Rotary compressor

Abstract

This suppresses the decrease in the amount of lubrication supplied to the sliding parts inside the rotary compressor. [Solution] A rotary compressor comprising a casing (16) into which a first space (Si) into which refrigerant at suction pressure flows, an electric motor (10) arranged in the first space (Si), a drive shaft (70) that rotates around the axial direction by the electric motor (10), and a compression mechanism (15) driven by the drive shaft (70) that compresses the refrigerant in the first space (Si) and discharges the compressed refrigerant from discharge ports (24, 29), wherein the casing (16) has an oil reservoir (85) for storing refrigerant oil and a high-pressure gas space (HS) into which refrigerant discharged from the discharge ports (24, 29) flows and which communicates with vane chambers (48, 49), and an oil separation mechanism (82) for separating the refrigerant discharged from the discharge ports (24, 29) from the refrigerant oil is arranged in the high-pressure gas space (HS).

Description

Technical Field

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[0001] The present disclosure relates to a rotary compressor and a refrigeration cycle apparatus including the same. The rotary compressor is a compressor that compresses gas in a compression chamber formed in a cylinder by eccentrically rotating a roller in the cylinder. The rotary compressor generally has a vane for partitioning the compression chamber. The rotary compressor includes a so-called rolling roller type in which a vane separate from the roller abuts against the roller while the roller eccentrically rotates, a so-called swing type in which a vane formed integrally with the roller swings along with the eccentric rotation of the roller, a so-called hinge vane type in which the tip of the vane is rotatably fitted into a recess on the outer peripheral surface of the roller and the roller eccentrically rotates, and the like.

Background Art

[0002] Patent Document 1 discloses a rotary compressor including an oil separator that separates lubricating oil contained in a refrigerant. An oil supply passage is connected to the oil separator, and the lubricating oil separated by the oil separator flows through the oil supply passage and is supplied to a predetermined sliding portion in the compressor.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In Patent Document 1, the oil separator is disposed outside the rotary compressor. Therefore, when the path length of the oil supply passage connecting the oil separator to the sliding portion becomes long, the flow path resistance in the oil supply passage increases, and the amount of oil supplied to the sliding portion decreases.

[0005] An object of the present disclosure is to suppress a decrease in the amount of oil supplied to a sliding portion in a rotary compressor.

Means for Solving the Problems

[0006] The first aspect is, A casing (16) in which a first space (Si) is formed inside into which refrigerant at suction pressure flows, An electric motor (10) is arranged in the first space (Si), The drive shaft (70) rotates around the axial direction by the electric motor (10), The system includes a compression mechanism (15) which is driven by the drive shaft (70) and compresses the refrigerant in the first space (Si) and discharges the compressed refrigerant from the discharge ports (24, 29), The compression mechanism (15) is Cylinders (30, 35) and A roller (40, 45) rotates eccentrically in a cylinder chamber (S1, S2) surrounded by the inner walls of the cylinder (30, 35), The vanes (41, 46) are inserted into the vane chambers (48, 49) formed inside the cylinders (30, 35), and divide the cylinder chambers (S1, S2) formed by the space surrounded by the inner walls of the cylinders (30, 35) and the rollers (40, 45) into an intake side space (Ss) and a discharge side space (Sd). A first end plate (20) closes one end of the cylinder (30, 35) in the axial direction, The cylinder (30, 35) has a second end plate (25) that closes the other end in the axial direction of the cylinder, The casing (16) includes: An oil reservoir (85) where refrigeration oil is stored, The refrigerant discharged from the aforementioned outlets (24, 29) flows into a high-pressure gas space (HS) that communicates with the vane chambers (48, 49), An oil separation mechanism (82) is provided in the high-pressure gas space (HS) to separate the refrigerant discharged from the discharge ports (24, 29) from the refrigeration oil. It is a rotary compressor.

[0007] In the first embodiment, the oil separation mechanism (82) is located inside the casing (16). This allows for a reduction in the length of the refrigerant oil flow path from the oil separation mechanism (82) to the oil reservoir (85), and from the oil reservoir (85) to the sliding parts (especially the vane chambers (48, 49)). This reduces the resistance in the refrigerant oil flow path from the oil separation mechanism (82) to the oil reservoir (85), thereby suppressing a decrease in the amount of refrigerant oil supplied to the sliding parts.

[0008] A second aspect is, in the first aspect, The oil reservoir (85) is formed in the high-pressure gas space (HS), The system further includes an oil supply passage (90) for supplying refrigerant oil from the oil reservoir (85) to the vane chambers (48, 49).

[0009] In the second embodiment, a high-pressure gas space (HS) for supplying refrigerant oil to the vane chambers (48, 49) is formed within the casing (16), which shortens the oil supply passage (90) from the oil reservoir (85) to the vane chambers (48, 49). This reduces flow resistance within the oil supply passage (90), thereby suppressing a decrease in the amount of oil supplied to the vane chambers (48, 49).

[0010] A third aspect is a manifestation of the first or second aspect, An inlet (83) through which the refrigerant compressed by the compression mechanism (15) flows into the high-pressure gas space (HS), An outlet (84) through which the refrigerant in the high-pressure gas space (HS) flows out of the high-pressure gas space (HS), Furthermore, The inlet (83) is positioned within a range of 90° to 270° from the outlet (84) toward the circumferential direction of the casing (16) with respect to the drive shaft (70).

[0011] In the third embodiment, the distance from the inlet (83) to the outlet (84) can be increased. This allows the flow path length of the refrigerant in the oil separation mechanism (82) located in the high-pressure gas space (HS) to also be increased, thereby enabling the separation of more oil from the refrigerant.

[0012] In a fourth aspect, in any one of the first to third aspects, the oil reservoir (85) is provided at the bottom of the high-pressure gas space (HS), and an oil supply passage (90) for supplying refrigeration oil from the oil reservoir (85) to the vane chamber is provided, and the bottom of the high-pressure gas space (HS) has a tapered surface (81a) that slopes downward toward the oil supply passage (90).

[0013] In the fourth aspect, the oil reservoir (85) is formed such that refrigeration oil collects at the lower end of the oil supply passage (90). Thereby, it is possible to easily supply the refrigeration oil in the oil reservoir (85) to the oil supply passage (90).

[0014] A fifth aspect is in the first or second aspect, and further includes a muffler portion (61, 63) that forms a muffler chamber (62, 64) when the refrigerant discharged from the discharge ports (24, 29) flows in, and the oil separation mechanism (82) is disposed inside the muffler chamber (62, 64) or inside the muffler portion (61, 63).

[0015] In the fifth aspect, since the oil separation mechanism (82) also serves as a soundproof space, it is possible to suppress an increase in the volume of the high-pressure gas space (HS) and also suppress the refrigerant filling amount.

[0016] A sixth aspect is in the first or second aspect, and the oil separation mechanism (82) is provided inside the cylinder (30, 35).

[0017] In the sixth aspect, since the oil separation mechanism (82) is provided inside the cylinder (30, 35), it is possible to eliminate the space required for providing the oil separation mechanism (82). Thereby, the size of the casing (16) can be made compact.

[0018] A seventh aspect is in any one of the first to sixth aspects, The oil separation mechanism (82) is a porous member or mesh member that separates into refrigerant and refrigerating machine oil when the refrigerant gas passes through it, or has a plate member that separates into refrigerant and refrigerating machine oil when the refrigerant gas collides with it.

[0019] In the seventh aspect, the refrigerant and the refrigerating machine oil can be separated with a relatively simple mechanism. The cost of the oil separation mechanism (82) can be suppressed.

[0020] The eighth aspect is any one of the first to seventh aspects, the compression mechanism (15) is of a two-cylinder type, has a first cylinder (30) and a second cylinder (35) arranged in the axial direction, and a middle plate (50) disposed between the first cylinder (30) and the second cylinder (35), further has a communication passage (91) provided in the compression mechanism (15) and communicating a first discharge port (24) for discharging the refrigerant compressed in the first cylinder (30) and a second discharge port (29) for discharging the refrigerant compressed in the second cylinder (35), the communication passage (91) supplies the discharged refrigerant to the oil separation mechanism (82).

[0021] In the eighth aspect, by providing the communication passage (91) even in a two-cylinder type rotary compressor, the same effect as in the first aspect can be obtained with one oil separation mechanism (82).

[0022] The ninth aspect is a refrigeration cycle device including a rotary compressor according to any one of the first to eighth aspects.

[0023] In the ninth aspect, a refrigeration cycle device including the rotary compressor of the present disclosure can be provided.

Brief Description of the Drawings

[0024] [Figure 1] FIG. 1 is a configuration diagram of a refrigerant circuit of a refrigeration cycle device of an embodiment. [Figure 2] Figure 2 shows a vertical cross-section of a rotary compressor. [Figure 3A] Figure 3A shows a horizontal cross-section of the first compression mechanism. [Figure 3B] Figure 3B shows a horizontal cross-section of the second compression mechanism. [Figure 4] Figure 4 shows the operation of the first and second compression mechanisms. [Figure 5] Figure 5 shows a vertical cross-section of the rotary compressor according to Modification 1. [Figure 6] Figure 6 shows a cross-sectional view of the rotary compressor shown in Figure 5, taken along the VV arrow. [Figure 7] Figure 7 shows a vertical cross-section of the rotary compressor according to Modification 2. [Figure 8] Figure 8 shows a vertical cross-section of the rotary compressor according to Modification 2, viewed from a different direction than in Figure 7. [Figure 9] Figure 9 shows a vertical cross-section of the rotary compressor according to Modification 3. [Figure 10] Figure 10 shows a cross-sectional view of the rotary compressor shown in Figure 9, taken along the XX arrow. [Figure 11] Figure 11 shows a vertical cross-section of the rotary compressor according to Modification 4. [Figure 12] Figure 12 shows a vertical cross-section of the rotary compressor according to Modification 4, viewed from a different direction than in Figure 11. [Figure 13] Figure 13 shows a vertical cross-section of a rotary compressor according to modification 5. [Figure 14] Figure 14 is a schematic diagram showing the configuration of an oil separation mechanism according to another embodiment. [Modes for carrying out the invention]

[0025] Embodiments of the present invention will be described below with reference to the drawings. The following embodiments are essentially preferred examples and are not intended to limit the scope of the present invention, its applications, or its uses. Furthermore, the embodiments, modifications, and other examples described below can be combined or partially replaced to the extent that the present invention is implementable.

[0026] (1) Refrigeration cycle equipment As shown in Figure 1, the rotary compressor (1) in this example is applied to a refrigeration cycle device (100). The refrigeration cycle device (100) is, for example, an air conditioning device that provides air conditioning for a room. The refrigeration cycle device (100) has an outdoor unit (7) located outside and an indoor unit (8) located inside. The outdoor unit (7) houses the rotary compressor (1), a four-way switching valve (3), an outdoor heat exchanger (4), and an expansion valve (5). The indoor unit (8) houses an indoor heat exchanger (6).

[0027] The refrigeration cycle device (100) includes a refrigerant circuit (9). A rotary compressor (1), a four-way switching valve (3), an outdoor heat exchanger (4), an expansion valve (5), and an indoor heat exchanger (6) are connected to the refrigerant circuit (9). The refrigeration cycle is performed by the flow of refrigerant through the refrigerant circuit (9).

[0028] The refrigeration cycle device (100) performs heating and cooling operations by switching the four-way switching valve (3). In cooling operation, the first refrigeration cycle is performed. Specifically, when the first port (P1) and the third port (P3) of the four-way switching valve (3) are in communication, and the second port (P2) and the fourth port (P4) are in communication (solid line in Figure 1), the indoor heat exchanger (6) functions as an evaporator and the outdoor heat exchanger (4) functions as a radiator. In heating operation, the second refrigeration cycle is performed. Specifically, when the first port (P1) and the fourth port (P4) of the four-way switching valve (3) are in communication, and the second port (P2) and the third port (P3) are in communication (dashed line in Figure 1), the indoor heat exchanger (6) functions as a radiator and the outdoor heat exchanger (4) functions as an evaporator.

[0029] (2) Rotary compressor The rotary compressor (1) shown in Figure 2 is a so-called low-pressure dome type, in which a low-pressure space is formed inside the casing (16) by the intake refrigerant. Hereinafter, the rotary compressor (1) of this disclosure may be simply referred to as the compressor. The compressor (1) comprises a casing (16), an electric motor (10), a drive shaft (70), a compression mechanism (15), and an oil separation mechanism (82). The oil separation mechanism (82) will be described later.

[0030] (2-1) Casing The casing (16) is a cylindrical sealed container in an upright position. The casing (16) comprises a cylindrical body (17) and an upper end plate (18) and a lower end plate (19) that close the ends of the body (17). The casing (16) houses the compression mechanism (15) and the electric motor (10). Inside the casing (16), the electric motor (10) and the compression mechanism (15) are arranged from top to bottom. The casing (16) is provided with an intake pipe (53), a discharge pipe (54), and an inlet pipe (55). An oil reservoir (not shown) is formed at the bottom of the casing (16) for supplying refrigerant oil to the bearing section of the compression mechanism (15), which will be described later.

[0031] The suction pipe (53) introduces the suction refrigerant into the casing (16). This creates a first space (Si) inside the casing (16) into which the refrigerant at the suction pressure flows. The first space (Si) is a low-pressure space filled with refrigerant at the suction pressure. Therefore, the first space (Si) is either an suction pressure space or a low-pressure space. In this embodiment, the first space (Si) is the space excluding the inside of the compression mechanism (15). The suction pipe (53) is connected to the body (17). Specifically, the suction pipe (53) penetrates the body (17) at a height between the electric motor (10) and the compression mechanism (15).

[0032] The discharge pipe (54) discharges the refrigerant compressed by the compression mechanism (15) to the outside of the casing (16). The discharge pipe (54) is connected to the body (17). Specifically, one end of the discharge pipe (54) is connected to the body (17) at a height lower than the compression mechanism (15).

[0033] The inlet pipe (55) introduces refrigerant at the suction pressure of the first space (Si) into the compression mechanism (15). Specifically, one end of the inlet pipe (55) is connected to the upper end plate (18). The other end of the inlet pipe (55) extends outside the casing (16) and then branches into two. One of the branched ends, the first outlet end, communicates with the first suction port (33) of the first compression mechanism (K1), which will be described later, and the other end, the second outlet end, communicates with the suction ports (33, 38) of the second compression mechanism (K2), which will be described later.

[0034] (2-2) Electric motor The electric motor (10) is located in the first space (Si). Specifically, the electric motor (10) is located in the upper part of the internal space of the casing (16). The electric motor (10) comprises a stator (11) and a rotor (12). The stator (11) is fixed to the body (17) of the casing (16). The rotor (12) is attached to the drive shaft (70) of the compression mechanism (15), which will be described later. The drive shaft (70) extends downward from the electric motor (10). The drive shaft (70) extends downward from the electric motor (10) so as to coincide with the cylindrical axis of the casing (16). The drive shaft (70) is rotated by the electric motor (10) around its axial direction. Details of the drive shaft (70) will be described later. (2-3) Compression mechanism The compression mechanism (15) shown in Figures 2, 3A, and 3B is a so-called oscillating roller type rotary fluid machine. The compression mechanism (15) is connected to the drive shaft (70). The compression mechanism (15) is driven by the drive shaft (70), compresses the refrigerant in the first space (Si), and discharges the compressed refrigerant from the discharge ports (24, 29).

[0035] The compression mechanism (15) of this embodiment is a two-cylinder rotary fluid machine comprising a first compression mechanism (K1) and a second compression mechanism (K2). The first compression mechanism (K1) and the second compression mechanism (K2) each include one cylinder (30, 35), one roller (40, 45), and one vane (41, 46). Each cylinder (30, 35) is provided with a pair of bushings (42, 47).

[0036] The compression mechanism (15) includes a front muffler (61), a front head (20), a first cylinder (30), a middle plate (50), a second cylinder (35), a rear head (25), and a rear muffler (63). Within the casing (16), the front muffler (61), front head (20), first cylinder (30), middle plate (50), second cylinder (35), rear head (25), and rear muffler (63) are arranged in order from top to bottom. The front head (20), first cylinder (30), middle plate (50), second cylinder (35), and rear head (25) are fastened to each other by several bolts (not shown). In the compression mechanism (15), the front head (20) is fixed to the body (17) of the casing (16).

[0037] (2-3-1) First compression mechanism and second compression mechanism The first compression mechanism (K1) comprises a first cylinder (30), a first roller (40), and a first vane (41). The second compression mechanism (K2) comprises a second cylinder (35), a second roller (45), and a second vane (46). In the compression mechanism (15), the first compression mechanism (K1) and the second compression mechanism (K2) are stacked vertically with a middle plate (50) in between. In this embodiment, the first compression mechanism (K1) and the second compression mechanism (K2) are identical except for the configuration of the intake ports (33, 38). The different configurations of the first compression mechanism (K1) and the second compression mechanism (K2) will be described later.

[0038] (2-3-2) Cylinder Two cylinders (30, 35) are housed inside the casing (16). Each cylinder (30, 35) is a thick-walled disc-shaped member. Each cylinder (30, 35) has an inner wall and vane housing holes (32, 37). The first cylinder (30) has a first intake port (33). The second cylinder (35) has a second intake port (38).

[0039] The thickness of the first cylinder (30) and the second cylinder (35) are equal. Although not shown in Figure 2, each cylinder (30, 35) has multiple through holes that penetrate through the thickness direction, such as through holes for inserting bolts for assembling the compression mechanism (15).

[0040] The cylinders (30, 35) are formed in an annular shape. The cylinders (30, 35) have an inner circumferential surface (31, 36) and an outer circumferential surface. The inner circumferential surfaces (31, 36) of the cylinders (30, 35) constitute the inner wall of the cylinders (30, 35). The inner circumferential surfaces (31, 36) of the cylinders constitute the cylinder chambers (S1, S2) described later. The inner circumferential surfaces (31, 36) of the cylinders (30, 35) have a first inner circumferential surface (31) formed on the first cylinder (30) and a second inner circumferential surface (36) formed on the second cylinder (35).

[0041] The vane housing holes (32,37) are holes that extend radially outward from the inner circumferential surface (31,36) of the cylinder (30,35). These vane housing holes (32,37) penetrate the cylinder (30,35) in the thickness direction. The vane housing hole (32,37) of the first cylinder (30) is the first vane housing hole (32). The vane housing hole (32,37) of the second cylinder (35) is the second vane housing hole (37).

[0042] The vane housing holes (32, 37) constitute vane chambers (48, 49) that house the vanes (41, 46). The vane chambers (48, 49) are formed inside the cylinders (30, 35). Specifically, the vane chambers (48, 49) have a first vane chamber (48) and a second vane chamber (49). The first vane chamber (48) houses the first vane (41). The first vane chamber (48) is a space partitioned by the inner wall surface of the first vane housing hole (32), the front head (20), and the middle plate (50). The second vane chamber (49) houses the second vane (46). The second vane chamber (49) is a space partitioned by the inner wall surface of the second vane housing hole (37), the middle plate (50), and the rear head (25).

[0043] In Figure 3, the first inhalation port (33) is located to the right of the first vane housing hole (32), and the second inhalation port (38) is located to the right of the second vane housing hole (37). Each inhalation port (33, 38) communicates with the inhalation-side space (Ss), which will be described later.

[0044] (2-3-3) Front Head The front head (20) shown in Figure 2 is a member that closes the end face of the first cylinder (30) on the motor (10) side (the upper end face of the first cylinder (30) in Figure 1). The front head (20) comprises a main body (21), a main bearing portion (22), and an outer peripheral wall portion (23). The main body (21), the main bearing portion (22), and the outer peripheral wall portion (23) are integrally molded. The front head (20) is an example of a first end plate (20) that closes one end of the cylinder (30, 35) in the axial direction.

[0045] The main body (21) is formed in a generally circular, thick plate shape. The main body (21) is positioned to cover the end face of the first cylinder (30). The lower surface of the main body (21) is in close contact with the first cylinder (30). The main bearing portion (22) is formed in a cylindrical shape extending from the main body (21) toward the electric motor (10) side (upper side in Figure 1). The main bearing portion (22) is positioned in the center of the main body (21). The main bearing portion (22) constitutes a journal bearing that supports the drive shaft (70) of the compression mechanism (15). The outer peripheral wall portion (23) is a thick, annular portion formed continuously with the outer peripheral edge of the main body (21).

[0046] A first discharge port (24) is formed in the front head (20). The first discharge port (24) is an example of a discharge port (24, 29) of this disclosure. The first discharge port (24) discharges the refrigerant compressed in the first cylinder (30). The first discharge port (24) penetrates the main body (21) of the front head (20) in the thickness direction. The first discharge port (24) is positioned to the side of the first vane housing hole (32). A discharge valve (not shown) for opening and closing the first discharge port (24) is provided in the main body (21) of the front head (20).

[0047] (2-3-4) Rear Head The rear head (25) shown in Figure 2 is a member that closes the end face of the second cylinder (35) on the side opposite to the electric motor (10) (the lower end face of the second cylinder (35) in Figure 1). The rear head (25) comprises a main body (26), a sub-bearing portion (27), and an outer peripheral wall portion (28). The rear head (25) is an example of a second end plate (25) that closes the other end of the cylinder (30, 35) in the direction of the cylinder axis.

[0048] The main body (26) is formed in a generally circular, thick plate shape. The main body (26) is positioned to cover the end face of the second cylinder (35). The upper surface of the main body (26) is in close contact with the second cylinder (35). The sub-bearing portion (27) is formed in a cylindrical shape extending from the main body (26) to the side opposite to the second cylinder (35) (the lower side in Figure 2). The sub-bearing portion (27) is positioned in the center of the main body (26). The sub-bearing portion (27) constitutes a journal bearing that supports the drive shaft (70) of the compression mechanism (15). The outer peripheral wall portion (28) is formed in a cylindrical shape extending from the outer peripheral edge of the main body (26) to the side opposite to the second cylinder (35).

[0049] A second discharge port (29) is formed in the rear head (25). The second discharge port (29) is an example of a discharge port (24, 29) in this disclosure. The second discharge port (29) discharges the refrigerant compressed by the second cylinder (35). The second discharge port (29) penetrates the main body (26) of the rear head (25) in the thickness direction. The second discharge port (29) is located to the left of the second vane housing hole (37). A discharge valve (not shown) for opening and closing the second discharge port (29) is provided in the main body (26) of the rear head (25).

[0050] (2-3-5) Middle Plate The middle plate (50) shown in Figure 2 is positioned so as to be sandwiched between the first cylinder (30) and the second cylinder (35). The middle plate (50) is in close contact with the lower end surface of the first cylinder (30) and the upper end surface of the second cylinder (35).

[0051] A central hole (51) is formed in the center of the middle plate (50), penetrating the middle plate (50) in the thickness direction. The intermediate connecting portion (78) of the drive shaft (70), which will be described later, is inserted through the central hole (51) of the middle plate (50).

[0052] (2-3-6) Front muffler and rear muffler The front muffler (61) shown in Figure 2 is positioned above the front head (20) so as to cover the first discharge port (24). The front muffler (61) is an example of the muffler portion (61) of this disclosure. A front muffler chamber (62) is formed between the front muffler (61) and the front head (20). The front muffler chamber (62) is a muffler chamber (62, 64) into which the refrigerant discharged from the first discharge port (24) flows. Thus, the front muffler chamber (62) is provided on the first end plate (20). A high-pressure gas space (HS) is formed in the front muffler chamber (62) by the discharged refrigerant flowing in from the first discharge port (24).

[0053] The rear muffler (63) shown in Figure 2 is positioned below the rear head (25) so as to cover the second discharge port (29). The rear muffler (63) is an example of the muffler portion (63) of this disclosure. A rear muffler chamber (64) is formed between the rear muffler (63) and the rear head (25). The rear muffler chamber (64) is a muffler chamber (62,64) into which the refrigerant discharged from the second discharge port (29) flows. Thus, the rear muffler chamber (64) is provided on the second end plate (25). A high-pressure gas space (HS) is formed in the rear muffler chamber (64) by the discharged refrigerant flowing in from the second discharge port (29).

[0054] (2-3-7) Drive shaft As shown in Figures 2 and 3, the drive shaft (70) is a component that drives the rollers (40, 45) described later. Specifically, the drive shaft (70) comprises a main shaft portion (72), a first eccentric portion (75), an intermediate connecting portion (78), a second eccentric portion (76), and a sub-shaft portion (74) (see Figure 1). The rotational axis (70a) of the drive shaft (70) substantially coincides with the cylindrical axis of each cylinder (30, 35).

[0055] In the drive shaft (70), the main shaft portion (72), the first eccentric portion (75), the intermediate connecting portion (78), the second eccentric portion (76), and the sub-shaft portion (74) are arranged in order from top to bottom. In the drive shaft (70), the main shaft portion (72), the first eccentric portion (75), the intermediate connecting portion (78), the second eccentric portion (76), and the sub-shaft portion (74) are integrally formed with each other.

[0056] The main shaft (72) and the secondary shaft (74) are columnar or rod-shaped portions with a circular cross-section. The rotor (12) of the electric motor (10) is attached to the upper part of the main shaft (72). The lower part of the main shaft (72) forms a journal supported by the main bearing portion (22) of the front head (20). The secondary shaft (74) forms a journal supported by the secondary bearing portion (27) of the rear head (25). The central axis of the main shaft (72) and the central axis of the secondary shaft (74) coincide with the rotational axis (70a) of the drive shaft (70).

[0057] Each eccentric portion (75, 76) is a cylindrical part with a larger diameter than the main shaft portion (72). The central axis of each eccentric portion (75, 76) is eccentric with respect to the rotation axis (70a) of the drive shaft (70). The first eccentric portion (75) is eccentric with respect to the rotation axis (70a) of the drive shaft (70) in the opposite direction to the second eccentric portion (76). In other words, the direction of eccentricity of the first eccentric portion (75) with respect to the rotation axis (70a) of the drive shaft (70) is 180° different from the direction of eccentricity of the second eccentric portion (76) with respect to the rotation axis (70a) of the drive shaft (70).

[0058] The eccentricity e1 of the first eccentric part (75) and the eccentricity e2 of the second eccentric part (76) are equal to each other. The eccentricity e1 of the first eccentric part (75) is the distance between the central axis (75a) of the first eccentric part (75) and the rotational axis (70a) of the drive shaft (70). The eccentricity e2 of the second eccentric part (76) is the distance between the central axis (76a) of the second eccentric part (76) and the rotational axis (70a) of the drive shaft (70).

[0059] The outer diameter of the first eccentric section (75) is equal to the outer diameter of the second eccentric section (76). The heights (vertical lengths) of the first eccentric section (75) and the second eccentric section (76) are substantially equal to each other.

[0060] The intermediate connecting section (78) is positioned between the first eccentric section (75) and the second eccentric section (76), and connects the first eccentric section (75) and the second eccentric section (76).

[0061] (2-3-8) Laura Eccentrically rotating rollers (40, 45) are arranged in the space surrounded by the inner circumferential surfaces (31, 36) of the cylinders (30, 35). The space surrounded by the inner circumferential surfaces (31, 36) of the cylinders (30, 35) and the rollers (40, 45) form cylinder chambers (S1, S2). The rollers (40, 45) consist of a first roller (40) and a second roller (45). The first roller (40) and the second roller (45) are identical in shape, dimensions, and material. Each roller (40, 45) is a slightly thick-walled cylindrical member. The first roller (40) is arranged in the first cylinder (30). The second roller (45) is arranged in the second cylinder (35).

[0062] The cylinder chamber (S1, S2) comprises a first cylinder chamber (S1) and a second cylinder chamber (S2). The first cylinder chamber (S1) is a space partitioned by a first roller (40), a first inner surface (31), a front head (20), and a middle plate. The second cylinder chamber (S2) is a space partitioned by a second roller (45), a second inner surface (36), a middle plate (50), and a rear head.

[0063] The first eccentric portion (75) of the drive shaft (70) is inserted through the first roller (40). The first roller (40) rotates eccentrically as the first eccentric portion (75) of the drive shaft (70) rotates.

[0064] The outer circumferential surface of the first roller (40) slides against the first inner circumferential surface (31). The upper surface of the first roller (40) slides against the lower surface of the main body (21) of the front head (20). The lower surface of the first roller (40) slides against the upper surface of the middle plate (50).

[0065] The second eccentric portion (76) of the drive shaft (70) is inserted through the second roller (45). The second roller (45) rotates eccentrically as the second eccentric portion (76) of the drive shaft (70) rotates.

[0066] The outer surface of the second roller (45) slides against the second inner surface (36). The lower surface of the second roller (45) slides against the upper surface of the main body (21) of the rear head (25). The upper surface of the second roller (45) slides against the lower surface of the middle plate (50).

[0067] (2-3-9) Bane As shown in Figure 3, the first vane (41) and the second vane (41) are slightly thick rectangular flat members. The thickness of each vane (41, 46) in the vertical direction (in the direction of the drive shaft (70)) is the same as the thickness of the rollers (40, 45) in the vertical direction. Each vane (41, 46) is inserted into the vane chambers (48, 49) and divides the cylinder chambers (S1, S2) into an intake side space (Ss) and a discharge side space (Sd).

[0068] Specifically, the first vane (41) is formed integrally with the first roller (40). The first vane (41) extends radially outward from the outer surface of the first roller (40). This radially outer end of the first vane (41) is sometimes referred to as the tip of the first vane (41). The first vane (41) is positioned such that its tip is contained within the first vane chamber (48). The first vane (41) divides the first cylinder chamber (S1) into an intake-side space (Ss) and a discharge-side space (Sd). The intake-side space (Ss) of the first cylinder chamber (S1) communicates with the first intake port (33). The discharge-side space of the second cylinder chamber (S2) communicates with the first discharge port (24).

[0069] The second vane (46) is formed integrally with the second roller (45). The second vane (46) extends radially outward from the outer surface of the second roller (45). The radially outer end of the second vane (46) is sometimes referred to as the tip of the second vane (46). The second vane (46) is positioned such that its tip is contained within the second vane chamber (49). The second vane (46) divides the second cylinder chamber (S2) into an intake-side space (Ss) and a discharge-side space (Sd). The intake-side space (Ss) of the second cylinder chamber (S2) communicates with the second intake port (38). The discharge-side space of the second cylinder chamber (S2) communicates with the second discharge port (29).

[0070] (2-3-10) Bush Cylinders (30, 35) are provided with bushes (42, 47). The bushes (42, 47) are a pair of plate-shaped semicircular members that face each other with a vane (41, 46) in between. The flat surfaces of the pair of semicircular members sandwich the vane (41, 46). The bushes (42, 47) have a first bush (42) and a second bush (47). The first bush (42) is provided in the first cylinder (30). The second bush (47) is provided in the second cylinder (35).

[0071] The first bush (42) supports the first vane (41). The first vane (41) is supported by the first cylinder (30) via the first bush (42) so as to be able to swing and move back and forth. As a result, the first roller (40) is configured as a swing-type roller that revolves along the inner wall surface of the first cylinder (30) as the drive shaft (70) rotates, while swinging relative to the central axis (75a) of the first eccentric part (75).

[0072] The second bush (47) supports the second vane (46). The second vane (46) is supported by the second cylinder (35) via the second bush (47) so as to be able to swing and move back and forth. As a result, the second roller (45) is configured as a swinging roller that revolves along the inner wall surface of the second cylinder (35) as the drive shaft (70) rotates, while swinging relative to the central axis (76a) of the second eccentric part (76).

[0073] (3) Operation of the compressor The operation of the compressor (1) will be explained with reference to Figure 4. When the electric motor (10) drives the drive shaft (70), each roller (40, 45) of the compression mechanism (15) is driven by the drive shaft (70). Each roller (40, 45) is periodically displaced within the corresponding cylinder (30, 35) each time the drive shaft (70) rotates, as shown in Figure 5. In the rotary compressor (1), the first compression mechanism (K1) and the second compression mechanism (K2) of the compression mechanism (15) each perform the processes of drawing in, compressing, and discharging refrigerant.

[0074] (4) Operation of the compression mechanism As described above, in the compression mechanism (15) of this embodiment, the eccentric directions of each roller (40, 45) in the first compression mechanism (K1) and the second compression mechanism (K2) are different from each other. Specifically, the eccentric direction of the first roller (40) with respect to the rotational axis (70a) of the drive shaft (70) is 180° different from the eccentric direction of the second roller (45) with respect to the rotational axis (70a) of the drive shaft (70). Therefore, the displacement period of the first roller (40) and the displacement period of the second roller (45) are shifted by 180° (i.e., half a period).

[0075] In each cylinder (30, 35), the volume of the suction side space (Ss) and discharge side space (Sd) of the cylinder chamber (S1, S2) changes as the roller (40, 45) is displaced. As a result, each cylinder (30, 35) performs an intake stroke in which refrigerant is drawn into the cylinder chamber (S1, S2) from the intake port (33, 38), a compression stroke in which the refrigerant drawn into the cylinder chamber (S1, S2) is compressed, and a discharge stroke in which the compressed refrigerant is discharged from the discharge port (24, 29).

[0076] The operation of the first compression mechanism (K1) and the second compression mechanism (K2) will be described below. Note that the angles shown in Figure 5 are defined as follows: 0° is the rotation angle of the drive shaft (70) when the first vane (41) of the first compression mechanism (K1) is furthest back from the first cylinder (30), and 180° is the rotation angle of the drive shaft (70) when the first vane (41) of the first compression mechanism (K1) is furthest inside the first cylinder (30).

[0077] (4-1) Operation of the first compression mechanism In the first compression mechanism (K1), when the drive shaft (70) rotates slightly clockwise as shown in Figure 5 from a rotation angle of 0°, the contact point between the first roller (40) and the first cylinder (30) passes through the first suction port (33). At this time, the suction of refrigerant into the suction side space (Ss) of the first cylinder (30) (suction process) begins.

[0078] As the rotation angle of the drive shaft (70) increases, the volume of the intake space (Ss) gradually increases, and the amount of refrigerant drawn into the intake space (Ss) increases. The intake stroke continues until the rotation angle of the drive shaft (70) reaches 360°, after which the process transitions to the compression stroke and the discharge stroke.

[0079] When the drive shaft (70) rotates slightly from a rotation angle of 0°, the contact point between the first roller (40) and the first cylinder (30) passes through the first intake port (33) again. At this point, the refrigerant is contained in the intake space (Ss). Subsequently, the intake space (Ss), which was connected to the first intake port (33), becomes the discharge space (Sd), which is connected only to the first discharge port (24).

[0080] From this state, compression of the refrigerant in the discharge-side space (Sd) begins. As the rotation angle of the drive shaft (70) increases, the volume of the discharge-side space (Sd) decreases and the pressure in the discharge-side space (Sd) increases. When the pressure in the discharge-side space (Sd) exceeds a predetermined pressure, the discharge valve opens. At this time, the refrigerant in the discharge-side space (Sd) is discharged from the first discharge port (24) to the outside of the compression mechanism (15).

[0081] The compression and discharge strokes continue until the rotation angle of the drive shaft (70) reaches 360°, after which the suction stroke begins. In this way, the refrigerant compression operation is continuously performed in the first compression mechanism (K1) by repeating the series of strokes: the suction stroke, the compression stroke, and the discharge stroke.

[0082] (4-2) Operation of the second compression mechanism In the second compression mechanism (K2), when the drive shaft (70) rotates slightly clockwise as shown in Figure 5 from a rotation angle of 180°, the contact point between the second roller (45) and the second cylinder (35) passes through the second suction port (38). At this time, the suction of refrigerant into the suction side space (Ss) of the second cylinder (35) (suction stroke) begins.

[0083] As the rotation angle of the drive shaft (70) increases, the volume of the suction side space (Ss) gradually increases, and the amount of refrigerant drawn into the suction side space (Ss) increases. This refrigerant intake stroke continues until the rotation angle of the drive shaft (70) reaches the next 180°, after which the process transitions to the compression stroke and discharge stroke.

[0084] When the drive shaft (70) rotates slightly from its 180° rotation angle, the contact point between the second roller (45) and the second cylinder (35) passes through the second intake port (38) again. At this point, the refrigerant is contained in the intake space (Ss), and the intake space (Ss), which was connected to the first intake port (33), becomes the discharge space (Sd), which is connected only to the second discharge port (29).

[0085] From this state, compression of the refrigerant in the discharge-side space (Sd) begins. As the rotation angle of the drive shaft (70) increases, the volume of the discharge-side space (Sd) decreases and the pressure in the discharge-side space (Sd) increases. When the pressure in the discharge-side space (Sd) exceeds a predetermined pressure, the discharge valve opens. At this time, the refrigerant in the discharge-side space (Sd) is discharged out of the compression mechanism (15) from the second discharge port (29).

[0086] The compression and discharge strokes continue until the rotation angle of the drive shaft (70) reaches the next 180°, after which the suction stroke begins. In this way, the refrigerant compression operation is continuously performed in the second compression mechanism (K2) by repeating the series of strokes of the suction stroke, compression stroke, and discharge stroke.

[0087] (5)Oil separator As shown in Figure 2, the rotary compressor (1) of this embodiment has an oil separator (80) for separating refrigerant oil from the refrigerant in the compressor (1). Here, a portion of the refrigerant exists in the compressor (1) mixed with the refrigerant oil. The oil separator (80) separates the refrigerant oil from the mixed fluid in which the refrigerant oil and refrigerant are mixed. The separated refrigerant oil is supplied to a predetermined part of the compression mechanism (15). In this embodiment, the refrigerant oil separated in the oil separator (80) is supplied into the vane chambers (48, 49). For convenience, below, "separating refrigerant oil from the mixed fluid" may be referred to as "separating refrigerant oil from the refrigerant."

[0088] The oil separator (80) is located below the rear muffler (63). The oil separator (80) has a housing (81) and an oil separation mechanism (82) located inside the housing (81).

[0089] The housing (81) is formed in a generally cylindrical shape. The inside of the housing (81) is into which the refrigerant discharged from the first discharge port (24) and the second discharge port (29) flows, and is also in communication with the vane chambers (48, 49). As a result, a high-pressure gas space (HS) is formed inside the housing (81). A gas inlet (83) and a gas outlet (84) are formed in the housing (81).

[0090] The gas inlet (83) is the inlet through which the refrigerant compressed by the compression mechanism (15) flows into the housing (81). The gas inlet (83) communicates with the first discharge port (24) and the second discharge port (29). The gas inlet (83) communicates with the downstream end of the discharge gas passage (91).

[0091] The gas outlet (84) is the outlet through which the refrigerant inside the housing (81) flows out of the housing (81). The gas outlet (84) is in communication with the discharge pipe (54).

[0092] An oil reservoir (85) for storing refrigerant oil is formed inside the housing (81). The oil reservoir (85) is formed at the bottom of the housing (81). The bottom of the casing (16) has an inclined tapered surface (81a). As a result, the refrigerant oil in the oil reservoir (85) collects at the lower end of the tapered surface (81a). Specifically, an oil supply passage (90) is connected to the housing (81) to supply refrigerant oil from the oil reservoir (85) to each vane chamber, and the inlet end of the oil supply passage (90) is located in the oil reservoir (85). The tapered surface (81a) slopes downwards towards the inlet end of the oil supply passage (90).

[0093] The oil separation mechanism (82) separates the refrigerant discharged from the discharge ports (24, 29) from the refrigerant oil. In this embodiment, the oil separation mechanism (82) is a mesh member. The mesh member separates the refrigerant from the refrigerant oil as the refrigerant gas passes through it. The mesh member is provided inside the housing (81) from the gas inlet (83) to the gas outlet (84). This allows the refrigerant oil to be separated from the refrigerant as it travels from the gas inlet (83) to the gas outlet (84) inside the housing (81).

[0094] (6) Discharge gas passage and oil supply passage The discharge gas passage (91) indicated by the dashed arrow in Figure 2 is a connecting passage (91) that links the first discharge port (24) and the second discharge port (29). Specifically, the discharge gas passage (91) penetrates the first cylinder (30), the middle plate (50), the second cylinder (35), and the rear muffler (63) in the vertical direction.

[0095] The oil supply passage (90) is a passage that connects the oil reservoir (85) and each vane chamber (48, 49). The oil supply passage (90) penetrates the rear muffler (63), rear head (25), and middle plate (50) in the vertical direction (indicated by the dashed arrow in Figure 2). The outlet end of the oil supply passage (90) communicates with the first vane chamber (48) in the first cylinder (30) and with the second vane chamber (49) in the second cylinder (35). The inlet end of the oil supply passage (90) is located within the oil reservoir (85).

[0096] (7) Flow of discharged refrigerant and refrigerant oil The high-pressure refrigerant discharged from the first outlet (24) to the front muffler chamber (62) flows through the discharge gas passage (91) toward the rear muffler chamber. The high-pressure refrigerant in the discharge gas passage (91) merges with the high-pressure refrigerant discharged from the second outlet (29) in the rear muffler chamber (64) (see dashed arrow in Figure 2).

[0097] The high-pressure refrigerant that flows from the rear muffler (63) through the gas inlet (83) into the oil separator (80) flows through the housing (81) toward the gas outlet (84). Inside the housing (81), refrigerant oil is separated from the high-pressure refrigerant as it passes through the oil separation mechanism (82). The high-pressure refrigerant flows into the discharge pipe (54) through the gas outlet (84). The refrigerant oil separated from the refrigerant falls to the bottom of the housing (81) and is stored in the oil reservoir (85).

[0098] Because the space inside the housing (81) is under high pressure due to the discharged refrigerant, the refrigerant oil in the oil reservoir flows into the oil supply passage (90) toward the vane chambers (48, 49) where the pressure is lower. The refrigerant oil that flows into the oil supply passage (90) rises up the oil supply passage (90) (dotted arrow in Figure 2) and is transported to the second vane chamber (49) and the first vane chamber (48), respectively. The refrigerant oil that flows into the second vane chamber (49) is supplied to the sliding part where the second bush (47) and the second vane (46) are in contact. The refrigerant oil that flows into the first vane chamber (48) is supplied to the sliding part where the first bush (42) and the first vane (41) are in contact.

[0099] (8) Characteristics (8-1) Feature 1 In the rotary compressor (1) of this embodiment, the casing (16) has an oil reservoir (85) for storing refrigerant oil and a high-pressure gas space (HS) into which refrigerant discharged from the discharge ports (24, 29) flows and which communicates with each vane chamber (48, 49). An oil separation mechanism (82) for separating the refrigerant discharged from the discharge ports (24, 29) from the refrigerant oil is arranged in the high-pressure gas space (HS). In addition, since the oil separation mechanism (82) does not need to be installed outside the casing (16), the number of parts can be kept down and damage to the refrigerant oil flow path due to vibration of the rotary compressor can be suppressed.

[0100] According to this embodiment, since the oil separation mechanism (82) is located inside the casing (16), the distance from the oil separation mechanism (82) to the oil reservoir (85) can be shortened. This eliminates the need for pipes to transport the refrigerant oil separated by the oil separation mechanism (82) to the oil reservoir (85). Even if pipes to transport the refrigerant oil are installed, these pipes can be shortened, thus suppressing a reduction in the amount of oil supplied to the vane chambers (48, 49).

[0101] (8-2) Feature 2 In the rotary compressor (1) of this embodiment, the oil reservoir (85) is formed in the high-pressure gas space (HS). The rotary compressor (1) further includes an oil supply passage (90) for supplying refrigerant oil from the oil reservoir (85) to the vane chambers (48, 49).

[0102] According to this embodiment, a high-pressure gas space (HS) for supplying refrigerant oil to the vane chambers (48, 49) is formed within the casing (16), allowing the oil supply passage (90) from the oil reservoir (85) to the vane chambers (48, 49) to be shortened. This reduces flow resistance within the oil supply passage (90), thereby suppressing a decrease in the amount of oil supplied to the vane chambers (48, 49). If the diameter of the oil supply passage (90) were increased to reduce flow resistance, the amount of oil required to fill the compressor would increase accordingly, and the amount of refrigerant dissolved in the refrigerant oil would also increase, thus increasing the required amount of refrigerant to fill. However, since the oil supply passage (90) can be shortened, there is no need to increase the pipe diameter, and as a result, increases in both the amount of oil and refrigerant to fill can be suppressed.

[0103] (8-3) Feature 3 The oil reservoir (85) in this embodiment is located at the bottom of the high-pressure gas space (HS). The rotary compressor (1) is equipped with an oil supply passage (90) that supplies refrigerant oil from the oil reservoir (85) to each vane chamber (48, 49). The bottom of the high-pressure gas space (HS) has a tapered surface (81a) that slopes downward towards the inlet end of the oil supply passage (90).

[0104] According to this embodiment, the inlet of the oil supply passage (90) is located in the oil reservoir (85). Since the bottom surface of the oil reservoir (85) is formed to slope toward the oil supply passage (90), the refrigerant oil tends to collect at the inlet of the oil supply passage (90). This makes it easier for the refrigerant oil in the oil reservoir (85) to flow into the oil supply passage (90).

[0105] (8-4) Feature 4 The oil separation mechanism (82) in this embodiment is a mesh member that separates the refrigerant from the refrigerant oil as the refrigerant gas passes through it. Since it only requires providing the mesh member in the housing (81), the refrigerant and refrigerant oil can be separated with a relatively simple mechanism. The cost of the oil separation mechanism (82) can be reduced.

[0106] (8-5) Feature 5 The rotary compressor (1) of this embodiment has a two-cylinder compression mechanism (15), and further has a connecting passage (91) provided in the compression mechanism (15) that connects a first discharge port (24) for discharging refrigerant compressed in the first cylinder (30) and a second discharge port (29) for discharging refrigerant compressed in the second cylinder (35). The connecting passage (91) supplies the discharged refrigerant to the oil separation mechanism (82).

[0107] According to this embodiment, even in a two-cylinder rotary compressor, the effects described in features 1 and 2 can be obtained with a single oil separation mechanism (82) by providing a connecting passage (91).

[0108] (8-6) Feature 6 The refrigeration cycle device (100) is equipped with the rotary compressor of this embodiment. A refrigeration cycle device can be provided that is equipped with a rotary compressor (1) having an oil separation mechanism (82) inside the casing (16). Since the space required for the oil separator (80) within the refrigeration cycle device (100) is eliminated, the refrigeration cycle device (100) can be made more compact.

[0109] (9) Variant A modified version of the rotary compressor (1) of the above embodiment will be described below. The following describes a configuration that differs from the rotary compressor (1) of the above embodiment.

[0110] (9-1) Variation 1 In the rotary compressor (1) of Modification 1 shown in Figures 5 and 6, the oil separation mechanism (82) is located in the rear muffler chamber (64). The discharge pipe (54) is provided to communicate directly with the rear muffler (63).

[0111] The discharge gas passage (91) is formed to extend from the front muffler chamber (62) to the rear muffler chamber (64), passing through each cylinder (30, 35) and the middle plate in the vertical direction. The high-pressure gas space (HS) includes the rear muffler chamber (64).

[0112] The oil separation mechanism (82) is located in the rear muffler chamber (64) (dotted area in Figure 6). In modified example 1, the refrigerant and refrigerant oil are separated in the rear muffler chamber (64). An oil reservoir (85) is formed in the rear muffler chamber (64). The refrigerant oil is stored in the rear muffler (63).

[0113] The oil supply passage (90) connects the rear muffler chamber (64) and each vane chamber (48, 49). The inlet (83) of the oil supply passage (90) is located in the oil reservoir (85) of the rear muffler chamber (64).

[0114] The high-pressure refrigerant discharged from the first outlet (24) into the front muffler chamber (62) flows downward through the discharge gas passage (91) (dashed arrow in Figure 5) and merges with the high-pressure refrigerant discharged from the second outlet (29) in the rear muffler chamber (64). In the rear muffler chamber (64), the refrigerant gas and refrigerant oil are separated by the oil separation mechanism (82). The refrigerant gas flows out into the discharge pipe (54) (dashed arrow in Figure 6), while the refrigerant oil stored in the oil reservoir (85) flows into the oil supply passage (90) (dotted arrow in Figure 6). Subsequently, the refrigerant oil flows upward through the oil supply passage (90) (dotted arrow in Figure 5) and is supplied to the first vane chamber (48) and the second vane chamber (49), respectively.

[0115] Thus, in the rotary compressor (1) of the modified example 1, the oil separation mechanism (82) is located in the rear muffler chamber (64), which suppresses interference with the opening and closing of the discharge valve of the second discharge port (29) by the separated refrigerant oil. This suppresses a decrease in the compression efficiency of the rotary compressor (1). In addition, by having the rear muffler chamber (64) also serve as the housing space for the oil separation mechanism (82), it is possible to reduce the amount of refrigerant charged into the refrigerant circuit (9).

[0116] (9-2) Modification example 2 In the rotary compressor (1) of modified example 2 shown in Figures 7 and 8, the oil separation mechanism (82) is located in the front muffler chamber (62). The discharge pipe (54) is provided to communicate directly with the front muffler chamber (62).

[0117] The discharge gas passage (91) is formed to extend from the rear muffler chamber (64) to the front muffler chamber (62), passing through each cylinder (30, 35) and the middle plate in the vertical direction. The high-pressure gas space (HS) includes the front muffler chamber (62).

[0118] The oil separation mechanism (82) is located in the front muffler chamber (62). In modified example 2, the refrigerant and refrigerant oil are separated in the front muffler chamber (62). An oil reservoir (85) is formed in the front muffler chamber (62).

[0119] The oil supply passage (90) connects the front muffler chamber (62) and each vane chamber (48, 49). The inlet (83) of the oil supply passage (90) is located in the oil reservoir (85) of the front muffler chamber (62).

[0120] The high-pressure refrigerant discharged from the first discharge port (24) and the second discharge port (29) merge in the front muffler chamber (62). In the front muffler chamber (62), the refrigerant gas and refrigerant oil are separated by the oil separation mechanism (82). The refrigerant gas flows out into the discharge pipe (54), while the refrigerant oil is stored in the oil reservoir (85). The refrigerant oil in the oil reservoir (85) flows into the oil supply passage (90) and is supplied sequentially to the first vane chamber (48) and the second vane chamber (49).

[0121] As described above, in the modified example 3, the oil separation mechanism (82) is located in the front muffler chamber (62), making it easier for the separated refrigerant oil to be supplied to the vane chambers (48, 49) by its own weight. This improves the efficiency of oil supply to the vane chambers (48, 49).

[0122] (9-3) Modification 3 The rotary compressor (1) of Modification 3 differs from the rotary compressor (1) of Modification 1 in the arrangement of the oil separation mechanism (82). Specifically, as shown in Figures 9 and 10, the oil separation mechanism (82) is located inside the second cylinder (35). The discharge pipe (54) is provided to communicate with the rear muffler chamber (64).

[0123] The second cylinder (35) has a larger diameter than the first cylinder (30). The second cylinder (35) is radially thicker than the first cylinder (30). A high-pressure gas space (HS) is formed in the second cylinder (35). The high-pressure gas space (HS) is formed around the cylinder chambers (S1, S2). The high-pressure gas space (HS) is formed in an arc shape so as to extend in the circumferential direction of the cylinders (30, 35). Near one end of the high-pressure gas space (HS), a gas inlet (83) is formed that communicates with the discharge gas passage (91). At the other end of the high-pressure gas space (HS), a gas outlet (84) is formed that communicates with the discharge pipe (54) connected to the rear head (25). Thus, a gas inlet (83) is formed near one end of the arc-shaped high-pressure gas space (HS), and a gas outlet (84) is provided at the other end. The gas inlet (83) is positioned within a range of 90° to 150° from the gas outlet (84) in the circumferential direction of the casing (16) with respect to the drive shaft (70).

[0124] The oil separation mechanism (82) is located in the high-pressure gas space (HS) of the second cylinder (35). The oil separation mechanism (82) is provided to extend in the longitudinal direction (circumferential direction) of the high-pressure gas space (HS). The oil supply passage (90) is formed at the other end of the high-pressure gas space (HS) and near the gas outlet (84). In the second cylinder (35), a portion of the oil supply passage (90) connects the high-pressure gas space (HS) and the second vane chamber (49).

[0125] The high-pressure refrigerant discharged from the first discharge port (24) into the front muffler chamber (62) flows into the discharge gas passage (91) and merges with the high-pressure refrigerant discharged from the second discharge port (29) in the rear muffler chamber. The merged high-pressure refrigerant flows into the high-pressure gas space (HS) where it is separated into refrigerant and refrigerant oil. The refrigerant flows into the discharge pipe (54) via the gas outlet (84), and the refrigerant oil flows into the second vane chamber (49). A portion of the refrigerant oil that flows into the second vane chamber (49) flows into the second bush (47), and the remainder flows upward through the oil supply passage (90) into the first vane chamber (48). The refrigerant oil that flows into the first vane chamber (48) is supplied to the first bush (42).

[0126] In this way, by providing an oil separation mechanism (82) inside the cylinders (30, 35), the flow path length of the oil supply passage (90) that communicates with each vane chamber (48, 49) can be shortened.

[0127] (9-4) Modification 4 The rotary compressor (1) of Modification 4 shown in Figures 11 and 12 has a high-pressure gas space (HS) in the space below the casing (16). The rotary compressor (1) has a partition plate (95) that partitions the high-pressure gas space (HS). The partition plate (95) is located below the compression mechanism (15). The partition plate (95) is provided so as to close the upper part of the lower end plate (19). The high-pressure gas space (HS) is the space enclosed by the lower end plate (19) and the partition plate (95).

[0128] The discharge pipe (54) communicates with the high-pressure gas space (HS). The discharge pipe (54) is provided so as to penetrate the side of the lower end plate (19).

[0129] The discharge gas passage (91) is provided to extend from the front muffler chamber (62) to the high-pressure gas space (HS), passing through the first cylinder (30), middle plate (50), second cylinder (35), rear head (25), rear muffler (63), and partition plate (95). The discharge gas passage (91) has a discharge gas pipe (91a) that passes through the rear muffler (63) and the partition plate (95).

[0130] The oil separation mechanism (82) is located in the space below the partition plate (95). The oil reservoir (85) is formed at the bottom of the casing (16).

[0131] The oil supply passage (90) has a first passage (90a) and a second passage (90b). The first passage (90a) and the second passage (90b) are connected in order in the direction of the refrigeration oil flow. The first passage (90a) is provided outside the casing (16). The inlet end of the first passage (90a) is connected to the lower end plate (19). The inlet of the first passage (90a) is connected to the lowest part of the oil reservoir (85). The outlet end of the first passage (90a) penetrates the body (17) from the radially outer to the inward direction and is connected to the rear head (25). The second passage (90b) is formed to penetrate the rear head (25), the second cylinder (35), the middle plate (50), and the first cylinder (30) in the vertical direction. The second channel (90b) communicates with the first vane chamber (48) and the second vane chamber (49).

[0132] The high-pressure refrigerant discharged from the first discharge port (24) and the second discharge port (29) flows into the high-pressure gas space (HS) via the discharge gas passage (91). In the high-pressure gas space (HS), the refrigerant gas and refrigerant oil are separated by the oil separation mechanism (82). The refrigerant gas flows out into the discharge pipe (54), while the refrigerant oil is stored in the oil reservoir (85). The refrigerant oil in the oil reservoir (85) flows into the first flow path (90a), and then flows out from the first flow path (90a) to the rear head (25). The refrigerant oil that has flowed into the rear head (25) rises up the second flow path (90b). At this time, the refrigerant oil is supplied sequentially to the second vane chamber (49) and the first vane chamber (48).

[0133] Thus, in Modification 4, the compressor (1) is made into a high- and low-pressure dome, and by placing the oil separator (80) in the high-pressure gas space (HS), refrigerant gas leakage from the high-pressure gas space (HS) to the low-pressure space can be suppressed. In addition, by installing the oil supply passage (90) outside the casing (16), the flexibility of the compressor (1)'s installation can be improved.

[0134] (9-5) Variation 5 The rotary compressor (1) of Modification 5 shown in Figure 13 differs from the rotary compressor (1) of Modification 4 in only the configuration of the oil supply passage (90). The first passage (90a) of the oil supply passage (90) in Modification 5 is provided inside the casing (16). The first passage (90a) is provided so as to penetrate the partition plate (95) and the rear muffler (63). In Modification 5, the length of the oil supply passage (90) can be shortened by providing the oil supply passage (90) to penetrate the partition plate (95).

[0135] (10) Other embodiments The rotary compressor (1) of the above embodiment and each of the above modifications may be configured as follows.

[0136] In the modified example 3, the oil separation mechanism (82) may be provided inside the first cylinder (30) or inside the middle plate (50). When the oil separation mechanism (82) is provided in the first cylinder (30), the discharge pipe (54) is connected to the first cylinder (30). When the oil separation mechanism (82) is provided in the middle plate (50), the discharge pipe (54) is connected to the middle plate (50). By arranging the oil separation mechanism (82) in the middle plate (50), it is possible to suppress a decrease in the amount of refrigerant oil supplied to each vane chamber (48, 49) of vertically adjacent cylinders (first cylinder (30) and second cylinder (35)).

[0137] The oil separation mechanism (82) in the modified example 3 may be provided so as to penetrate the first cylinder (30), the middle plate (50), and the second cylinder (35). In this case, a space is formed that penetrates the first cylinder (30), the middle plate (50), and the second cylinder (35) in the vertical direction. The oil separation mechanism (82) is placed in this space. As a result, the space in which the oil separation mechanism (82) is placed is formed to be vertically elongated, so that a sufficient amount of refrigerant oil can be stored in the lower part of such a space.

[0138] The oil separation mechanism (82) in the above embodiments and each of the above modifications may be located in a high-pressure gas space (HS). For example, the high-pressure gas space (HS) may be located inside the front muffler (61) or the rear muffler (63). In this case, the oil separation mechanism (82) is located inside the front muffler (61) or the rear muffler (63). Such a space becomes a high-pressure gas space. For example, the high-pressure refrigerant discharged from the first discharge port (24) into the front muffler chamber (62) flows into the oil separation mechanism (82) located inside the front muffler (61), where it is separated into refrigerant and refrigerant oil. The oil separation mechanism (82) may be located inside both the front muffler (61) and the rear muffler (63).

[0139] In the rotary compressor (1) of Modification 3, the high-pressure gas space (HS) may be positioned within a range of 90° to 270° in the circumferential direction of the casing (16) from the position of the gas outlet (84) where the discharge gas flows out, with the drive shaft (70) as the center. Such arrangement of the gas outlet (84) and gas inlet (83) is not limited to Modification 3 and may be applied to the high-pressure gas space (HS) of the above embodiment and each of the above modifications. By configuring the high-pressure gas space (HS) in this way, the distance from the gas inlet (83) to the gas outlet (84) can be increased. As a result, the flow path length of the refrigerant in the oil separation mechanism (82) located in the high-pressure gas space (HS) can also be increased, allowing for the separation of more oil from the refrigerant.

[0140] In modified example 5, the discharge gas passage (91) may be located outside the casing (16). In this case, the discharge gas passage (91) connects the high-pressure gas space (HS) separated by a partition plate with the front muffler chamber (62) and the rear muffler chamber (64). This shortens the distance between the oil separation mechanism (82) and the vane chambers (48, 49), making it easier to supply refrigerant oil to the vane chambers (48, 49). In addition, locating the discharge gas passage (91) outside the casing (16) increases the flexibility of its installation.

[0141] In modified example 4 or 5, the rotary compressor (1) may be configured such that the compression mechanism (15) is located above the electric motor (10). In this case, the high-pressure gas space (HS) is formed above the first space (Si). This allows the separated refrigerant oil to be easily supplied to each vane chamber (48, 49) by its own weight.

[0142] The compression mechanism (15) of the rotary compressor (1) in the above embodiments and each of the above modifications may be a single-cylinder type. In this case, the muffler section (61, 63) may be either a front muffler (61) or a rear muffler (63). Furthermore, in the compression mechanism (15) of the above embodiments and each of the above modifications, the muffler section (61, 63) may be either a front muffler (61) or a rear muffler (63), as long as the oil separation mechanism (82) of this disclosure can be installed within the range.

[0143] The rotary compressor (1) in the above embodiments and each of the above modifications may be of a horizontal type.

[0144] The rotary compressor (1) in the above embodiment and each of the above modifications may be provided with a return oil channel (not shown) that returns the excess refrigerant oil supplied to each vane chamber (48, 49) back to the oil reservoir (85).

[0145] The oil separation mechanism (82) in the above embodiments and each of the above modifications may be any mechanism that allows refrigerant gas to flow and separates refrigerant oil from the refrigerant gas, and may be, for example, a porous material. Also, as shown in Figure 14, the oil separation mechanism (82) may be a plate member (96) provided on the housing (81). The plate member (96) separates the refrigerant from the refrigerant oil by collision with the refrigerant gas. Specifically, the plate member (96) is provided so that the flow path of the refrigerant gas from the gas inlet (83) to the gas outlet (84) formed in the housing (81) is not straight. More specifically, a plurality of plate members (96) are provided so as to block the gas refrigerant flowing straight from the gas inlet (83) to the gas outlet (84). In the example shown in Figure 14, plate members (96) are connected to each of the opposing inner surfaces of the inner surface of the housing (81). Multiple plate members (96) are arranged so that the refrigerant gas flows in a zigzag pattern from the gas inlet (83) to the gas outlet (84). As a result, the refrigerant gas flows meanderingly within the housing (81), making it easier to separate the refrigerant oil from the refrigerant gas through centrifugal force. In addition, as the refrigerant gas flows toward the gas outlet (84) while colliding with the plate members (96), the collisions also make it easier to separate the refrigerant oil from the refrigerant gas.

[0146] The rotary compressor (1) in the above embodiment and each of the above modifications does not necessarily have an inlet pipe (55). In this case, the compression mechanism (15) has a refrigerant flow path (not shown) that connects the first space (Si) and each cylinder (30, 35). Specifically, the refrigerant flow path is formed so that the refrigerant flows from an intake hole (not shown) provided in the front head (20) toward the intake ports (33, 38) of each cylinder (30, 35). As a result, the low-pressure refrigerant in the first space (Si) is drawn into each compression mechanism (K1, K2) via the refrigerant flow path and compressed. The compressed refrigerant is discharged from the rear head (25). The oil separation mechanism (82) is provided in any of the above embodiment and each of the above modifications.

[0147] The oil separation mechanism in the above embodiments and each of the above modifications may be a cyclone type or a helical type. In this case, the refrigerant oil is separated from the refrigerant by centrifugal force.

[0148] In each of the above modified examples, if the oil reservoir (85) is formed at the bottom of the casing (16), the oil reservoir (85) may also serve as a storage section for storing refrigerant oil supplied to the compression mechanism (15).

[0149] In the above embodiments and each of the above modifications, each rotary compressor (1) may have a tapered surface (81a). Furthermore, it may have a housing (81) that contains an oil separation mechanism (82) inside.

[0150] While embodiments and modifications have been described above, it will be understood that a variety of changes in form and details are possible without departing from the spirit and scope of the claims. Furthermore, these embodiments and modifications may be combined or substituted as appropriate, as long as they do not impair the functions of the subject matter of this disclosure. The terms “First,” “Second,” etc., used above are used to distinguish the phrases to which these terms are attached, and do not limit the number or order of such phrases. [Industrial applicability]

[0151] As explained above, this disclosure is useful for rotary compressors. [Explanation of Symbols]

[0152] 1. Rotary compressor (compressor) 10 Electric motor 15 Compression mechanism 16 Casing 20 Front head (first end plate) 24 1st outlet 24,29 Discharge port 25 Rear head (second end plate) 29 2nd outlet 30 First Cylinder 30,35 cylinders 35 Second Cylinder 40,45 Laura 41,46 Bane 48,49 Vane Chamber 50 Middle Plate 61, 63 Muffler section 62,64 Muffler chamber 70 Drive shaft 81a Tapered surface 82 Oil separation mechanism 83 Gas inlet (inlet) 84 Gas outlet (outlet) 90 Oil supply path 91 Discharge gas passage (connecting passage) 96 Plate members 100 Refrigeration cycle equipment HS High-Pressure Gas Space S1, S2 Cylinder Chamber Sd discharge side space Si 1st space Ss Suction side space

Claims

1. A casing (16) in which a first space (Si) is formed inside into which refrigerant at suction pressure flows, An electric motor (10) is arranged in the first space (Si), The drive shaft (70) rotates around the axial direction by the electric motor (10), The system includes a compression mechanism (15) which is driven by the drive shaft (70) and compresses the refrigerant in the first space (Si) and discharges the compressed refrigerant from the discharge ports (24, 29), The compression mechanism (15) is Cylinders (30, 35) and A roller (40, 45) rotates eccentrically in the space enclosed by the inner walls of the cylinder (30, 35), The vanes (41, 46) are inserted into the vane chambers (48, 49) formed inside the cylinders (30, 35), and divide the cylinder chambers (S1, S2) formed by the space surrounded by the inner walls of the cylinders (30, 35) and the rollers (40, 45) into an intake side space (Ss) and a discharge side space (Sd). A first end plate (20) closes one end of the cylinder (30, 35) in the axial direction, The cylinder (30, 35) has a second end plate (25) that closes the other end in the axial direction of the cylinder, The casing (16) includes: An oil reservoir (85) where refrigeration oil is stored, The refrigerant discharged from the aforementioned outlets (24, 29) flows into a high-pressure gas space (HS) that communicates with the vane chambers (48, 49), and An oil separation mechanism (82) is provided in the high-pressure gas space (HS) to separate the refrigerant discharged from the outlets (24, 29) from the refrigerating oil. The oil reservoir (85) is formed in the high-pressure gas space (HS), The system further includes an oil supply passage (90) for supplying the refrigeration oil from the oil reservoir (85) to the vane chambers (48, 49), The oil supply passage (90) is not formed inside the drive shaft (70). Rotary compressor.

2. An inlet (83) through which the refrigerant compressed by the compression mechanism (15) flows into the high-pressure gas space (HS), The outlet (84) through which the refrigerant in the high-pressure gas space (HS) flows out of the high-pressure gas space (HS) and Furthermore, The inlet (83) is positioned within a range of 90° to 270° from the outlet (84) toward the circumferential direction of the casing (16) with respect to the drive shaft (70). The rotary compressor according to claim 1.

3. The oil reservoir (85) is provided at the bottom of the high-pressure gas space (HS), The bottom of the high-pressure gas space (HS) has a tapered surface (81a) that slopes downward toward the oil supply passage (90). The rotary compressor according to claim 1 or 2.

4. The system further comprises muffler sections (61, 63) into which the refrigerant discharged from the aforementioned outlets (24, 29) flows, forming muffler chambers (62, 64), The oil separation mechanism (82) is located inside the muffler chamber (62, 64) or inside the muffler section (61, 63). The rotary compressor according to claim 1 or 2.

5. The oil separation mechanism (82) is provided inside the cylinders (30, 35). The rotary compressor according to claim 1 or 2.

6. The oil separation mechanism (82) is It is a mesh member that separates the refrigerant from the refrigerant oil as the refrigerant gas passes through it, or The plate member (96) separates the refrigerant from the refrigerant oil by collision with the refrigerant gas. The rotary compressor according to claim 1 or 2.

7. The compression mechanism (15) is a two-cylinder type, A first cylinder (30) and a second cylinder (35) are arranged in the axial direction, It has a middle plate (50) positioned between the first cylinder (30) and the second cylinder (35), The compression mechanism (15) is provided with a communication passage (91) that connects a first discharge port (24) for discharging refrigerant compressed in the first cylinder (30) and a second discharge port (29) for discharging refrigerant compressed in the second cylinder (35), The communication passage (91) supplies the discharged refrigerant to the oil separation mechanism (82). The rotary compressor according to claim 1 or 2.

8. A refrigeration cycle device comprising the rotary compressor according to claim 1 or 2.

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