JP7853606B2 - Rotary compressor - Google Patents

Description

This disclosure relates to a rotary compressor and a refrigeration cycle system equipped therewith. A rotary compressor is a compressor that compresses gas in a compression chamber formed within a cylinder by eccentrically rotating a roller within the cylinder. A rotary compressor generally has vanes for partitioning the compression chamber. Rotary compressors include so-called rolling roller types, where separate vanes contact the roller while the roller rotates eccentrically; so-called swing types, where vanes integrally formed with the roller swing in conjunction with the roller's eccentric rotation; and so-called hinge vane types, where the tip of the vane is rotatably fitted into a recess on the outer surface of the roller while the roller rotates eccentrically.

Patent Document 1 discloses a rotary compressor equipped with an oil separator for separating lubricating oil contained in the 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 predetermined sliding parts within the compressor.

Japanese Patent Publication No. 2012-202357

In Patent Document 1, the oil separator is located outside the rotary compressor. Therefore, if the length of the oil supply path connecting the oil separator to the sliding part increases, the flow resistance within the oil supply path increases, reducing the amount of oil supplied to the sliding part.

The purpose of this disclosure is to suppress the reduction in the amount of lubrication supplied to the sliding parts within a rotary compressor.

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 cylinders (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
The rotary compressor is configured such that 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 refrigerant oil.

In the first embodiment, the oil separation mechanism (82) is arranged inside the casing (16). Therefore, the flow path length of the refrigerant oil from the oil separation mechanism (82) to the oil reservoir (85), and the flow path length of the refrigerant oil from the oil reservoir (85) to the sliding parts (especially the vane chambers (48, 49)) can be shortened. This reduces the resistance in the flow path of the refrigerant oil from the oil separation mechanism (82) to the oil reservoir (85), and prevents a decrease in the amount of refrigerant oil supplied to the sliding parts.

The second aspect is the same as 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).

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), thus shortening 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 minimizing the reduction in the amount of oil supplied to the vane chambers (48, 49).

A third aspect is a modification 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).

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

The fourth aspect is one of the first to third aspects,
The oil reservoir (85) is provided at the bottom of the high-pressure gas space (HS),
The system includes an oil supply passage (90) for supplying refrigerant oil from the oil reservoir (85) to the vane chamber.
The bottom of the high-pressure gas space (HS) has a tapered surface (81a) that slopes downward toward the oil supply passage (90).

In the fourth embodiment, an oil reservoir (85) is formed at the lower end of the oil supply passage (90) so that the refrigerant oil collects there. This makes it easier to supply the refrigerant oil from the oil reservoir (85) to the oil supply passage (90).

A fifth aspect is a modification of the first or second aspect,
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).

In the fifth embodiment, since the oil separation mechanism (82) also serves as a sound-absorbing space, the increase in the volume of the high-pressure gas space (HS) can be suppressed, and the amount of refrigerant to be charged can also be reduced.

The sixth aspect is the first or second aspect,
The oil separation mechanism (82) is provided inside the cylinders (30, 35).

In the sixth embodiment, since the oil separation mechanism (82) is provided inside the cylinders (30, 35), the space required for the oil separation mechanism (82) is eliminated. This allows for a more compact casing (16).

The seventh aspect is one of the first to sixth aspects,
The oil separation mechanism (82) is
The device has a porous or mesh-like member that separates the refrigerant from the refrigerant oil as the refrigerant gas passes through it, or a plate member that separates the refrigerant from the refrigerant oil as the refrigerant gas collides with it.

In the seventh embodiment, the refrigerant and refrigeration oil can be separated using a relatively simple mechanism. The cost of the oil separation mechanism (82) can be reduced.

The eighth aspect is one of the first to seventh aspects,
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).

In the eighth embodiment, even in a two-cylinder rotary compressor, by providing a connecting passage (91), the same effect as in the first embodiment can be obtained with a single oil separation mechanism (82).

The ninth embodiment is a refrigeration cycle system comprising a rotary compressor according to one of the first to eighth embodiments.

In a ninth aspect, a refrigeration cycle apparatus comprising the rotary compressor of the present disclosure can be provided.

Figure 1 is a diagram showing the configuration of the refrigerant circuit of the refrigeration cycle device according to the embodiment. Figure 2 shows a vertical cross-section of a rotary compressor. Figure 3A shows a horizontal cross-section of the first compression mechanism. Figure 3B shows a horizontal cross-section of the second compression mechanism. Figure 4 shows the operation of the first and second compression mechanisms. Figure 5 shows a vertical cross-section of a rotary compressor according to Modification 1. Figure 6 shows a cross-sectional view of the rotary compressor shown in Figure 5, taken along the V-V line. Figure 7 shows a vertical cross-section of the rotary compressor according to the modified example 2. Figure 8 shows a vertical cross-section of the rotary compressor according to Modification 2, viewed from a different direction than that shown in Figure 7. Figure 9 shows a vertical cross-section of a rotary compressor according to modification 3. Figure 10 shows a cross-sectional view of the rotary compressor shown in Figure 9, taken along the line X-X. Figure 11 shows a vertical cross-section of a rotary compressor according to the modified example 4. 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 shows a vertical cross-section of a rotary compressor according to modification 5. Figure 14 is a schematic diagram showing the configuration of an oil separation mechanism according to another embodiment.

The embodiments of the present invention will be described below with reference to the drawings. Note that 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.

(1) Refrigeration cycle device 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 air-conditions 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).

The refrigeration cycle unit (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).

The refrigeration cycle system (100) performs heating and cooling operations by switching the four-way directional 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 directional valve (3) are connected, and the second port (P2) and the fourth port (P4) are connected (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 directional valve (3) are connected, and the second port (P2) and the third port (P3) are connected (dashed line in Figure 1), the indoor heat exchanger (6) functions as a radiator, and the outdoor heat exchanger (4) functions as an evaporator.

(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.

(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). At the bottom of the casing (16), an oil reservoir (not shown) is formed for supplying refrigerant oil to the bearing section of the compression mechanism (15), which will be described later.

The suction pipe (53) introduces the suction refrigerant into the casing (16). This creates a first space (Si) inside the casing (16) through 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 interior 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).

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).

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.

(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 the axial direction of the drive shaft (70). 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).

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). Each of the first and second compression mechanisms (K1) comprises 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).

The compression mechanism (15) comprises 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 multiple bolts (not shown). The front head (20) of the compression mechanism (15) is fixed to the body (17) of the casing (16).

(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.

(2-3-2) Cylinders 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).

The thicknesses 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, including through-holes for inserting bolts for assembling the compression mechanism (15).

The cylinders (30, 35) are formed in an annular shape. Each cylinder (30, 35) has 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 walls 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) include 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).

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).

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).

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.

(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 (22), and an outer peripheral wall (23). The main body (21), the main bearing (22), and the outer peripheral wall (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.

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) towards 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).

A first discharge port (24) is formed in the front head (20). The first discharge port (24) is an example of the discharge ports (24, 29) of this disclosure. The first discharge port (24) discharges the refrigerant compressed by the first cylinder (30). The first discharge port (24) penetrates the main body (21) of the front head (20) in its 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).

(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.

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 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 the second cylinder (35).

A second discharge port (29) is formed in the rear head (25). The second discharge port (29) is an example of the discharge ports (24, 29) of 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 its 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).

(2-3-5) Middle Plate The middle plate (50) shown in Figure 2 is positioned 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).

A central hole (51) is formed in the middle of the middle plate (50), penetrating it in the thickness direction. The intermediate connecting portion (78) of the drive shaft (70), described later, is inserted through the central hole (51) of the middle plate (50).

(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).

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 section (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).

(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).

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 sequentially 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.

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 axes of the main shaft (72) and the secondary shaft (74) coincide with the rotational axis (70a) of the drive shaft (70).

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

The eccentricity e1 of the first eccentric part (75) and the eccentricity e2 of the second eccentric part (76) are equal. Note that 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).

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.

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

(2-3-8) Roller A roller (40, 45) that rotates eccentrically is arranged in the space surrounded by the inner circumferential surfaces (31, 36) of the cylinder (30, 35). The space surrounded by the inner circumferential surfaces (31, 36) of the cylinder (30, 35) and the roller (40, 45) form a cylinder chamber (S1, S2). The roller (40, 45) has 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).

The cylinder chambers (S1, S2) comprise 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.

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.

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).

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

The outer circumferential surface of the second roller (45) slides against the second inner circumferential 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).

(2-3-9) Vanes 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).

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).

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). This 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).

(2-3-10) Bushings Bushings (42, 47) are provided in the cylinders (30, 35). Bushings (42, 47) are a pair of plate-shaped semicircular members that are positioned facing each other with the vanes (41, 46) in between. The flat surfaces of the pair of semicircular members sandwich the vanes (41, 46). Bushings (42, 47) consist of a first bushing (42) and a second bushing (47). The first bushing (42) is provided in the first cylinder (30). The second bushing (47) is provided in the second cylinder (35).

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) in a pivotable and reciprocable manner. As a result, the first roller (40) is configured as a pivoting roller that revolves along the inner wall surface of the first cylinder (30) in conjunction with the rotation of the drive shaft (70), while pivoting relative to the central axis (75a) of the first eccentric portion (75).

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) in a pivotable and reciprocable manner. As a result, the second roller (45) is configured as a pivoting roller that revolves along the inner wall surface of the second cylinder (35) in conjunction with the rotation of the drive shaft (70), while pivoting relative to the central axis (76a) of the second eccentric portion (76).

(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 the refrigerant.

(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).

In each cylinder (30, 35), the volume of the intake space (Ss) and discharge space (Sd) of the cylinder chamber (S1, S2) changes as the roller (40, 45) is displaced. As a result, each cylinder (30, 35) performs three strokes: 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).

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° represents the rotation angle of the drive shaft (70) at the position where the first vane (41) of the first compression mechanism (K1) is furthest back from the first cylinder (30), and 180° represents the rotation angle of the drive shaft (70) at the position where the first vane (41) of the first compression mechanism (K1) is furthest inside the first cylinder (30).

(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 position 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.

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. The suction stroke continues until the rotation angle of the drive shaft (70) reaches 360°, after which the process transitions to the compression stroke and discharge stroke.

When the drive shaft (70) rotates slightly from a 0° rotation angle, 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 within 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).

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).

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: suction stroke, compression stroke, and discharge stroke.

(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.

As the rotation angle of the drive shaft (70) increases, the volume of the suction space (Ss) gradually increases, and the amount of refrigerant drawn into the suction 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 and discharge strokes.

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 within 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).

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 second discharge port (29) to the outside of the compression mechanism (15).

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: suction stroke, compression stroke, and discharge stroke.

(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 the 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".

The oil separator (80) is positioned below the rear muffler (63). The oil separator (80) comprises a housing (81) and an oil separation mechanism (82) located within the housing (81).

The housing (81) is formed in a generally cylindrical shape. The interior of the housing (81) receives refrigerant discharged from the first discharge port (24) and the second discharge port (29), and is connected to the vane chambers (48, 49). This creates a high-pressure gas space (HS) inside the housing (81). The housing (81) has a gas inlet (83) and a gas outlet (84).

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) also communicates with the downstream end of the discharge gas passage (91).

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 connected to the discharge pipe (54).

An oil reservoir (85) for storing refrigerant oil is formed within the housing (81). The oil reservoir (85) is formed at the bottom of the housing (81). The bottom of the casing (16) has a tapered surface (81a) that slopes downwards. This causes the refrigerant oil in the oil reservoir (85) to collect 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).

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 within the housing (81) from the gas inlet (83) to the gas outlet (84). This allows for the separation of the refrigerant oil from the refrigerant as it travels from the gas inlet (83) to the gas outlet (84) within the housing (81).

(6) Discharge gas passage and oil supply passage The discharge gas passage (91) shown by the dashed arrow in Figure 2 is a connecting passage (91) that connects 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.

The oil supply passage (90) is a passage connecting the oil reservoir (85) and each vane chamber (48, 49). The oil supply passage (90) penetrates vertically through the rear muffler (63), rear head (25), and middle plate (50) (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).

(7) Flow of discharged refrigerant and refrigerant oil The high-pressure refrigerant discharged from the first discharge port (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 discharge port (29) in the rear muffler chamber (64) (see dashed arrow in Figure 2).

The high-pressure refrigerant, flowing from the rear muffler (63) through the gas inlet (83) into the oil separator (80), flows through the housing (81) towards the gas outlet (84). Within 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 then 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 collected in the oil reservoir (85).

Because the space within 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 flowing into the oil supply passage (90) rises along the oil supply passage (90) (indicated by the dashed arrow in Figure 2) and is transported to the second vane chamber (49) and the first vane chamber (48), respectively. The refrigerant oil flowing into the second vane chamber (49) is supplied to the sliding portion where the second bush (47) and the second vane (46) meet. The refrigerant oil flowing into the first vane chamber (48) is supplied to the sliding portion where the first bush (42) and the first vane (41) meet.

(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 flow path of the refrigerant oil due to vibration of the rotary compressor can be suppressed.

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 for transporting the refrigerant oil are installed, they can be shortened, thus minimizing the reduction in the amount of oil supplied to the vane chambers (48, 49).

(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).

According to this embodiment, since a high-pressure gas space (HS) for supplying refrigerant oil to the vane chambers (48, 49) is formed within the casing (16), the oil supply passage (90) from the oil reservoir (85) to the vane chambers (48, 49) can be shortened. This reduces flow resistance within the oil supply passage (90), thereby minimizing the reduction in the amount of oil supplied to the vane chambers (48, 49). If the pipe diameter of the oil supply passage (90) were increased to reduce flow resistance, the required amount of oil to be filled into the compressor would increase, and the amount of refrigerant dissolved in the refrigerant oil would also increase, thus increasing the required amount of refrigerant to be filled. 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 oil and refrigerant filling amounts can be suppressed.

(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) includes 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).

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 easily collects at the inlet of the oil supply passage (90). This facilitates the flow of the refrigerant oil from the oil reservoir (85) into the oil supply passage (90).

(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.

(8-5) Feature 5
The rotary compressor (1) of this embodiment has a two-cylinder compression mechanism (15), and further has a communication 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 communication passage (91) supplies the discharged refrigerant to the oil separation mechanism (82).

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).

(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.

(9) Modified Versions 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.

(9-1) Modification example 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).

The discharge gas passage (91) is formed to extend from the front muffler chamber (62) to the rear muffler chamber (64), penetrating vertically through each cylinder (30, 35) and the middle plate. The high-pressure gas space (HS) includes the rear muffler chamber (64).

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).

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).

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). The refrigerant oil then 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.

Thus, in the rotary compressor (1) of Modification 1, the oil separation mechanism (82) is located in the rear muffler chamber (64), thereby suppressing 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). Furthermore, by having the rear muffler chamber (64) also serve as the housing space for the oil separation mechanism (82), a reduction in the amount of refrigerant charged to the refrigerant circuit (9) can be achieved.

(9-2) Modification 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).

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

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). The oil reservoir (85) is formed in the front muffler chamber (62).

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).

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).

In this 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).

(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).

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).

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 longitudinally (circumferentially) along 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) to the second vane chamber (49).

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 flowing 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 flowing into the first vane chamber (48) is supplied to the first bush (42).

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) communicating with each vane chamber (48, 49) can be shortened.

(9-4) Modification 4
The rotary compressor (1) of modified example 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).

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

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).

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).

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).

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 flows into the rear head (25) rises through 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).

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. Furthermore, by installing the oil supply passage (90) outside the casing (16), the flexibility of the compressor (1)'s installation can be improved.

(9-5) Modification 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).

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

The oil separation mechanism (82) in Modification 3 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), a decrease in the supply amount of refrigerant oil to the vane chambers (48, 49) of vertically adjacent cylinders (first cylinder (30) and second cylinder (35)) can be suppressed.

In the modified example 3, the oil separation mechanism (82) 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 arranged in this space. As a result, the space in which the oil separation mechanism (82) is arranged is formed to be vertically elongated, and a sufficient amount of refrigerant oil can be secured in the lower part of such a space.

The oil separation mechanism (82) in the above embodiments and each of the above modifications may be located in the high-pressure gas space (HS). For example, the high-pressure gas space (HS) may be provided inside the front muffler (61) or the rear muffler (63). In this case, the oil separation mechanism (82) is provided 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) provided inside the front muffler (61), where it is separated into refrigerant and refrigerant oil. The oil separation mechanism (82) may be provided inside both the front muffler (61) and the rear muffler (63).

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 discharged gas exits, centered on the drive shaft (70). 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. This allows for an increased flow path length of the refrigerant within the oil separation mechanism (82) located in the high-pressure gas space (HS), thus enabling the separation of more oil from the refrigerant.

In Modification 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), which is partitioned by a baffle plate, to 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), facilitating the supply of 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.

In modified example 4 or 5, the rotary compressor (1) may be configured such that the compression mechanism (15) is positioned 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.

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 available space.

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

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

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). This causes the refrigerant gas to meander through the housing (81), facilitating the separation of refrigerant oil from the gas through centrifugal force. In addition, as the refrigerant gas flows towards the gas outlet (84) while colliding with the plate members (96), the collisions further facilitate the separation of refrigerant oil from the gas.

The rotary compressor (1) in the above embodiment and each of the above modifications may not 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 embodiments and each of the above modifications.

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.

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 refrigerant oil supplied to the compression mechanism (15).

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) containing an oil separation mechanism (82) internally.

While embodiments and modifications have been described above, it will be understood that various changes in form and detail are possible without departing from the spirit and scope of the claims. Furthermore, these embodiments and modifications may be combined or substituted as appropriate, provided that they do not impair the function of the subject matter of this disclosure. The terms "first," "second," etc., used above are used to distinguish the phrases to which they are assigned, and do not limit the number or order of such phrases.

As explained above, this disclosure is useful for rotary compressors.

1. Rotary compressor (compressor)
10 Electric motor
15 Compression mechanism
16 Casing
20 Front head (first end plate)
24 1st discharge port
24,29 Discharge port
25 Rear head (second end plate)
29 Second discharge port
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 (8)

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. An inlet (83) through which the refrigerant compressed by the compression mechanism (15) flows into the high-pressure gas space (HS),
The system further comprises an outlet (84) through which the refrigerant in the high-pressure gas space (HS) flows out of the high-pressure gas space (HS),
The rotary compressor according to claim 1 , wherein 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 oil reservoir (85) is provided at the bottom of the high-pressure gas space (HS) ,
The rotary compressor according to claim 1 or 2, wherein the bottom of the high-pressure gas space (HS) has a tapered surface (81a) that slopes downward toward the oil supply passage (90). 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 rotary compressor according to claim 1 or 2, wherein 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, wherein the oil separation mechanism (82) is provided inside the cylinders (30, 35). The oil separation mechanism (82) is
A rotary compressor according to claim 1 or 2, having a mesh member that separates the refrigerant from the refrigerant oil as the refrigerant gas passes through it, or a plate member (96) that separates the refrigerant from the refrigerant oil as the refrigerant gas collides with it. 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 rotary compressor according to claim 1 or 2, wherein the communication passage (91) supplies the discharged refrigerant to the oil separation mechanism (82). A refrigeration cycle device comprising the rotary compressor according to claim 1 or 2.