage 81c to the discharge connection port 73 and is discharged towards the condenser.

[0194] Furthermore, in this compressor, such as Figure 19 As shown in (A) to (D), the discharge port 73 and the connecting passage 81c are respectively eccentric relative to the rotation axis O1. Therefore, in this compressor, the drive scroll 30 is directed towards... Figure 19 During one revolution of the rotation direction R1 shown in (A) to (D), the phase of the discharge port 73 and the connection passage 81c changes. That is, the phase of the discharge port 73 and the connection passage 81c changes with the rotation of the second boss 81b.

[0195] That is, in this compressor, when the rotation angle of the driving scroll 30 is zero degrees, the discharge port 73 and the connection passage 81c become... Figure 19 The phase shown in (A). Then, if the driving vortex element 30 is from Figure 19 Rotating approximately 90° from the position shown in (A) in the rotation direction R1, the discharge port 73 and the connecting passage 81c become... Figure 19 The phase shown in (B). Then, if the driving vortex element 30 is from Figure 19 From the position shown in (B), rotate approximately 90° in the direction of rotation R1 (if the driving vortex component 30 is driven from...). Figure 19 (A) is rotated approximately 180° in the direction of rotation R1, then the discharge port 73 and the connecting passage 81c become Figure 19 The phase shown in (C). Then, if the driving vortex element 30 is from Figure 19 From the position shown in (C), rotate approximately 90° in the direction of rotation R1 (if the driving scroll 30 is driven from...). Figure 19 (A) is rotated approximately 270° in the direction of rotation R1 from the position shown. Then, the discharge port 73 and the connecting passage 81c become Figure 19 The phase shown in (D).

[0196] During the period when the drive scroll 30 rotates once, the communication area between the discharge port 73 and the connection passage 81c changes. As a result, the flow resistance of the refrigerant gas flowing from the connection passage 81c to the discharge port 73, i.e., the discharge-side flow resistance, changes in the compressor.

[0197] Specifically, if the communication area between the discharge port 73 and the connecting passage 81c increases, the discharge side resistance decreases; conversely, if the communication area between the discharge port 73 and the connecting passage 81c decreases, the discharge side resistance increases. Therefore, in this compressor, when the phase of the discharge port 73 and the connecting passage 81c is... Figure 19 When the state shown in (A) is reached, the communication area between the discharge port 73 and the connecting passage 81c is maximized, and the flow resistance on the discharge side is minimized. On the other hand, when the phase of the discharge port 73 and the connecting passage 81c is... Figure 19 When the state shown in (C) is reached, the connection area between the discharge port 73 and the connection passage 81c becomes the minimum, and the flow resistance on the discharge side becomes the maximum.

[0198] Here, in this compressor, when the flow rate of refrigerant gas discharged from the compression chamber 12 to the discharge chamber 83 is at its minimum, the discharge port 73 and the connection passage 81c are in a phase that minimizes the flow resistance on the discharge side (see reference). Figure 19 (A)). Furthermore, in this compressor, when the flow rate of refrigerant gas discharged from the compression chamber 12 to the discharge chamber 83 is at its maximum, the discharge port 73 and the connection passage 81c are in a phase that maximizes the flow resistance on the discharge side (see reference). Figure 19 (C)).

[0199] As a result, similar to the compressor in Example 1, although discharge pulsations are inevitably generated due to the discharge of refrigerant gas from each compression chamber 12 to the discharge chamber 83, the discharge pulsations can be reduced.

[0200] Furthermore, in this compressor, the discharge port 73 and the connecting passage 81c are connected in the direction of the rotation axis O1. Therefore, compared to a configuration where the discharge port 73 and the connecting passage 81c are connected radially in the housing 6, the compressor as a whole can be radially miniaturized by including the housing 6 internally. Other functions in this compressor are the same as those in the compressor of Embodiment 1.

[0201] Example 3

[0202] like Figure 20 As shown, in the compressor of Embodiment 3, the outer casing 6 is composed of an outer casing body 60 and an outer casing cover 75. Furthermore, in this compressor, the drive scroll member 30 has a fourth cover 88 instead of the second cover 37.

[0203] The outer casing 75 is composed of a first main body component 75a and a first retaining component 75b. The first main body component 75a is made of aluminum alloy. Like the outer casing 70 in the compressor of Embodiment 2, the first main body component 75a is formed in a generally disk-shaped manner centered on the rotation axis O1. The first main body component 75a has a front surface 751 facing forward, a rear surface 752 located on the opposite side of the front surface 751 and facing rearward, and an outer peripheral surface 753 connecting the front surface 751 and the rear surface 752 and located between the front surface 751 and the rear surface 752.

[0204] The first main component 75a is fixed to the outer casing 60 in the same way as the outer casing 62 in the compressor of Embodiment 1. In this way, the outer casing 60 and the outer casing 75 are also fixed in this compressor.

[0205] Additionally, a second insertion hole 76 and a first connection port 77a are formed in the first main body component 75a. The second insertion hole 76 is formed in a cylindrical shape centered on the rotation axis O1 and extends within the first main body component 75a in the direction of the rotation axis O1. The rear end of the second insertion hole 76 opens at the rear surface 752. Here, the diameter of the second insertion hole 76 is larger than that of the second insertion hole 72 in the compressor of Embodiment 2.

[0206] The first connection port 77a extends through the first main body component 75a in the direction of the rotation axis O1. Thus, the front end of the first connection port 77a opens on the front surface 751, and the rear end communicates with the second insertion hole 76. Although detailed drawings are omitted, the first connection port 77a, like the discharge connection port 73 in the compressor of Embodiment 2, is formed in a cylindrical shape eccentrically relative to the rotation axis O1. That is, the first connection port 77a is formed on the first main body component 75a at a position eccentrically relative to the rotation axis O1.

[0207] The first retaining member 75b is made of resin. The first retaining member 75b is formed into a generally cylindrical shape with a bottom. A second connecting port 77b is formed at the front of the first retaining member 75b. The second connecting port 77b extends through the front of the first retaining member 75b in the direction of the rotation axis O1. The second connecting port 77b is formed into a cylindrical shape that is coaxial with and has the same diameter as the first connecting port 77a. That is, the second connecting port 77b is formed at the front of the first retaining member 75b at a position eccentric relative to the rotation axis O1.

[0208] The first retaining member 75b is accommodated within the second insertion hole 76. At this time, the first retaining member 75b is accommodated within the second insertion hole 76 in a non-rotatable state. Thus, neither the first main body member 75a nor the first retaining member 75b can rotate within the outer casing 75. Furthermore, through the first retaining member 75b being accommodated within the second insertion hole 76, the second connecting port 77b is located behind and communicates with the first connecting port 77a. In this way, a discharge connecting port 77 is formed through the first connecting port 77a and the second connecting port 77b. That is, the discharge connecting port 77 is formed in the outer casing 75 at a position eccentric to the rotation axis O1. The discharge connecting port 77 is an example of a "discharge section" in this invention.

[0209] Furthermore, a radial ball bearing 78 is provided inside the first retaining member 75b. That is, the first retaining member 75b holds the radial ball bearing 78 within the second through hole 76. Moreover, sealing rings 79a and 79b are provided on the outer peripheral surface of the first retaining member 75b. The sealing rings 79a and 79b seal between the outer peripheral surface of the first retaining member 75b and the inner peripheral surface of the second through hole 76. Alternatively, a sliding bearing may be provided inside the first retaining member 75b instead of the radial ball bearing 78. Alternatively, the first retaining member 75b may be formed using synthetic rubber or a metal with lower stiffness than the first main body member 75a.

[0210] The fourth cover 88 has a cover body 88a and a second boss 88b. The second boss 88b is also an example of a "rotation shaft portion" in this invention. The cover body 88a has the same configuration as the cover body 81a in the compressor of Embodiment 2, and further as the cover body 37a in the compressor of Embodiment 1. The second boss 88b is integrally formed on the cover body 88a and protrudes forward from the center of the cover body 88a in the direction of the rotation axis O1 and the driven axis O2. Thus, the center of the second boss 88b is coaxial with the rotation axis O1. Here, the second boss 88b protrudes forward a shorter distance than the second boss 81b in the compressor of Embodiment 2.

[0211] A connecting passage 88c is formed in the fourth cover 88. The connecting passage 88c is also an example of a "discharge connection" in this invention. The connecting passage 88c extends through the fourth cover 88, including the second boss 88b, in the direction of the rotation axis O1. That is, the connecting passage 88c is formed in the second boss 88b. Similar to the connecting passage 81c in the compressor of Embodiment 2, the connecting passage 88c is formed as a cylinder eccentric to the rotation axis O1. In other words, the connecting passage 88c is formed in the fourth cover 88 at a position eccentric to the rotation axis O1. Furthermore, the connecting passage 88c is formed with a diameter smaller than the discharge connection port 77.

[0212] The fourth housing 88, like the third housing 81 in the compressor of Embodiment 2, is connected to the drive end plate 31 by a plurality of bolts 50. Thus, the connection passage 88c communicates with the discharge chamber 83 from the front. Furthermore, the connection passage 88c is located downstream of the discharge reed valve 57 in the direction of refrigerant gas flow.

[0213] In this compressor, the second boss 88b is inserted into the radial ball bearing 78. Thus, the second boss 88b is supported within the first retaining member 75b, and further within the second through hole 76 of the first main body member 75a, allowing it to rotate. Additionally, the discharge port 77 communicates with the connecting passage 88c in the direction of the rotation axis O1. The other components of this compressor are the same as those in the compressor of Embodiment 2.

[0214] In this compressor, the discharge port 77 and the connecting passage 88c are respectively eccentric relative to the rotation axis O1. Therefore, similar to the compressor of Embodiment 2, in this compressor, the drive scroll 30 is eccentric in the rotational direction R1 (refer to...). Figure 19 During one revolution of (B) to (D), the phase of the discharge port 77 and the connection passage 88c changes. That is, the phase of the discharge port 77 and the connection passage 88c changes with the rotation of the second boss 88b. In this way, the discharge pulsation can be reduced in this compressor, just like in the compressor of Embodiment 2.

[0215] In this compressor, when the refrigerant gas is compressed in each compression chamber 12, the driving scroll 30 and the driven scroll 40 inevitably vibrate. To address this, in this compressor, a resin-made first retaining member 75b, located within the second through-hole 76, holds the radial ball bearing 78. Thus, in this compressor, the vibration of the driving scroll 30, transmitted to the first main body member 75a via the second boss 88b and the radial ball bearing 78, can be suppressed by the first retaining member 75b. Therefore, in this compressor, vibration of the outer casing 75, and consequently the outer casing 6, during operation can be suppressed as much as possible. Other functions in this compressor are the same as those in the compressor of Embodiment 1.

[0216] Example 4

[0217] like Figure 21 As shown, the compressor of Embodiment 4 includes a housing 301, a fixing block 303, a drive shaft 305, an electric motor 307, and a compression mechanism 314.

[0218] 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 radially along the motor housing 313.

[0219] The first peripheral wall 313b is connected to the rear wall 313a and extends forward from the rear wall 313a in the direction of the rotation axis O3 of the drive shaft 305. The rotation axis O3 is parallel to the front-back direction. Through these rear walls 313a and the first peripheral walls 313b, the motor housing 313 forms a bottomed cylindrical shape. Furthermore, through the rear walls 313a and the first peripheral walls 313b, a suction chamber 317 is formed inside the motor housing 313.

[0220] Additionally, a support recess 313c and a suction portion 313d are formed on the rear wall 313a. The support recess 313c is recessed towards the rear while facing the suction chamber 317. The support recess 313c is formed into a generally cylindrical shape centered on the rotation axis O3. A first radial ball bearing 319 is provided inside the support recess 313c.

[0221] The suction section 313d is composed of a first passage 401 and a second passage 402. The first passage 401 opens on the outer peripheral surface of the rear wall 313a and extends radially along the motor housing 313 inside the rear wall 313a. Here, the first passage 401 does not penetrate the rear wall 313a radially through the motor housing 313. In addition, the first passage 401 is connected to an evaporator (not shown).

[0222] The second passage 402 extends in the rear wall 313a along the direction of the rotation axis O3. Thus, the first passage 401 and the second passage 402 are orthogonal. The rear end of the second passage 402 is connected to the first passage 401. Furthermore, the front end of the second passage 402 is connected to the interior of the support recess 313c.

[0223] The second passage 402 is formed as a cylinder eccentric to the rotation axis O3. That is, the second passage 402 is formed on the rear wall 313a at a position eccentric to the rotation axis O3.

[0224] 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 radially along the compressor housing 315. The second peripheral wall 315b is connected to the front wall 315a and extends rearward from the front wall 315a in the direction of the rotation axis O3. Through these front walls 315a and second peripheral walls 315b, the compressor housing 315 also forms a bottomed cylindrical shape.

[0225] The compressor housing 315 includes an oil separation chamber 315c, a first discharge recess 315d, a discharge passage 315e, and a discharge connection port 315f. The oil separation chamber 315c is located at the front side within the compressor housing 315 and extends radially along the compressor housing 315. The first discharge recess 315d is located at the rear side within the compressor housing 315, forming a shape that is recessed towards the oil separation chamber 315c. The discharge passage 315e extends along the rotation axis O3, connecting the oil separation chamber 315c to the first discharge recess 315d. The discharge connection port 315f is connected to the upper end of the oil separation chamber 315c and opens towards the outside of the compressor housing 315. A pipe (not shown) is connected to the discharge connection port 315f.

[0226] A separator 321 is fixed inside the oil separation chamber 315c. Furthermore, the inner circumferential surface of the oil separation chamber 315c and the outer circumferential surface of the separator 321 form a separator. Additionally, a filter 323 is provided inside the oil separation chamber 315c, located below the separator 321.

[0227] A fixing block 303 is disposed between the motor housing 313 and the compressor housing 315. Multiple bolts 325 are inserted into the compressor housing 315 to fasten the motor housing 313, the compressor housing 315, and the fixing block 303. In this way, the fixing block 303 is clamped and fixed to both the motor housing 313 and the compressor housing 315. Furthermore, the fixing block 303 is disposed within the housing 301 between the electric motor 307 and the compression mechanism 314. Additionally, in... Figure 21 The diagram shows one of the multiple bolts 25. Furthermore, the methods for securing the motor housing 313, compressor housing 315, and fixing block 303 can be appropriately designed.

[0228] The fixed block 303 has a boss 303a that protrudes toward the suction chamber 317 and further toward the electric motor 307. A through hole 303b is formed at the top of the boss 303a. A second radial ball bearing 327 and a seal 329 are disposed in the boss 303a.

[0229] In addition to forming multiple connecting passages 355, the fixing block 303 also has multiple rotation-stopping pins 331 fixed thereon. Each connecting passage 355 is located on the outer side of the boss 303a and passes through the fixing block 303 in the direction of the rotation axis O3. Thus, each connecting passage 355 connects the suction chamber 317 to the interior of the compressor housing 315. Each rotation-stopping pin 331 is fixed to the fixing block 303 in a rearward protruding state. Furthermore, in Figure 21 In the diagram, each connecting path 355 and its respective switching pin 331 are illustrated.

[0230] The drive shaft 305 is cylindrical and extends along the rotation axis O3. A suction connection 500 is formed on the drive shaft 305. The suction connection 500 is composed of a shaft path 501 and a radial path 502.

[0231] The shaft path 501 opens at the rear end face of the drive shaft 305 and extends inside the drive shaft 305 along the direction of the rotation axis O3. Here, the shaft path 501 does not penetrate the drive shaft 305 in the direction of the rotation axis O3. The shaft path 501 is formed as a cylinder eccentric to the rotation axis O3. That is, the shaft path 501 is formed on the drive shaft 305 at a position eccentric to the rotation axis O3. Furthermore, the shaft path 501 is formed with a diameter smaller than that of the second passage 402.

[0232] The path 502 opens on the outer peripheral surface of the drive shaft 305 and extends radially along the drive shaft 305 and further along the housing 301 inside the drive shaft 305. Thus, the path 502 is connected to the shaft path 501.

[0233] Additionally, an eccentric pin 505 is fixed to the drive shaft 305. The eccentric pin 505 is located in the front end face of the drive shaft 305, at a position eccentric to the rotation axis O3. The eccentric pin 505 is formed as a cylinder with a diameter smaller than that of the drive shaft 305, and extends forward from the drive shaft 305.

[0234] A drive shaft 305 is disposed within the intake 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. Thus, at the intake connection 500, the shaft path 501 and the second passage 402 of the intake portion 313d are connected in the direction of the rotation axis O3. Furthermore, at the intake connection 500, the path 502 is open in the intake chamber 317. In this way, the intake connection 500 connects the intake portion 313d to the intake chamber 317.

[0235] Furthermore, a drive shaft 305 is disposed within the suction chamber 317, with its front portion and eccentric pin 505 inserted into the insertion hole 303b of the fixing block 303, entering the boss 303a. Within the boss 303a, the front portion of the drive shaft 305 is supported by a second radial ball bearing 327, allowing it to rotate. This enables the drive shaft 305 to rotate around the rotation axis O3 within the suction chamber 317. Additionally, a seal 329 seals the fixing block 303 and the drive shaft 305. Moreover, the eccentric pin 505 is fitted into the bushing 350 within the boss 303a.

[0236] Furthermore, a counterweight 333 is integrally formed on the drive shaft 305. The counterweight 333 is located at the front portion of the drive shaft 305, positioned off-center from the rotation axis O3. More specifically, the counterweight 333 is positioned on the opposite side of the eccentric pin 505, separated from the rotation axis O3. Additionally, the counterweight 333 is located within the suction chamber 317, between the stationary block 303 and the electric motor 307.

[0237] The electric motor 307 consists 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 peripheral wall 313b inside the suction chamber 317.

[0238] Rotor 307b is disposed within stator 307a. Drive shaft 305 is fixed to rotor 307b by thermoforming. Thus, rotor 307b and drive shaft 305 are integrated. Rotation of rotor 307b within stator 307a causes drive shaft 305 to rotate about axis of rotation O3.

[0239] The compression mechanism 314 has a fixed scroll member 309 and a movable scroll member 310. The fixed scroll member 309 is disposed within the compressor housing 315 and fixed to the compressor housing 315. The fixed scroll member 309 has a fixed end plate 309a, a fixed peripheral wall 309b, and a fixed scroll wall 309c. The fixed end plate 309a is located at the front end of the fixed scroll member 309 and is formed in a disc shape. A second discharge recess 309d and a discharge outlet 309e are formed on the fixed end plate 309a. The second discharge recess 309d is formed in a shape that is recessed from the front end face of the fixed end plate 309a toward the rear. The fixed scroll member 309 is fixed to the compressor housing 315, so that the second discharge recess 309d is opposite to the first discharge recess 315d. In this way, the discharge chamber 335 is formed by the first discharge recess 315d and the second discharge recess 309d. The discharge chamber 335 is connected to the oil separation chamber 315c via the discharge passage 315e. The discharge outlet 309e passes through the fixed end plate 309a in the direction of the rotation axis O3 and is connected to the discharge chamber 335.

[0240] Additionally, a discharge reed valve 339 and a retainer 341 are mounted on the fixed end plate 309a via fixing bolts 337. The fixing bolts 337, the discharge reed valve 339, and the retainer 341 are disposed within the discharge chamber 335. The discharge reed valve 339 opens and closes the discharge port 309e through elastic deformation. The retainer 341 adjusts the opening degree of the discharge reed valve 339.

[0241] The fixed peripheral wall 309b connects to the fixed end plate 309a on the outer periphery of the fixed end plate 309a and extends rearward in a cylindrical shape. An intake port 309f is formed in the fixed peripheral wall 309b. The intake port 309f penetrates the fixed peripheral wall 309b radially through the fixed scroll member 309. Thus, the intake port 309f opens within the compressor housing 315. The fixed scroll wall 309c rises from the rear surface of the fixed end plate 309a and is integral with the fixed peripheral wall 309b on its inner side.

[0242] Additionally, an oil supply passage 343 is formed in the fixed scroll member 309. The oil supply passage 343 extends through the fixed end plate 309a and the fixed peripheral wall 309b. Thus, the front end of the oil supply passage 343 opens on the front surface of the fixed end plate 309a, and the rear end of the oil supply passage 343 opens on the rear surface of the fixed peripheral wall 309b. The oil supply passage 343 is connected to the oil separation chamber 315c via the filter 323. Furthermore, the shape of the oil supply passage 343 can be appropriately designed.

[0243] A movable scroll member 310 is disposed within the compressor housing 315, located between the fixed scroll member 309 and the fixed block 303. The movable scroll member 310 has a movable end plate 310a and a movable scroll wall 310b. The movable end plate 310a is located at the rear end of the movable scroll member 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. Thus, the movable scroll member 310 is connected to the drive shaft 305 at an eccentric position from the rotation axis O3 via the bushing 350 and the eccentric pin 505.

[0244] Additionally, the movable end plate 310a is provided with the same number of rings 347 as the rotation-stopping pins 331. Furthermore, in Figure 21 The diagram shows one of the multiple rings 347.

[0245] The movable scroll wall 310b stands upright on the front surface of the movable end plate 310a and extends toward the fixed end plate 309a. In addition, near the center of the movable scroll wall 310b, an air supply hole 310d is formed, which opens at the front end of the movable scroll wall 310b and extends along the direction of the rotation axis O3 to the movable end plate 310a inside the movable scroll wall 310b.

[0246] The fixed scroll member 309 and the movable scroll member 310 mesh with each other. Thus, a compression chamber 349 is formed between the fixed scroll member 309 and the movable scroll member 310 via a fixed end plate 309a, a fixed scroll wall 309c, a movable end plate 310a, and a movable scroll wall 310b. The volume of the compression chamber 349 changes due to the rotation of the movable scroll member 310. Therefore, the compression chamber 349 is connected to the intake port 309f and the discharge port 309e, respectively.

[0247] Furthermore, by inserting each rotation-preventing pin 331 into a ring 347, each ring 47 is connected to its respective rotation-preventing pin 331. These rotation-preventing pins 331 and rings 347 together form a rotation-prevention mechanism 316. Moreover, the rotation-preventing mechanism 316 may consist of three or more rotation-preventing pins 331 and rings 347, and the number can be appropriately designed.

[0248] Furthermore, a metal thrust plate 361 is provided between the movable scroll member 310 and the fixed block 303. The thrust plate 361 can exert force on the movable scroll member 310 towards the forward side, i.e., the side of the fixed scroll member 309, through the restoring force during elastic deformation. In addition, a back pressure chamber 363 is formed in the boss 303a of the fixed block 303 through the movable end plate 310a and the thrust plate 361. The back pressure chamber 363 is connected to the air supply port 310d.

[0249] In the compressor configured as described above, such as Figure 21 As shown by the dashed arrow, the low-temperature, low-pressure refrigerant gas after passing through the evaporator is drawn into the suction chamber 317 from the suction section 313d via the suction connector 500. Furthermore, driven by the electric motor 307, the rotor 307b rotates together with the drive shaft 305 within the stator 307a. This causes the movable scroll member 310 to rotate in the compression mechanism 314, the movable end plate 310a to slide on the top of the fixed scroll wall 309c, and the fixed scroll wall 309c and the movable scroll wall 310b to slide relative to each other. At this time, the movable scroll member 310 is restricted from rotating by the anti-rotation mechanism 316, revolving only relative to the fixed scroll member 309.

[0250] Furthermore, as the movable scroll member 310 rotates, the refrigerant gas in the suction chamber 317 is drawn into the compression chamber 349 through the connecting passage 355 from the suction port 309f. The compression chamber 349 compresses the refrigerant gas inside as its volume decreases due to the rotation of the movable scroll member 310. Thus, the high-pressure refrigerant gas compressed in the compression chamber 349 is discharged from the discharge port 309e to the discharge chamber 335, and from the discharge chamber 335, it reaches the oil separation chamber 315c through the discharge passage 315e. As the high-pressure refrigerant gas circulates between the outer circumferential surface of the separator 321 and the inner circumferential surface of the oil separation chamber 315c, it separates the lubricating oil while flowing inside the separator 321 and being discharged from the discharge connecting port 315f to the outside of the outer casing 301.

[0251] On the other hand, the lubricating oil separated from the refrigerant gas is stored in the oil separation chamber 315c. Furthermore, the lubricating oil flows through the oil supply passage 343 via the filter 323, thereby supplying the sliding parts of the fixed scroll member 309 and the movable scroll member 310, the suction chamber 317, and the like.

[0252] Additionally, a portion of the high-pressure refrigerant gas compressed in the compression chamber 349 flows through the air supply port 310d and is supplied into the back pressure chamber 363. As a result, the movable scroll member 310 is forced towards the compression chamber 349 by the pressure within the back pressure chamber 363 via the thrust plate 361. Furthermore, the movable scroll member 310 is also forced towards the compression chamber 349 by the elastic force of the thrust plate 361. Thus, in this compressor, rotation of the movable scroll member 310 in a state of inclination relative to the rotation axis O3 is suppressed.

[0253] Furthermore, although suction pulsation is unavoidable during operation in this compressor, it can be appropriately reduced. That is, in this compressor, the low-temperature, low-pressure refrigerant gas after passing through the evaporator flows from the first passage 401 of the suction section 313d through the second passage 402, and then flows from the axial path 501 of the suction connection section 500 through the radial path 502, thereby being drawn into the suction chamber 317 from the radial path 502.

[0254] In this compressor, the second passage 402 and the shaft passage 501 are eccentric relative to the rotation axis O3. Therefore, during one revolution of the drive shaft 305 and consequently the movable scroll member 310, the phase of the second passage 402 and the shaft passage 501 changes. Furthermore, accompanying this phase change, the communication area between the second passage 402 and the shaft passage 501, and consequently the communication area between the suction section 313d and the suction connection section 500, changes. Consequently, during one revolution of the drive shaft 305, the communication area between the second passage 402 and the shaft passage 501 changes, and the flow resistance of the refrigerant gas flowing from the second passage 402 to the shaft passage 501, i.e., the suction-side flow resistance, changes.

[0255] Specifically, if the connection area between the second passage 402 and the axial passage 501 increases, the flow resistance on the suction side decreases; if the connection area between the suction part 313d and the suction connection part 500 decreases, the flow resistance on the suction side increases.

[0256] Although detailed illustrations are omitted, in this compressor, when the flow rate of refrigerant gas drawn from the suction port 309f into the compression chamber 349 is at its maximum, the second passage 402 and the shaft passage 501 are in a phase where the suction-side flow resistance is at its maximum. Furthermore, in this compressor, when the volume of the compression chamber 349 is at its maximum, the second passage 402 and the shaft passage 501 are in a phase where the suction-side flow resistance is at its minimum.

[0257] As a result, this compressor, like the compressor of Example 1, is able to reduce suction pulsation. Therefore, in this compressor, it is not necessary to excessively enlarge the suction chamber 317 to reduce suction pulsation. Consequently, in this compressor, the outer casing 301 becomes less likely to be enlarged.

[0258] Therefore, the compressor of Example 4 is also able to suppress large size while achieving high quietness.

[0259] Example 5

[0260] like Figure 22 As shown, in the compressor of Embodiment 5, the housing 301 consists of a motor housing 318 and a compressor housing 315 (see reference). Figure 21 )constitute.

[0261] Figure 22 The motor housing 318 shown is composed of a second main body component 91 and a second retaining component 92. The second main body component 91 is made of aluminum alloy. The second main body component 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 component 91, and thus the motor housing 318, and extends radially along the motor housing 318.

[0262] The first peripheral wall 91b is connected to the rear wall 91a and extends forward from the rear wall 91a in the direction of the rotation axis O3. Similar to the motor housing 313 in the compressor of Embodiment 4, a suction chamber 317 is also formed inside the motor housing 318. In addition, the motor housing 318 is also fastened to the compressor housing 315 and the fixing block 303 by a plurality of bolts 325.

[0263] Additionally, a support recess 911, a first passage 901, and a second passage 902 are formed on the rear wall 91a. The support recess 911 is recessed rearward while facing the suction chamber 317. The support recess 911 is formed into a generally cylindrical shape centered on the rotation axis O3. Here, the support recess 911 is formed with a diameter larger than that of the support recess 313c in the compressor of Embodiment 4.

[0264] 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 Embodiment 4. That is, the first passage 901 opens on the outer peripheral surface of the rear wall 91a and extends radially along the motor housing 318 inside the rear wall 91a. The first passage 901 is also connected to an evaporator (not shown). The second passage 902 extends in the rear wall 91a in the direction of the rotation axis O3, and its rear end communicates with the first passage 901. In addition, the second passage 902 communicates with the interior of the support recess 911 at its front end.

[0265] The second passage 902 is formed as a cylinder eccentric to the rotation axis O3. That is, the second passage 902 is formed on the rear wall 91a at a position eccentric to the rotation axis O3.

[0266] The second retaining member 92 is made of resin. The second retaining member 92 is formed into a generally cylindrical shape with a bottom. A third passage 903 is formed at the rear of the second retaining member 92. The third passage 903 extends through the rear of the second retaining member 92 in the direction of the rotation axis O3. The third passage 903 is formed into a cylindrical shape that is coaxial with and has the same diameter as the second passage 902. That is, the third passage 903 is formed at the rear of the second retaining member 92 at a position eccentric relative to the rotation axis O3.

[0267] The second retaining member 92 is housed within the support recess 911. At this time, the second retaining member 92 is housed within the support recess 911 in a non-rotatable state. Thus, neither the second main body member 91 nor the second retaining member 92 can rotate within the motor housing 318. Furthermore, through the second retaining member 92b being housed within the support recess 911, the third passage 903 is located in front of and connected to the second passage 902. In this way, the suction section 912 is formed through the first passage 901, the second passage 902, and the third passage 903.

[0268] Furthermore, a first radial ball bearing 319 is disposed inside the second retaining member 92. In this way, the second retaining member 92 holds the first radial ball bearing 319 within the support recess 911. Moreover, sealing rings 79c and 79d are provided on the outer peripheral surface of the second retaining member 92. The sealing rings 79c and 79d seal between the outer peripheral surface of the second retaining member 92 and the inner peripheral surface of the support recess 911. Alternatively, a sliding bearing may be disposed inside the second retaining member 92 instead of the first radial ball bearing 319. Furthermore, similar to the first retaining member 75b in the compressor of Embodiment 3, the second retaining member 92 may be formed using synthetic rubber or a metal with lower stiffness than the second main body member 91.

[0269] 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 on the second retaining member 92, and further, on the support recess 911, via the first radial ball bearing 319. Additionally, at the suction connection 500, the shaft path 501 and the third passage 903 of the suction section 912 are connected in the direction of the rotation axis O3. Therefore, in this compressor, the suction section 912 and the suction chamber 317 are connected via the suction connection 500. The other components of this compressor are the same as those of the compressor in Embodiment 4.

[0270] In this compressor, the low-temperature, low-pressure refrigerant gas after passing through the evaporator flows sequentially from the first passage 901 of the suction section 912 through the second passage 902 and the third passage 903, and then flows from the axial path 501 of the suction connection section 500 through the radial path 502, thereby being drawn into the suction chamber 317 from the radial path 502 (see reference). Figure 22 (The dashed arrow). Furthermore, in this compressor, during one revolution of the drive shaft 305, and consequently the movable scroll member 310, the phase of the third passage 903 and the second passage 902 relative to the shaft passage 501 changes. In this way, similar to the compressor of Embodiment 4, suction pulsation can be reduced in this compressor.

[0271] Furthermore, in this compressor, the vibration of the movable scroll member 310 during operation can be suppressed by the second retaining member 92 and transmitted to the second main body member 91 via the drive shaft 305 and the first radial ball bearing 319. Therefore, in this compressor, the vibration of the motor housing 318, and consequently the housing 301, during operation can be suppressed as much as possible. Other functions in this compressor are the same as those in the compressor of Embodiment 4.

[0272] The present invention has been described above in conjunction with embodiments 1 to 5, but the present invention is not limited to the above embodiments 1 to 5, and can of course be applied with appropriate modifications without departing from its spirit.

[0273] For example, in the compressors of Examples 1 to 3, both the discharge pulsation and the intake pulsation are reduced, but not limited to this, only the discharge pulsation or only the intake pulsation may be reduced.

[0274] Furthermore, in the compressors of embodiments 1 to 3, the compression mechanism 14 is configured as a dual-rotation scroll compression mechanism. However, it is not limited to this; the compression mechanism 14 may also be configured as a scroll compression mechanism in which one of the two scroll members is fixed to the outer casing 6.

[0275] Alternatively, in the compressors of Examples 1 to 3, the compression mechanism 14 may be a rotary compression mechanism or a vane compression mechanism, etc. The same applies to the compression mechanism 314 in the compressors of Examples 4 and 5.

[0276] In addition, in the compressor of Embodiment 1, a discharge chamber 8 is formed in the drive scroll member 30, i.e., the compression mechanism 14, but it is not limited to this; the discharge chamber 8 may also be formed inside the housing 6. In this case, it may also be configured such that the discharge chamber 8 communicates with a portion on the opposite side of the discharge passage 67 in the rotational direction R1, separated by the second protrusion 37b, and that it radially penetrates the second protrusion 37b with respect to the discharge connection hole 37d.

[0277] Furthermore, in the compressor of Embodiment 1, the second boss 37b is designated as the "rotating shaft portion" in this invention. By inserting the second boss 37b into the second through hole 61, the second boss 37b is supported by the second support portion 66 and is rotatable. However, this is not a limitation; it is also possible to configure the second boss 37b to be rotatable by the second support portion 66 by inserting the second support portion 66 into its interior. The same applies to the compressors of Embodiments 2 and 3.

[0278] Furthermore, in the compressor of Embodiment 4, it is configured such that the second passage 402 and the shaft passage 501 are connected in the direction of the rotation axis O3, thereby connecting the suction section 313d and the suction connection section 500 in the direction of the rotation axis O3. However, it is not limited to this, and it may also be configured such that the suction section 313d and the suction connection section 500 are connected radially in the outer casing 301. The same applies to the compressor of Embodiment 5.

[0279] Furthermore, in the compressor of Embodiment 2, the discharge port 73 is formed as a cylinder eccentric to the rotation axis O3. However, it is not limited to this, and the discharge port 73 may also be other shapes. The same applies to the discharge port 77 in the compressor of Embodiment 3, the second passage 402 in the compressor of Embodiment 4, and the second passage 902 and third passage 903 in the compressor of Embodiment 5.

[0280] In addition, the following technical solutions are included in this specification.

[0281] (Note 1)

[0282] A compressor, characterized in that it comprises:

[0283] The outer casing has a discharge section for discharging fluid to the outside; and

[0284] A compression mechanism is disposed within the housing.

[0285] The compression mechanism includes a compression chamber that compresses the fluid while reducing its volume, and a rotating shaft supported by the housing that is rotatable about a rotation axis.

[0286] The outer casing or the compression mechanism has a discharge chamber that communicates with the compression chamber and allows the fluid compressed in the compression chamber to be discharged.

[0287] A discharge connection portion is formed in the rotating shaft portion to allow fluid discharged into the discharge chamber to flow into the discharge portion.

[0288] As the rotating shaft rotates, the phase between the discharge section and the discharge connection section changes, thereby changing the flow resistance of the fluid flowing from the discharge connection section to the discharge section, i.e., the discharge-side flow resistance.

[0289] The discharge section and the discharge connection section are in a phase in which the flow resistance on the discharge side increases as the flow rate of the fluid discharged from the compression chamber to the discharge chamber approaches its maximum.

[0290] (Note 2)

[0291] According to the compressor described in Appendix 1,

[0292] The discharge section and the discharge connection section are connected radially in the outer casing.

[0293] (Note 3)

[0294] According to the compressor described in Appendix 1,

[0295] The discharge section and the discharge connection section are connected in the direction of the rotation axis.

[0296] (Note 4)

[0297] According to the compressor described in Appendix 3,

[0298] The discharge section is eccentric relative to the rotation axis.

[0299] The discharge connection is eccentric relative to the rotation axis.

[0300] (Note 5)

[0301] The compressor described in any of the appendices 1 to 4,

[0302] When the flow rate of fluid discharged from the compression chamber to the discharge chamber is at its minimum, the discharge section and the discharge connection section are in a phase that minimizes the flow resistance on the discharge side.

[0303] (Note 6)

[0304] The compressor described in any of the notes 1 to 5,

[0305] When the flow rate of the fluid discharged from the compression chamber to the discharge chamber is at its maximum, the discharge section and the discharge connection section are in a phase that maximizes the flow resistance on the discharge side.

[0306] (Note 7)

[0307] According to any of the notes 1 to 6, the compressor

[0308] The compression mechanism is provided with a discharge valve that allows fluid to be discharged from the compression chamber to the discharge chamber while preventing fluid from flowing from the discharge chamber to the compression chamber.

[0309] The discharge connection is located downstream of the discharge valve in the direction of fluid flow.

[0310] (Note 8)

[0311] A compressor, characterized in that it comprises:

[0312] The outer casing has 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

[0313] A compression mechanism is disposed within the housing.

[0314] The compression mechanism includes a compression chamber that compresses the fluid while reducing its volume, and a supported portion supported by the housing that is rotatable about a rotation axis.

[0315] The supported portion has an intake connection portion that allows fluid in the intake passage to flow into the compression chamber.

[0316] As the supported portion rotates, the phase between the suction passage and the suction connector changes, thereby changing the flow resistance of the fluid flowing from the suction passage to the suction connector, i.e., the suction-side flow resistance.

[0317] The suction passage and the suction connection portion are in a phase where the flow resistance on the suction side increases as the volume of the compression chamber decreases relative to its maximum.

[0318] (Note 9)

[0319] According to the compressor described in Appendix 8,

[0320] The inhalation passage and the inhalation connection are connected radially to the outer casing.

[0321] (Postscript 10)

[0322] According to the compressor described in Appendix 8 or 9,

[0323] When the volume of the compression chamber is at its maximum, the suction passage and the suction connection are in a phase that minimizes the flow resistance on the suction side.

[0324] (Postscript 11)

[0325] The compressor described in any of the appendices 8 to 10,

[0326] When the flow rate of the fluid drawn into the compression chamber is at its maximum, the suction passage and the suction connection are in a phase that maximizes the flow resistance on the suction side.

[0327] (Postscript 12)

[0328] The compressor described in any of the appendices 1 to 11,

[0329] The compression mechanism has:

[0330] A drive scroll component capable of rotating about the axis of rotation; and

[0331] The driven scroll member, which is opposite to the driving scroll member, rotates about the driven axis through the driving scroll member and the driven mechanism while being eccentric relative to the driving scroll member, thereby forming the compression chamber between itself and the driving scroll member.

[0332] The driving scroll component has a driving end plate and a driving scroll body integral with the driving end plate and protruding in a scroll shape toward the driven scroll component.

[0333] The driven scroll member has a driven end plate and a driven scroll body that is integral with the driven end plate and protrudes in a scroll shape toward the driving scroll member.

[0334] (Postscript 13)

[0335] A compressor, characterized in that it comprises:

[0336] The outer casing has a suction chamber and a suction section for drawing in fluid from the outside;

[0337] A drive shaft, disposed within the suction chamber, is rotatable about a rotational axis; and

[0338] A compression mechanism, disposed within the housing, is connected to the drive shaft.

[0339] The drive shaft has an intake connection portion that communicates with the intake section in the direction of the rotation axis and allows fluid to flow from the intake section to the intake chamber.

[0340] The compression mechanism includes a compression chamber that compresses the fluid while reducing its volume, and an intake port that draws the fluid from the intake chamber into the compression chamber.

[0341] As the drive shaft rotates, the phase between the suction section and the suction connection section changes, thereby changing the flow resistance of the fluid flowing from the suction section to the suction connection section, i.e., the suction-side flow resistance.

[0342] The suction section and the suction connection section are in a phase where the flow resistance on the suction side increases as the volume of the compression chamber decreases relative to its maximum.

[0343] (Postscript 14)

[0344] According to the compressor described in Appendix 13,

[0345] The suction section is eccentric relative to the axis of rotation.

[0346] The inhalation connection is eccentric relative to the rotation axis.

[0347] (Postscript 15)

[0348] According to the compressor described in Appendix 13 or 14,

[0349] When the volume of the compression chamber is at its maximum, the suction section and the suction connection section are in a phase that minimizes the flow resistance on the suction side.

[0350] (Postscript 16)

[0351] The compressor described in any of the appendices 13 to 15,

[0352] When the flow rate of the fluid drawn into the compression chamber is at its maximum, the suction section and the suction connection section are in a phase that maximizes the flow resistance on the suction side.

[0353] Industrial availability

[0354] This invention can be used in vehicle air conditioning systems, etc.

[0355] Explanation of reference numerals in the attached figures

[0356] 6. 301 casing

[0357] 8, 83, 335 Exhaust Room

[0358] 12, 349 Compression Chamber

[0359] 14, 314 Compression Mechanism

[0360] 15. Inhalation route

[0361] 20 Driven Mechanism

[0362] 30 Driven scroll component

[0363] 31 Driver End Board

[0364] 33 Driving vortex body

[0365] 35. First cover (supported part)

[0366] 35e Suction Connection Hole (Suction Connection Part)

[0367] 37b, 81b, 88b Second boss (rotating shaft part)

[0368] 37d Discharge connection hole (discharge connection part)

[0369] 40 Driven scroll component

[0370] 41 Driven end plate

[0371] 43 Driven vortex body

[0372] 57 Discharge reed valve (discharge valve)

[0373] 63 Discharge section

[0374] 65, 317 Inhalation Chamber

[0375] 68. Suction connector

[0376] 73, 77 Discharge connection port (discharge section)

[0377] 81c, 88c connection passage (exhaust connector)

[0378] 305 drive shaft

[0379] 309f intake port

[0380] 313d, 912 Inhalation Section

[0381] 500 Inhalation Connection

[0382] O1, O3 Rotation Axis

[0383] O2 driven shaft

Claims

1. A compressor, characterized in that, have: The outer casing has a discharge section for discharging fluid to the outside; and A compression mechanism is disposed within the housing. The compression mechanism includes a compression chamber that compresses the fluid while reducing its volume, and a rotating shaft supported by the housing that is rotatable about a rotation axis. The outer casing or the compression mechanism has a discharge chamber that communicates with the compression chamber and allows the fluid compressed in the compression chamber to be discharged. A discharge connection portion is formed in the rotating shaft portion to allow fluid discharged into the discharge chamber to flow into the discharge portion. As the rotating shaft rotates, the phase between the discharge section and the discharge connection section changes, thereby changing the flow resistance of the fluid flowing from the discharge connection section to the discharge section, i.e., the discharge-side flow resistance. The discharge section and the discharge connection section are in a phase in which the flow resistance on the discharge side increases as the flow rate of the fluid discharged from the compression chamber to the discharge chamber approaches its maximum.

2. The compressor according to claim 1, The discharge section and the discharge connection section are connected radially in the outer casing.

3. The compressor according to claim 1, The discharge section and the discharge connection section are connected in the direction of the rotation axis.

4. The compressor according to claim 3, The discharge section is eccentric relative to the rotation axis. The discharge connection is eccentric relative to the rotation axis.

5. The compressor according to any one of claims 1 to 3, When the flow rate of fluid discharged from the compression chamber to the discharge chamber is at its minimum, the discharge section and the discharge connection section are in a phase that minimizes the flow resistance on the discharge side.

6. The compressor according to any one of claims 1 to 3, When the flow rate of the fluid discharged from the compression chamber to the discharge chamber is at its maximum, the discharge section and the discharge connection section are in a phase that maximizes the flow resistance on the discharge side.

7. The compressor according to any one of claims 1 to 3, The compression mechanism is provided with a discharge valve that allows fluid to be discharged from the compression chamber to the discharge chamber while preventing fluid from flowing from the discharge chamber to the compression chamber. The discharge connection is located downstream of the discharge valve in the direction of fluid flow.

8. A compressor, characterized in that, have: The outer casing has an inlet for drawing in fluid from the outside, an inlet chamber communicating with the inlet, and an inlet passage communicating with the inlet chamber. and A compression mechanism is disposed within the housing. The compression mechanism includes a compression chamber that compresses the fluid while reducing its volume, and a supported portion supported by the housing that is rotatable about a rotation axis. The supported portion has an intake connection portion that allows fluid in the intake passage to flow into the compression chamber. As the supported portion rotates, the phase between the suction passage and the suction connector changes, thereby changing the flow resistance of the fluid flowing from the suction passage to the suction connector, i.e., the suction-side flow resistance. The suction passage and the suction connection portion are in a phase where the flow resistance on the suction side increases as the volume of the compression chamber decreases relative to its maximum.

9. The compressor according to claim 8, The inhalation passage and the inhalation connection are connected radially to the outer casing.

10. The compressor according to claim 8 or 9, When the volume of the compression chamber is at its maximum, the suction passage and the suction connection are in a phase that minimizes the flow resistance on the suction side.

11. The compressor according to claim 8 or 9, When the flow rate of the fluid drawn into the compression chamber is at its maximum, the suction passage and the suction connection are in a phase that maximizes the flow resistance on the suction side.

12. The compressor according to claim 1 or 8, The compression mechanism has: A drive scroll component capable of rotating about the axis of rotation; and The driven scroll member, which is opposite to the driving scroll member, rotates about the driven axis through the driving scroll member and the driven mechanism while being eccentric relative to the driving scroll member, thereby forming the compression chamber between itself and the driving scroll member. The driving scroll component has a driving end plate and a driving scroll body integral with the driving end plate and protruding in a scroll shape toward the driven scroll component. The driven scroll member has a driven end plate and a driven scroll body that is integral with the driven end plate and protrudes in a scroll shape toward the driving scroll member.

13. A compressor, characterized in that, have: The outer casing has a suction chamber and a suction section for drawing in fluid from the outside; A drive shaft, which is disposed in the suction chamber, is capable of rotating about a rotation axis; as well as A compression mechanism, disposed within the housing, is connected to the drive shaft. The drive shaft has an intake connection portion that communicates with the intake section in the direction of the rotation axis and allows fluid to flow from the intake section to the intake chamber. The compression mechanism includes a compression chamber that compresses the fluid while reducing its volume, and an intake port that draws the fluid from the intake chamber into the compression chamber. As the drive shaft rotates, the phase between the suction section and the suction connection section changes, thereby changing the flow resistance of the fluid flowing from the suction section to the suction connection section, i.e., the suction-side flow resistance. The suction section and the suction connection section are in a phase where the flow resistance on the suction side increases as the volume of the compression chamber decreases relative to its maximum.

14. The compressor according to claim 13, The suction section is eccentric relative to the axis of rotation. The inhalation connection is eccentric relative to the rotation axis.

15. The compressor according to claim 13 or 14, When the volume of the compression chamber is at its maximum, the suction section and the suction connection section are in a phase that minimizes the flow resistance on the suction side.

16. The compressor according to claim 13 or 14, When the flow rate of the fluid drawn into the compression chamber is at its maximum, the suction section and the suction connection section are in a phase that maximizes the flow resistance on the suction side.

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