Compressors and refrigeration cycle systems

Abstract

This compressor includes a sealed container, a rotary electric machine, a rotary shaft, a compression mechanism, and an intake pipe. The compression mechanism has a cylinder, a piston, a vane, an upper bearing, and a lower bearing. The cylinder has an intake flow path formed therein, and the intake flow path has an intake hole to which the intake pipe is connected, and a constricted portion formed radially inward of the intake hole and forming a space that communicates the intake hole with a cylinder chamber. The constricted portion has: a pair of constricted-portion side surfaces that constitute both inner side surfaces of the constricted portion and are formed to approach each other as the pair of constricted-portion side surfaces extend radially inward of the cylinder; a shaft-side opening that is defined by the pair of constricted-portion side surfaces and is open at one end in the axial direction of the rotary shaft; an inner-side opening that is defined by the pair of constricted-portion side surfaces, is open toward the radially inward side of the cylinder so as to communicate with the cylinder chamber, and is formed to be contiguous with the shaft-side opening; and a plate-shaped closing wall provided at the other end in the axial direction of the rotary shaft so as to close the constricted portion.

Description

Technical Field

[0001] The present disclosure relates to a compressor and a refrigeration cycle device.

Background Art

[0002] Conventionally, a compressor is known that forms a rotary compressor by enclosing an electric motor element and a compression element driven by the electric motor element (see, for example, Patent Document 1). The compression element of this compressor includes a cylinder, an upper end plate and a lower end plate respectively disposed on both end faces of the cylinder, a piston disposed in the cylinder, and a vane that partitions the space formed by the cylinder, the upper end plate, the lower end plate, and the piston into a high-pressure chamber and a low-pressure chamber. Further, the cylinder is formed with a suction hole formed to extend radially inward from the outer peripheral surface of the cylinder, and a notch formed on the radially inner side of the suction hole to reduce the resistance during refrigerant suction. The notch is formed so as to penetrate both end faces of the cylinder in order to expand the opening area of the passage through which the refrigerant flowing from the suction hole to the low-pressure chamber passes, and connects the suction hole and the low-pressure chamber.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] However, in the compressor of Patent Document 1, since the notch is formed so as to penetrate both end faces of the cylinder, the strength of this portion is weak, and there is a risk that the cylinder may be deformed by the pressing force of the vane due to the differential pressure between the high-pressure chamber and the low-pressure chamber on the cylinder.

[0005] This disclosure aims to solve the above-mentioned problems and to provide a compressor and refrigeration cycle device that can increase the strength of the cylinder. [Means for solving the problem]

[0006] The compressor according to this disclosure comprises a sealed container, a rotating electric machine disposed within the sealed container, a rotating shaft disposed within the sealed container and rotationally driven by the rotating electric machine, a compression mechanism disposed within the sealed container and compressing a refrigerant by a driving force transmitted from the rotating electric machine via the rotating shaft, and an intake pipe that penetrates the sealed container and is connected to the compression mechanism, forming a flow path for the refrigerant. The compression mechanism comprises at least one cylinder formed in a cylindrical shape and having a cylinder chamber inside, a piston fitted onto the rotating shaft and housed in the cylinder chamber, which rotates eccentrically with the rotation of the rotating shaft to compress the refrigerant, vanes arranged in vane grooves formed to extend radially in the cylinder and, together with the piston, divide the cylinder chamber into two spaces, and upper and lower bearings arranged on the end face of the cylinder and close the cylinder chamber. An intake passage is formed that connects the outside of the cylinder to the cylinder chamber. The intake passage extends radially inward from the outer surface of the cylinder and has an intake hole to which an intake pipe is connected on the outer surface, and a constricted portion formed radially inward from the intake hole, which forms a space that connects the intake hole to the cylinder chamber. The constricted portion has a pair of constricted side surfaces that make up both inner surfaces of the constricted portion and are formed to move closer to each other as they move radially inward from the cylinder, an axial-side opening formed by the pair of constricted side surfaces that opens at one end in the axial direction of the rotating shaft, an inner opening formed by the pair of constricted side surfaces that opens radially inward from the cylinder to communicate with the cylinder chamber and is connected to the axial-side opening, and a plate-shaped closing wall provided at the other end in the axial direction of the rotating shaft to close the constricted portion.

[0007] The refrigeration cycle device according to this disclosure comprises a compressor with the above configuration, an outdoor heat exchanger that performs heat exchange between outdoor air and a refrigerant flowing inside, a pressure reducer that reduces the pressure of the refrigerant flowing inside, and an indoor heat exchanger that performs heat exchange between indoor air and a refrigerant flowing inside. [Effects of the Invention]

[0008] The compressor and refrigeration cycle device according to this disclosure have a throttling section in the refrigerant intake passage formed in the cylinder. The throttling section has a pair of throttling section side surfaces that form both inner surfaces of the throttling section and are formed to approach each other as they extend radially inward from the cylinder. The throttling section is also composed of the pair of throttling section side surfaces and has an axial-side opening that opens at one end in the axial direction of the rotating shaft. The throttling section is also composed of the pair of throttling section side surfaces and has an inner opening that opens radially inward from the cylinder to communicate with the cylinder chamber and is formed to connect with the axial-side opening. The throttling section also has a plate-shaped closing wall at the other end in the axial direction of the rotating shaft that closes the throttling section. The throttling section can increase the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft by the axial-side opening and the inner opening, while ensuring the rigidity of the cylinder by the closing wall and increasing the strength of the cylinder. [Brief explanation of the drawing]

[0009] [Figure 1] This is a schematic longitudinal cross-sectional view showing the overall configuration of the compressor according to Embodiment 1. [Figure 2] This is a schematic cross-sectional view of the first cylinder portion of the compression mechanism according to Embodiment 1. [Figure 3] This is a schematic cross-sectional view of the second cylinder portion of the compression mechanism according to Embodiment 1. [Figure 4] This is a schematic partial longitudinal cross-sectional view of the compression mechanism according to Embodiment 1. [Figure 5] This is a perspective view of the first cylinder of the compressor according to Embodiment 1. [Figure 6] This is a partially enlarged view of the suction passage of the compressor according to Embodiment 1. [Figure 7]It is a conceptual diagram of the suction flow path of the compressor according to Embodiment 1. [Figure 8] It is a side view of the first cylinder of the compressor according to Embodiment 1 as viewed from the inner peripheral surface side. [Figure 9] It is a perspective view of the first cylinder of a modified example of the compressor according to Embodiment 1. [Figure 10] It is a partially enlarged view of the suction flow path of a modified example of the compressor according to Embodiment 1. [Figure 11] It is a perspective view of the second cylinder of the compressor according to Embodiment 1. [Figure 12] It is a partially enlarged view of the internal suction flow path of the compressor according to Embodiment 1. [Figure 13] It is a conceptual diagram of the internal suction flow path of the compressor according to Embodiment 1. [Figure 14] It is a perspective view of the second cylinder of a modified example of the compressor according to Embodiment 1. [Figure 15] It is a partially enlarged view of the internal suction flow path of a modified example of the compressor according to Embodiment 1. [Figure 16] It is a schematic configuration diagram of a refrigeration cycle device including the compressor according to Embodiment 1. [Figure 17] It is a schematic longitudinal sectional view showing the overall configuration of the compressor according to Embodiment 2. [Figure 18] It is a schematic partial longitudinal sectional view of the compression mechanism according to Embodiment 2. [Figure 19] It is a partially enlarged view of the internal suction flow path of the compressor according to Embodiment 2. [Figure 20] It is a partially enlarged view of the suction flow path of the compressor according to Embodiment 2. [Figure 21] It is a partially enlarged view of the internal suction flow path of a modified example of the compressor according to Embodiment 2. [Figure 22] It is a partially enlarged view of the suction flow path of a modified example of the compressor according to Embodiment 2. [Figure 23] It is a schematic longitudinal sectional view showing the overall configuration of the compressor according to Embodiment 3. [Figure 24] It is a schematic partial longitudinal sectional view of the compression mechanism according to Embodiment 3. [Figure 25]It is a perspective view of the first cylinder of the compressor according to Embodiment 3. [Figure 26] It is a partially enlarged view of the suction passage of the compressor according to Embodiment 3. [Figure 27] It is a perspective view of the first cylinder of a modified example of the compressor according to Embodiment 3. [Figure 28] It is a partially enlarged view of the suction passage of a modified example of the compressor according to Embodiment 3. [Figure 29] It is a schematic longitudinal sectional view showing the overall configuration of the compressor according to Embodiment 4. [Figure 30] It is a schematic partial longitudinal sectional view of the compression mechanism according to Embodiment 4.

Modes for Carrying Out the Invention

[0010] Hereinafter, the compressor and the refrigeration cycle device according to the embodiments will be described with reference to the drawings and the like. In the following drawings including FIG. 1, the relative dimensional relationships and shapes of each component may be different from the actual ones. Further, in the following drawings, those denoted by the same reference numerals are the same or corresponding ones, and this shall be common throughout the entire specification. In addition, terms indicating directions (for example, "upper", "lower", "right", "left", "front", "rear", etc.) are appropriately used for easy understanding, but their notations are only for the convenience of explanation and do not limit the arrangement and orientation of the device or parts.

[0011] Embodiment 1. [Configuration of Compressor 1] FIG. 1 is a schematic longitudinal sectional view showing the overall configuration of the compressor 1 according to Embodiment 1. Using FIG. 1, the compressor 1, which is a hermetic compressor, will be described. As shown in FIG. 1, the compressor 1 according to Embodiment 1 shows a rolling piston type compressor as an example of the compressor according to the present disclosure. The compressor 1 sucks in a low-temperature and low-pressure refrigerant, compresses the sucked refrigerant, and discharges a high-temperature and high-pressure refrigerant.

[0012] Compressor 1 is a two-cylinder rotary compressor, a fluid machine that discharges low-pressure gaseous refrigerant drawn into the compressor 1 as high-pressure gaseous refrigerant. Note that the two-cylinder rotary compressor is just one example; other rotary compressors, such as a one-cylinder rotary compressor, may also be used.

[0013] The compressor 1 comprises a sealed container 10, a compression mechanism 20, a rotating electric machine 30 located inside the sealed container 10, and a rotating shaft 40 located inside the sealed container 10 and driven by the rotating electric machine 30. The compressor 1 also comprises an intake pipe 2, a discharge pipe 4, an intake muffler 3, and a centrifugal pump 45. The compressor 1 houses the compression mechanism 20 for compressing the refrigerant, the rotating electric machine 30 for driving the compression mechanism 20, and the rotating shaft 40 connecting the compression mechanism 20 and the rotating electric machine 30 inside the sealed container 10. The compression mechanism 20 is housed in the lower part of the sealed container 10, and the rotating electric machine 30 is housed in the upper part of the sealed container 10.

[0014] (Sealed container 10) The sealed container 10 constitutes the outer casing and external appearance of the compressor 1. The sealed container 10, which constitutes the outer casing of the compressor 1, houses the compression mechanism 20, the rotating electric machine 30, the rotating shaft 40, and the like.

[0015] The sealed container 10 comprises a roughly cylindrical body portion 12, a roughly hemispherical or bottomed cylindrical head portion 11, and a roughly hemispherical or bottomed cylindrical bottom portion 13. The body portion 12 constitutes the outer casing of the middle section of the compressor 1, with the head portion 11 attached to the upper part and the bottom portion 13 attached to the lower part. The head portion 11 constitutes the outer casing of the upper part of the compressor 1. The bottom portion 13 constitutes the outer casing of the lower part of the compressor 1. For example, in the sealed container 10, the head portion 11 is welded to the upper part of the body portion 12, and the bottom portion 13 is welded to the lower part of the body portion 12.

[0016] A suction pipe 2 for supplying refrigerant into the sealed container 10 is connected to the body portion 12 of the sealed container 10. The body portion 12 of the sealed container 10 is provided with a through hole, and the suction pipe 2 is inserted into and connected to this through hole.

[0017] Furthermore, the stator 32 of the rotating electric machine 30 is attached to the inner circumferential surface of the body 12. Also, the compression mechanism 20 is attached to the inner circumferential surface of the body 12. The compressor 1 of Embodiment 1 employs a rolling piston type compression mechanism as the compression mechanism 20. When a rolling piston type compression mechanism is employed as the compression mechanism 20, the compressor 1 is often mounted on the inner circumferential surface of the body 12, below the position where the stator 32 is attached.

[0018] The head portion 11, which constitutes the upper part of the sealed container 10, is formed in a roughly bowl shape, as shown in Figure 1. A discharge pipe 4, which connects the inside and outside of the sealed container 10, is connected to the head portion 11 of the sealed container 10. The fixed portion between the discharge pipe 4 and the head portion 11 is joined by, for example, brazing or resistance welding.

[0019] The bottom portion 13 of the sealed container 10 is formed in a roughly bowl shape, as shown in Figure 1. Refrigerant oil 6, which is a lubricating oil, is stored in the bottom portion 13 of the sealed container 10. That is, refrigerant oil 6 is stored inside the sealed container 10. The compressor 1 is equipped with a centrifugal pump 45, described later, at the bottom of the rotating shaft 40 to pump up the refrigerant oil 6. As the rotating shaft 40 rotates, the centrifugal pump 45 pumps up the refrigerant oil 6 stored in the bottom portion 13 of the sealed container 10 and supplies it to the sliding parts of the compression mechanism 20. The compressor 1 ensures that the refrigerant oil 6 is supplied to the compression mechanism 20, reducing friction at the sliding parts of the compression mechanism 20. This ensures mechanical lubrication of the compression mechanism 20.

[0020] (Compression mechanism 20) Figure 2 is a schematic cross-sectional view of the first cylinder 21A portion of the compression mechanism 20 according to Embodiment 1. Figure 3 is a schematic cross-sectional view of the second cylinder 21B portion of the compression mechanism 20 according to Embodiment 1. Figure 4 is a schematic partial longitudinal cross-sectional view of the compression mechanism 20 according to Embodiment 1. Figures 2 and 3 are cross-sectional views of the compression mechanism 20 as seen from the side where the rotating electric machine 30 is located. The compression mechanism 20 will be explained using Figures 1 to 4. The compression mechanism 20 is connected to the suction pipe 2 and compresses the refrigerant.

[0021] The compression mechanism 20 is located inside the sealed container 10 and compresses the refrigerant by a driving force transmitted from the rotating electric machine 30 via the rotating shaft 40. The compression mechanism 20 is connected to the rotating shaft 40 and compresses the refrigerant drawn in from the outside with the power of the rotating electric machine 30 transmitted by the rotating shaft 40. The compression mechanism 20 is connected to the rotating electric machine 30 via the rotating shaft 40.

[0022] In the compressor 1 of Embodiment 1, the refrigerant flowing into the intake muffler 3 is supplied to the compression mechanism 20 via the intake pipe 2. That is, the compression mechanism 20 draws in external refrigerant via the intake pipe 2 and compresses this refrigerant. The refrigerant compressed by the compression mechanism 20 is released into the sealed container 10. As described above, the compressor 1 of Embodiment 1 employs a rolling piston type compression mechanism as the compression mechanism 20.

[0023] The compression mechanism 20 includes at least one cylinder 21 which is cylindrical and forms a cylinder chamber 55 inside, and a piston 22 which is fitted onto a rotating shaft 40 and housed in the cylinder chamber 55, and compresses the refrigerant by rotating eccentrically as the rotating shaft 40 rotates. The compression mechanism 20 also has vanes 50 which are arranged in vane grooves 56 formed to extend radially in the cylinder 21 and together with the piston 22 separate the cylinder chamber 55 into two spaces. The compression mechanism 20 also has upper bearings 24A and lower bearings 24B which are arranged on the end face of the cylinder 21 and close the cylinder chamber 55.

[0024] The compression mechanism 20 comprises a first cylinder 21A, a first piston 22A, a first vane 50A, a first spring 51A, an upper bearing 24A, a second cylinder 21B, a second piston 22B, a second vane 50B, a second spring 51B, a lower bearing 24B, and a partition plate 25. The first cylinder 21A and the second cylinder 21B are collectively referred to as cylinder 21. The first piston 22A and the second piston 22B are collectively referred to as piston 22, and the first vane 50A and the second vane 50B are collectively referred to as vane 50.

[0025] The first cylinder 21A is cylindrical in shape and forms the first cylinder chamber 55A. The first cylinder 21A is a cylindrical member formed with an open end in the axial direction of the rotating shaft 40, and has the first cylinder chamber 55A for compressing the refrigerant inside. The first cylinder 21A is formed in a hollow cylindrical shape, and a through hole is formed in the center that is concentric with the axis of the rotating shaft 40. The first cylinder 21A has this through hole closed by an upper bearing 24A positioned in contact with the upper end face of the first cylinder 21A and a partition plate 25 positioned in contact with the lower end face of the first cylinder 21A, thereby forming the first cylinder chamber 55A. The first cylinder 21A is fixed to the sealed container 10.

[0026] Inside the first cylinder chamber 55A are the first eccentric shaft portion 40A of the rotating shaft 40, which will be described later and will perform eccentric motion inside the first cylinder chamber 55A, and the first piston 22A fitted to the first eccentric shaft portion 40A of the rotating shaft 40. Also inside the first cylinder chamber 55A are the first vanes 50A that partition the first cylinder chamber 55A, formed between the inner circumferential wall 155 of the first cylinder chamber 55A and the outer circumferential wall 122 of the first piston 22A.

[0027] As shown in Figures 2 and 4, the first cylinder 21A has an intake passage 52A through which refrigerant is drawn in from the intake pipe 2, and a first discharge passage 53A through which refrigerant is discharged to the discharge pipe 4 via the internal space of the sealed container 10. In addition, as shown in Figure 4, the first cylinder 21A has a branch passage 52AA that branches off from the intake passage 52A.

[0028] In the compressor 1, the suction pipe 2 is press-fitted into the suction passage 52A on the outer surface of the first cylinder 21A. The branch passage 52AA connects the suction passage 52A of the first cylinder 21A to the connection path 25A of the partition plate 25, which will be described later. In other words, the branch passage 52AA is connected to the connection path 25A of the partition plate 25. The detailed configuration of the suction passage 52A and the branch passage 52AA will be described later.

[0029] A first vane groove 56A is formed in the first cylinder 21A. The first vane groove 56A is a groove that extends axially and radially in the first cylinder 21A. In the radial direction of the first cylinder 21A, one end of the first vane groove 56A opens into the first cylinder chamber 55A and communicates with the first cylinder chamber 55A, and the other end is provided with a first spring hole 54A.

[0030] The first spring hole 54A is formed at the radially outer end of the first vane groove 56A of the first cylinder 21A, and penetrates the first cylinder 21A axially, communicating with the first vane groove 56A. The first vane groove 56A houses the first vane 50A, and the first spring hole 54A houses the first spring 51A.

[0031] The first piston 22A is fitted onto the first eccentric shaft portion 40A of the rotating shaft 40 and rotates eccentrically with the first eccentric shaft portion 40A to compress the refrigerant. The first piston 22A is formed in a cylindrical shape. The first piston 22A is mounted on the outer circumference of the first eccentric shaft portion 40A of the rotating shaft 40 inside the first cylinder 21A. When the rotating shaft 40 is rotated by the rotating electric machine 30, the first piston 22A rotates inside the first cylinder 21A along its inner circumferential wall 155.

[0032] The first piston 22A rotates slidably inside the first cylinder 21A. This first piston 22A is configured to rotate eccentrically with respect to the rotation center of the rotating shaft 40 inside the first cylinder 21A. Hereinafter, rotational motion eccentric with respect to the rotation center of the rotating shaft 40 will be referred to as eccentric rotational motion. The first piston 22A rotates eccentrically inside the first cylinder chamber 55A due to the rotation of the rotating shaft 40.

[0033] The first piston 22A is connected to the rotating shaft 40 so that it can rotate inside the first cylinder 21A with a rotational phase shift of 180 degrees relative to the rotational phase of the second piston 22B when it rotates inside the second cylinder 21B.

[0034] The first vane 50A is inserted into the first vane groove 56A provided in the first cylinder 21A. The first vane 50A is arranged to reciprocate radially within the first vane groove 56A. The shape of the first vane 50A is that of a substantially rectangular parallelepiped, such that when mounted in the first vane groove 56A, its thickness in the circumferential direction of the first cylinder chamber 55A is smaller than the length of the first cylinder chamber 55A in the radial direction and in the axial direction.

[0035] The first vane 50A is positioned in the circumferential direction of the first cylinder 21A between the intake passage 52A and the first discharge passage 53A. The first vane 50A is positioned in the first vane groove 56A, which is formed to extend radially across the first cylinder 21A, and separates the first cylinder chamber 55A into a first low-pressure chamber 57A and a first high-pressure chamber 58A. The first low-pressure chamber 57A communicates with the intake passage 52A, and the first high-pressure chamber 58A communicates with the first discharge passage 53A. The first high-pressure chamber 58A is a compression chamber on the high-pressure side relative to the first low-pressure chamber 57A, and the first low-pressure chamber 57A is a compression chamber on the low-pressure side relative to the first high-pressure chamber 58A.

[0036] The first spring 51A is housed in the first spring hole 54A and presses the first vane 50A attached to the tip of the first spring 51A against the outer circumferential wall 122 of the first piston 22A.

[0037] The upper bearing 24A is positioned to abut against the upper end surface of the first cylinder 21A and closes the first cylinder chamber 55A. The upper bearing 24A rotatably supports the rotating shaft 40. The upper bearing 24A is provided with a valve (not shown) for releasing the refrigerant compressed by the first cylinder 21A and the first piston 22A. When this valve is opened, the compressor 1 can connect the space formed by the first cylinder 21A and the first piston 22A with the internal space of the first muffler 23A, which will be described later.

[0038] The upper bearing 24A is provided with a first muffler 23A through which the refrigerant compressed by the first cylinder 21A and the first piston 22A is discharged. The first muffler 23A is also provided with a refrigerant discharge section (not shown) that functions as a valve. As a result, the refrigerant compressed by the first cylinder 21A and the first piston 22A of the compressor 1 is discharged into the internal space of the first muffler 23A, and then released into the sealed container 10 from the refrigerant discharge section.

[0039] The second cylinder 21B is located below the first cylinder 21A. The second cylinder 21B is cylindrical and forms the second cylinder chamber 55B. The second cylinder 21B is fixed to the first cylinder 21A, for example, together with a partition plate 25.

[0040] The second cylinder 21B is a cylindrical member formed in a cylindrical shape with openings at both ends in the axial direction of the rotating shaft 40, and has a second cylinder chamber 55B for compressing the refrigerant inside. The second cylinder 21B is formed in a hollow cylindrical shape, and a through hole concentric with the axis of the rotating shaft 40 is formed in the center. The second cylinder 21B is closed by a lower bearing 24B positioned in contact with the lower end face of the second cylinder 21B and a partition plate 25 positioned in contact with the upper end face of the second cylinder 21B, thereby forming the second cylinder chamber 55B. The first cylinder chamber 55A and the second cylinder chamber 55B are collectively referred to as the cylinder chamber 55.

[0041] Inside the second cylinder chamber 55B are the second eccentric shaft portion 40B of the rotating shaft 40, which will be described later and will perform eccentric motion inside the second cylinder chamber 55B, and the second piston 22B which is fitted onto the second eccentric shaft portion 40B of the rotating shaft 40. Also inside the second cylinder chamber 55B are the second vanes 50B which partition the second cylinder chamber 55B and are formed between the inner circumferential wall 155 of the second cylinder chamber 55B and the outer circumferential wall 122 of the second piston 22B.

[0042] As shown in Figures 3 and 4, the second cylinder 21B has an internal suction passage 52B through which refrigerant is drawn in from the top surface of the second cylinder 21B, and a second discharge passage 53B through which refrigerant is discharged to the discharge pipe 4 via the internal space of the sealed container 10. The internal suction passage 52B of the second cylinder 21B is in communication with the connection path 25A of the partition plate 25. The compression mechanism 20 has the branch passage 52AA of the first cylinder 21A, the connection path 25A of the partition plate 25, and the internal suction passage 52B of the second cylinder 21B in communication, and refrigerant is drawn in from the suction pipe 2 to the internal suction passage 52B. The detailed configuration of the internal suction passage 52B will be described later.

[0043] A second vane groove 56B is formed in the second cylinder 21B. The second vane groove 56B is a groove that extends axially and radially in the second cylinder 21B. In the radial direction of the second cylinder 21B, one end of the second vane groove 56B opens into the second cylinder chamber 55B and communicates with the second cylinder chamber 55B, and the other end is provided with a second spring hole 54B.

[0044] The second spring hole 54B is formed at the radially outer end of the second vane groove 56B of the second cylinder 21B, and penetrates the second cylinder 21B axially, communicating with the second vane groove 56B. The second vane groove 56B houses the second vane 50B, and the second spring hole 54B houses the second spring 51B. The first vane groove 56A and the second vane groove 56B are collectively referred to as the vane groove 56.

[0045] The second piston 22B is fitted onto the second eccentric shaft portion 40B of the rotating shaft 40 and rotates eccentrically with the second eccentric shaft portion 40B to compress the refrigerant. The second piston 22B is formed in a cylindrical shape. The second piston 22B is mounted on the outer circumference of the second eccentric shaft portion 40B of the rotating shaft 40 inside the second cylinder 21B. When the rotating shaft 40 is rotated by the rotating electric machine 30, the second piston 22B rotates inside the second cylinder 21B along its inner circumferential wall 155.

[0046] The second piston 22B rotates slidably inside the second cylinder 21B. This second piston 22B is configured to perform eccentric rotational motion inside the second cylinder 21B. The second piston 22B rotates eccentrically inside the second cylinder chamber 55B due to the rotation of the rotating shaft 40.

[0047] The second piston 22B is connected to the rotating shaft 40 so that it can rotate inside the second cylinder 21B with a rotational phase shift of -180 degrees relative to the rotational phase of the first piston 22A when it rotates inside the first cylinder 21A.

[0048] The second vane 50B is inserted into the second vane groove 56B provided in the second cylinder 21B. The second vane 50B is arranged to reciprocate radially within the second vane groove 56B. The shape of the second vane 50B is that of a substantially rectangular parallelepiped, such that when mounted in the second vane groove 56B, its thickness in the circumferential direction of the second cylinder chamber 55B is smaller than the length of the second cylinder chamber 55B in the radial and axial directions.

[0049] The second vane 50B is positioned in the circumferential direction of the second cylinder 21B between the internal suction passage 52B and the second discharge passage 53B. The second vane 50B is positioned in the second vane groove 56B, which is formed to extend radially around the second cylinder 21B, and separates the second cylinder chamber 55B into a second low-pressure chamber 57B and a second high-pressure chamber 58B. The second low-pressure chamber 57B communicates with the internal suction passage 52B, and the second high-pressure chamber 58B communicates with the second discharge passage 53B. The second high-pressure chamber 58B is a compression chamber on the high-pressure side relative to the second low-pressure chamber 57B, and the second low-pressure chamber 57B is a compression chamber on the low-pressure side relative to the second high-pressure chamber 58B.

[0050] The second spring 51B is housed in the second spring hole 54B and presses the second vane 50B, which is attached to the tip of the second spring 51B, against the outer circumferential wall 122 of the second piston 22B.

[0051] The lower bearing 24B is positioned to abut against the lower end surface of the second cylinder 21B and closes the second cylinder chamber 55B. The lower bearing 24B rotatably supports the rotating shaft 40. The lower bearing 24B is also provided with a valve (not shown) for releasing the refrigerant compressed by the second cylinder 21B and the second piston 22B. When this valve is opened, the compressor 1 can connect the space formed by the second cylinder 21B and the second piston 22B with the internal space of the second muffler 23B, which will be described later.

[0052] The lower bearing 24B is provided with a second muffler 23B through which the refrigerant compressed by the second cylinder 21B and the second piston 22B is discharged. The internal space of this second muffler 23B is in communication with the internal space of the first muffler 23A via a refrigerant flow path (not shown) formed in the compression mechanism 20. As a result, the refrigerant compressed by the second cylinder 21B and the second piston 22B is discharged into the internal space of the second muffler 23B and then flows into the internal space of the first muffler 23A via the refrigerant flow path (not shown) formed in the compression mechanism 20. The refrigerant that has flowed into the internal space of the first muffler 23A is then released into the sealed container 10 from the refrigerant discharge section (not shown) of the first muffler 23A.

[0053] The partition plate 25 is formed in the shape of a plate or column. The partition plate 25 is positioned between the first cylinder 21A and the second cylinder 21B. The partition plate 25 is positioned so as to abut against the lower end surface of the first cylinder 21A and so as to abut against the upper end surface of the second cylinder 21B, thereby closing off the first cylinder chamber 55A and the second cylinder chamber 55B. The partition plate 25 is positioned between the first cylinder 21A and the second cylinder 21B, and closes off the shaft-side opening 59D (see Figure 6) and the second shaft-side opening 60D (see Figure 12), the first cylinder chamber 55A and the second cylinder chamber 55B, which will be described later.

[0054] The partition plate 25 has a connecting path 25A that communicates with a branched passage 52AA that branches off from the suction passage 52A of the first cylinder 21A. The connecting path 25A also communicates with an internal suction passage 52B formed in the second cylinder 21B. The connecting path 25A is a through hole formed in the partition plate 25. The connecting path 25A connects the branched passage 52AA of the first cylinder 21A with the internal suction passage 52B of the second cylinder 21B. The connecting path 25A connects the suction passage 52A of the first cylinder 21A with the internal suction passage 52B of the second cylinder 21B.

[0055] (Rotating electric machine 30) The rotating electric motor 30 is placed inside the sealed container 10 and is used to drive the compression mechanism 20. The rotating electric motor 30 is a motor that generates rotational driving force on the rotating shaft 40 using power supplied from an external power source and transmits the rotational driving force to the compression mechanism 20 via the rotating shaft 40. For example, a brushless DC motor is used for the rotating electric motor 30.

[0056] The rotating electric machine 30 has a rotor 31 that transmits its own rotation to the rotating shaft 40, and a stator 32 which is made of a laminated iron core with multiple phase windings attached. The stator 32 is formed in a hollow cylindrical shape when viewed from above. The rotor 31 is rotatably mounted inside the stator 32 and rotates by magnetic action.

[0057] In the rotating electric machine 30, power supplied from an external power source is supplied to the stator 32, causing the rotor 31 to rotate inside the stator 32. In the rotating electric machine 30, current is supplied from the power source (not shown) to windings provided on the laminated iron core of the stator 32, causing a rotating magnetic field to form on the stator 32. Thus, in the rotating electric machine 30, for example, the rotating magnetic field of the stator 32 acts on the permanent magnets provided on the rotor 31, causing the rotor 31 to rotate. The rotation of the rotor 31 is transmitted to the first piston 22A and the second piston 22B via the rotating shaft 40, causing the first piston 22A and the second piston 22B to perform eccentric rotational motion.

[0058] (Rotation axis 40) The rotating shaft 40 transmits power from the rotating electric machine 30 to the compression mechanism 20. The rotating shaft 40 is connected to the rotating electric machine 30 and rotates using the power of the rotating electric machine 30. The rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30 and rotates together with the rotor 31.

[0059] In the compressor 1 of Embodiment 1, the upper end of the rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30. As a result, the rotating shaft 40 rotates together with the rotation of the rotor 31. Note that the rotating shaft 40 shown in Figure 1 rotates around an axis that extends in the vertical direction of the paper as its center of rotation. The lower end of the rotating shaft 40 is connected to the compression mechanism 20. More specifically, the lower end of the rotating shaft 40 is rotatably supported by the upper bearing 24A and lower bearing 24B of the compression mechanism 20.

[0060] As shown in Figure 1, in the compressor 1 of Embodiment 1, the rotating shaft 40 has a first eccentric shaft portion 40A and a second eccentric shaft portion 40B between the portion where it is rotatably supported by the upper bearing 24A and the portion where it is rotatably supported by the lower bearing 24B. The first eccentric shaft portion 40A and the second eccentric shaft portion 40B are portions that are eccentric with respect to the center of the main part of the rotating shaft 40.

[0061] The rotating shaft 40 is connected such that the first piston 22A is able to rotate eccentrically to the first eccentric shaft portion 40A, and the second piston 22B is able to rotate eccentrically to the second eccentric shaft portion 40B. In other words, the rotating shaft 40 is connected such that the first piston 22A and the second piston 22B are able to rotate eccentrically between the portion where it is rotatably supported by the upper bearing 24A and the portion where it is rotatably supported by the lower bearing 24B.

[0062] As a result, the rotor 31 of the compressor 1 rotates along with the rotating shaft 40, causing the first piston 22A and the second piston 22B to rotate eccentrically. The compressor 1 compresses the refrigerant by the first cylinder 21A and the first piston 22A, and then compresses the refrigerant by the second cylinder 21B and the second piston 22B. In other words, the compression mechanism 20 compresses the refrigerant drawn in from the outside using the power of the rotating electric machine 30 transmitted by the rotating shaft 40.

[0063] The rotating shaft 40 has an oil supply hole 42 formed at one end 41 of the rotating shaft 40. The oil supply hole 42 opens at the end 41, which is one end of the rotating shaft 40. The end 41 corresponds to the first end. In the compressor 1 of this embodiment 1, the end 41 is the lower end of the rotating shaft 40. The oil supply hole 42 extends along the rotation center of the rotating shaft 40.

[0064] Furthermore, the rotating shaft 40 has a first oil inlet 43 and a second oil inlet 44. The first oil inlet 43 and the second oil inlet 44 serve as passages for supplying the refrigerant oil 6, which has been drawn into the oil hole 42, to the sliding part of the compression mechanism 20. One end of the first oil inlet 43 and the second oil inlet 44 communicates with the oil hole 42. The other end of the first oil inlet 43 and the second oil inlet 44 opens on the outer circumferential surface of the rotating shaft 40 at a location facing the compression mechanism 20. In this embodiment 1 of the compressor 1, the other end of the first oil inlet 43 opens at a location facing the upper bearing 24A of the compression mechanism 20. The other end of the second oil inlet 44 opens at a location facing the lower bearing 24B of the compression mechanism 20.

[0065] (Suction pipe 2) The suction pipe 2 penetrates the sealed container 10 and is connected to the compression mechanism 20, serving as a refrigerant flow path. The suction pipe 2 supplies refrigerant into the sealed container 10. As described above, the suction pipe 2 is connected to the body portion 12 of the sealed container 10. One end of the suction pipe 2 communicates with the first cylinder 21A of the compression mechanism 20. The other end of the suction pipe 2 communicates with the intake muffler 3. The suction pipe 2 may be a circular pipe with a circular cross-section, or it may be a non-circular pipe with an elliptical or oblong cross-section.

[0066] (Discharge piping 4) The discharge pipe 4 is a pipe that discharges the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10. The discharge pipe 4 is a pipe that discharges the high-temperature, high-pressure refrigerant inside the sealed container 10 to the outside of the sealed container 10.

[0067] (Intake muffler 3) The intake muffler 3 functions as a muffler that reduces refrigerant noise and other sounds generated when refrigerant flows into the compressor 1. The intake muffler 3 also functions as an accumulator capable of storing liquid refrigerant. The intake muffler 3 is connected to and communicates with the intake pipe 2.

[0068] (Centrifugal pump 45) The centrifugal pump 45 is installed inside the oil supply hole 42 of the rotating shaft 40. The centrifugal pump 45 is formed, for example, by twisting a plate-shaped member. The centrifugal pump 45 is a fluid machine that uses the centrifugal force generated by the rotational motion of the rotating shaft 40 to draw up the refrigerant oil 6, which is used as lubricating oil, stored at the bottom 13 of the sealed container 10.

[0069] The refrigerant oil 6 drawn up into the oil supply hole 42 by the centrifugal pump 45 is supplied to the sliding parts of the compression mechanism 20. Specifically, a portion of the refrigerant oil 6 drawn up into the oil supply hole 42 is supplied to the sliding part between the upper bearing 24A and the rotating shaft 40 of the compression mechanism 20 through the first oil supply port 43. In addition, a portion of the refrigerant oil 6 drawn up into the oil supply hole 42 is supplied to the sliding part between the lower bearing 24B and the rotating shaft 40 of the compression mechanism 20 through the second oil supply port 44. As the refrigerant oil 6, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, and polyol ester-based lubricants can be used.

[0070] [Operation of Compressor 1] In the compressor 1, refrigerant is drawn into the compressor 1 by the eccentric rotational motion of the first piston 22A and the second piston 22B. Specifically, in the compressor 1, the eccentric rotational motion of the first piston 22A and the second piston 22B causes low-pressure refrigerant from outside the compressor 1 to flow into the intake muffler 3. Then, in the compressor 1, the low-pressure gaseous refrigerant from the low-pressure refrigerant that has flowed into the intake muffler 3 flows into the compression mechanism 20 of the compressor 1 via the intake pipe 2.

[0071] A portion of the gaseous refrigerant flowing into the compression mechanism 20 is compressed in the first cylinder 21A and the first piston 22A to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant flows into the internal space of the first muffler 23A via the valve of the upper bearing 24A. The high-temperature, high-pressure gaseous refrigerant that has flowed into the internal space of the first muffler 23A is released into the internal space of the sealed container 10 from a refrigerant discharge section (not shown) provided in the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant released into the internal space of the sealed container 10 then moves to the upper part of the space inside the sealed container 10 via gaps such as those in the rotating electric machine 30, and is discharged from the discharge pipe 4.

[0072] The remaining gaseous refrigerant that has flowed into the compression mechanism 20 is compressed by the second cylinder 21B and the second piston 22B to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant flows into the internal space of the second muffler 23B through the valve of the lower bearing 24B. The high-temperature, high-pressure gaseous refrigerant that has flowed into the internal space of the second muffler 23B is sent from the internal space of the second muffler 23B through the refrigerant flow path (not shown) to the internal space of the first muffler 23A.

[0073] The high-temperature, high-pressure gaseous refrigerant supplied to the first muffler 23A is released into the internal space of the sealed container 10 from a refrigerant discharge section (not shown) provided in the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant released into the internal space of the sealed container 10 then moves to the upper part of the space inside the sealed container 10 through gaps such as those in the rotating electric machine 30, and is discharged from the discharge pipe 4.

[0074] Furthermore, the refrigerant oil 6 stored at the bottom 13 of the sealed container 10 is drawn up from the lower end of the oil supply hole 42 by a centrifugal pump 45 that rotates together with the rotating shaft 40. The refrigerant oil 6 drawn up from the lower end of the oil supply hole 42 flows as lubricant between the upper bearing 24A and the rotating shaft 40 from the first oil supply port 43. The refrigerant oil 6 also flows between the lower bearing 24B and the rotating shaft 40 from the second oil supply port 44. As the refrigerant oil 6 flows between these, the rotating shaft 40 can smoothly transmit rotational driving force to the first piston 22A and the second piston 22B.

[0075] Furthermore, a portion of the refrigerant oil 6 that flows from the first oil inlet 43 between the upper bearing 24A and the rotating shaft 40 flows between the upper bearing 24A and the upper surface of the first piston 22A. Also, a portion of the refrigerant oil 6 that flows from the second oil inlet 44 between the lower bearing 24B and the rotating shaft 40 flows between the lower bearing 24B and the lower surface of the second piston 22B. The refrigerant oil 6 is used to smoothly rotate the first piston 22A and the second piston 22B, but a portion of the refrigerant oil 6 is compressed together with the low-pressure gaseous refrigerant and discharged while contained in the high-temperature, high-pressure gaseous refrigerant.

[0076] [Detailed configuration of the intake passage 52A of the first cylinder 21A] Figure 5 is a perspective view of the first cylinder 21A of the compressor 1 according to Embodiment 1. Figure 6 is a partially enlarged view of the suction passage 52A of the compressor 1 according to Embodiment 1. Figure 7 is a conceptual diagram of the suction passage 52A of the compressor 1 according to Embodiment 1. Note that Figure 5 is a perspective view of the first cylinder 21A as seen from the partition plate 25 side. Also, Figure 7 is a conceptual diagram of the suction passage 52A as seen from the side where the rotating electric machine 30 is located. Next, the configuration of the suction passage 52A of the first cylinder 21A will be described in detail using Figures 5 to 7.

[0077] The compressor 1 has an intake passage 52A that leads from the outer circumferential surface 156 of the first cylinder 21A to the first cylinder chamber 55A, and an internal intake passage 52B formed in the second cylinder 21B that leads from the upper surface of the second cylinder 21B to the second cylinder chamber 55B. The compressor 1 also has a connecting path 25A formed in the partition plate 25 that connects the intake passage 52A and the internal intake passage 52B.

[0078] The first cylinder 21A has an intake passage 52A that connects the outside of the first cylinder 21A to the first cylinder chamber 55A. An intake pipe 2 is press-fitted into the intake passage 52A. The intake passage 52A extends radially inward from the outer circumferential surface of the first cylinder 21A and has an intake hole 61 to which the intake pipe 2 is connected, and a constricted portion 59 that forms a space connecting the intake hole 61 and the first cylinder chamber 55A.

[0079] As shown in Figures 6 and 7, the intake passage 52A includes an intake hole 61 extending radially inward from the outer circumferential surface 156 of the first cylinder 21A, and a throttling portion 59 formed radially inward of the intake hole 61, which connects the intake hole 61 with the first low-pressure chamber 57A. In other words, the intake passage 52A includes an intake hole 61 and a throttling portion 59 formed radially inward of the intake hole 61, which connects the intake hole 61 with the first cylinder chamber 55A.

[0080] The intake hole 61 is a hole that extends radially inward from the outer circumferential surface 156 of the first cylinder 21A. The intake hole 61 is a hole that connects the outside of the first cylinder 21A with the throttling portion 59. The tip of the intake pipe 2 is inserted into the intake hole 61. The intake hole 61 is a hole that connects the intake pipe 2 with the throttling portion 59.

[0081] The opening shape of the intake hole 61, which serves as the inlet for the intake passage 52A, only needs to match the shape of the intake pipe 2. Even if the opening shape of the intake hole 61 in the intake passage 52A is not circular to match the shape of the intake pipe 2, the shape of the throttling portion 59, which will be described later, can still be formed.

[0082] The constricted portion 59 has a pair of constricted side portions 59B that form both inner surfaces of the constricted portion 59 and are formed to approach each other as they extend radially inward from the first cylinder 21A. The constricted portion 59 is also composed of the pair of constricted side portions 59B and has an axial-side opening 59D that opens at one end of the rotating shaft 40 in the axial direction. The constricted portion 59 is also composed of the pair of constricted side portions 59B and has an inner opening 59C that opens radially inward from the first cylinder 21A to communicate with the first cylinder chamber 55A and is formed to connect with the axial-side opening 59D. The constricted portion 59 also has a constricted top portion 59A, which is a plate-shaped closing wall portion 150 provided at the other end of the rotating shaft 40 in the axial direction to close the constricted portion 59 in the axial direction of the rotating shaft 40.

[0083] The throttling section 59 has an opening on the outer surface of the first cylinder 21A on the lower and radially inward sides, a throttling section top 59A on the upper side, and a pair of throttling section side portions 59B on both inner sides that move closer to each other as they move radially inward. That is, the throttling section 59 has an opening on the partition plate 25 side of the first cylinder 21A and the inner circumferential wall 155 of the first cylinder chamber 55A, and a throttling section top 59A on the upper bearing 24A side. The throttling section 59 has a pair of throttling section side portions 59B that face each other in the circumferential direction. The pair of throttling section side portions 59B are formed so that they move closer to each other as they move radially outward to inward. In the compressor 1 of Embodiment 1, the throttling section top 59A constitutes the closing wall portion 150 of the throttling section 59.

[0084] When the first cylinder 21A is viewed in the axial direction, of the pair of throttling side portions 59B, the throttling side portion 59B1 on the side furthest from the first vane groove 56A in the circumferential direction of the first cylinder 21A is inclined to approach the first vane groove 56A as it moves from the radially outward direction inward. As shown in Figure 7, when the first cylinder 21A is viewed in plan, of the pair of throttling side portions 59B, the throttling side portion 59B1 on the side furthest from the first vane groove 56A is inclined with respect to the axis J1 of the intake passage 52A more than the throttling side portion 59B2 on the side closer to the first vane groove 56A.

[0085] The constricted portion 59 has an inner opening 59C and an axial-side opening 59D. A pair of constricted portion side portions 59B constitute the axial-side opening 59D and the inner opening 59C. The inner opening 59C is an opening formed in the inner circumferential wall 155. The inner opening 59C is an opening formed on the inner surface of the first cylinder 21A and is an opening that connects the internal space of the constricted portion 59 to the first cylinder chamber 55A. As shown in Figure 7, the first cylinder 21A is formed such that the inner opening 59C is biased toward the first vane groove 56A side with respect to the axis J1 of the intake passage 52A.

[0086] The shaft-side opening 59D is an opening formed on the outer surface of the first cylinder 21A on the partition plate 25 side. In the compression mechanism 20, the shaft-side opening 59D is covered and closed by the plate surface of the partition plate 25. The throttling portion 59 is formed such that the shaft-side opening 59D and the inner opening 59C are connected in the axial and radial directions of the rotating shaft 40. That is, the throttling portion 59 is formed such that the shaft-side opening 59D and the inner opening 59C are connected at the radial inner circumferential end and the end on the partition plate 25 side of the first cylinder 21A.

[0087] The top portion 59A of the constricted section is the part that closes one end of the constricted section 59 in the axial direction of the rotating shaft 40. The top portion 59A of the constricted section is formed in a plate shape. The top portion 59A of the constricted section forms the outer wall surface on the upper bearing 24A side of the first cylinder 21A in the axial direction of the rotating shaft 40. The top portion 59A of the constricted section is a wall portion that connects the constricted section side portion 59B1 on the side of the constricted section 59 furthest from the first vane groove 56A and the constricted section side portion 59B2 on the side of the constricted section 59 furthest from the first vane groove 56A at the end of the constricted section 59 on the upper bearing 24A side in the axial direction of the rotating shaft 40. The top portion 59A of the constricted section abuts against the upper bearing 24A in the compression mechanism 20.

[0088] The top portion 59A of the constricted section contributes to improving the rigidity of the first cylinder 21A regardless of which axial end face the first cylinder 21A is provided on. However, from the viewpoint of machinability and rigidity improvement, it is preferable to provide it on the side opposite to the side where the branched passage 52AA is formed.

[0089] In the axial direction of the rotating shaft 40, one end of the constricted portion 59 is open by the shaft-side opening 59D, and the other end is closed by the top of the constricted portion 59A. In the radial direction of the rotating shaft 40, one end of the constricted portion 59 communicates with the intake hole 61, and the other end communicates with the first cylinder chamber 55A.

[0090] Figure 8 is a side view of the first cylinder 21A of the compressor 1 according to Embodiment 1, as seen from the inner circumferential surface side. The dimensions of the suction passage 52A of the first cylinder 21A will be explained using Figures 6 and 8.

[0091] In the inner circumferential wall 155 of the first cylinder 21A, the portion between the first vane groove 56A and the inner opening 59C in the circumferential direction of the first cylinder 21A is defined as the intermediate wall portion 155A. The length of the intermediate wall portion 155A in the circumferential direction of the first cylinder 21A is defined as the circumferential length A. The circumferential length A is the distance between the first vane groove 56A and the inner opening 59C in the circumferential direction of the first cylinder 21A. In addition, in the first cylinder 21A, the thickness of the plate of the top portion 59A of the constricted section in the axial direction of the rotating shaft 40 is defined as the thickness B. In the first cylinder 21A, the diameter of the intake hole 61 is defined as the diameter C.

[0092] The first cylinder 21A is formed such that the circumferential length A, which is the distance between the first vane groove 56A and the inner opening 59C in the circumferential direction of the first cylinder 21A, is greater than the thickness B, which is the thickness of the plate at the top of the constricted portion 59A in the axial direction of the rotating shaft 40. In other words, the first cylinder 21A is formed such that the thickness B, which is the thickness of the plate at the top of the constricted portion 59A in the axial direction of the rotating shaft 40, is less than the circumferential length A, which is the distance between the first vane groove 56A and the inner opening 59C in the circumferential direction of the first cylinder 21A. The first cylinder 21A is formed such that the relationship "circumferential length A > thickness B" holds.

[0093] The intermediate wall portion 155A between the first vane groove 56A and the inner opening 59C is, as described above, the wall of the portion that constitutes the circumferential length A. The wall of the first cylinder 21A that constitutes the intermediate wall portion 155A is subjected to a pressing force from the first vane 50A due to the pressure difference between the first low-pressure chamber 57A and the first high-pressure chamber 58A. The top portion 59A of the constricted section has a thickness B as described above. The top portion 59A of the constricted section is subjected to a pressing force from the first vane 50A, but it is subjected to less pressing force from the first vane 50A than the wall of the portion that constitutes the intermediate wall portion 155A.

[0094] Therefore, the top of the constricted section 59A does not need to be as thick as the wall of the portion constituting the circumferential length A. By making the top of the constricted section 59A thinner than the wall of the portion constituting the intermediate wall 155A, the compressor 1 can reduce the weight of the first cylinder 21A. Furthermore, the top of the constricted section 59A does not need to be as thick as the wall of the portion constituting the circumferential length A. By making the top of the constricted section 59A thinner than the wall of the portion constituting the intermediate wall 155A, the compressor 1 can increase the diameter of the intake hole 61 formed in the first cylinder 21A compared to a case where this configuration is not present.

[0095] Furthermore, the first cylinder 21A is formed such that the thickness B of the plate at the top of the constricted portion 59A in the axial direction of the rotating shaft 40 is smaller than the diameter C of the intake hole 61. The first cylinder 21A is formed such that the diameter C of the intake hole 61 is larger than the thickness B of the plate at the top of the constricted portion 59A in the axial direction of the rotating shaft 40. In other words, the first cylinder 21A is formed such that the relationship "diameter C > thickness B" holds.

[0096] The first cylinder 21A is formed such that "diameter C > thickness B," which allows for a larger area for forming the intake hole 61 compared to a case where this relationship does not exist. In other words, the first cylinder 21A is formed such that "diameter C > thickness B," which allows for a larger diameter for the intake hole 61 formed in the first cylinder 21A compared to a case where this relationship does not exist.

[0097] The refrigerant flowing in from the suction pipe 2 connected to the first cylinder 21A flows into the first high-pressure chamber 58A through the suction passage 52A, is compressed inside the first high-pressure chamber 58A by the rotation of the first piston 22A, and is discharged as high-pressure refrigerant from the first discharge passage 53A. Thus, since the refrigerant moves inside the suction passage 52A of the compressor 1, the larger the diameter of the suction pipe 2 of the compressor 1, the smaller the flow pressure loss, so a larger diameter of the suction pipe 2 is desirable.

[0098] Furthermore, since the refrigerant moves through the suction passage 52A of the compressor 1, the larger the diameter of the passage inside the suction passage 52A, the smaller the flow pressure loss. Therefore, a larger diameter of the passage inside the suction passage 52A is desirable. In other words, since the refrigerant moves through the suction passage 52A of the compressor 1, the larger the cross-sectional area of ​​the passage inside the suction passage 52A, the smaller the flow pressure loss. Therefore, a larger cross-sectional area of ​​the passage inside the suction passage 52A is desirable.

[0099] Furthermore, in the first high-pressure chamber 58A, the intake, compression, and exhaust of refrigerant are repeatedly performed, and when the refrigerant is exhausted, there is a risk that the high-pressure refrigerant inside the sealed container 10 will flow back into the first high-pressure chamber 58A, which has finished compression and is now at a low pressure, from the first discharge passage 53A. In this case, the compressor 1 may experience a decrease in compressor efficiency due to the amount of refrigerant drawn in from the suction pipe 2 decreasing as the refrigerant that has flowed back into the first high-pressure chamber 58A enters the intake passage 52A. Therefore, in order to suppress the backflow of refrigerant into the first high-pressure chamber 58A when the refrigerant is exhausted, it is desirable for the inner opening 59C, which is the connection between the intake passage 52A and the first cylinder chamber 55A, to be close to the first vane groove 56A.

[0100] From the above, it is desirable for the compressor 1 to enlarge the intake passage 52A in the axial direction of the first cylinder 21A in order to improve the compressor efficiency. Furthermore, in order to improve the compressor efficiency, it is effective for the compressor 1 to have a throttling portion 59 at the inner circumference end of the intake passage 52A and to connect the intake passage 52A to the first cylinder chamber 55A at a position close to the first vane 50A.

[0101] On the other hand, if the intake hole 61 is enlarged or if the intake hole 61 is brought closer to the first vane groove 56A, the thickness of the wall between the intake hole 61 of the first cylinder 21A and the first vane groove 56A of the compressor 1 will decrease. In such cases, the compressor 1 may increase the risk of distortion of the first cylinder 21A due to external forces such as the press-fitting of the intake pipe 2 into the first cylinder 21A. Furthermore, in such cases, the compressor 1 may increase the risk of distortion of the first cylinder 21A due to external forces such as the pressing force of the first vane 50A against the first cylinder 21A caused by the differential pressure between the first low-pressure chamber 57A and the first high-pressure chamber 58A.

[0102] Therefore, the compressor 1 according to Embodiment 1 has a throttling portion 59 in the intake passage 52A. The intake passage 52A is formed such that the throttling portion 59 allows only one side of the first cylinder 21A in the axial direction to pass through, while the other side is walled by the top portion 59A of the throttling portion. The compressor 1 ensures the rigidity of the first cylinder 21A with the top portion 59A of the throttling portion, and the throttling portion 59 allows the intake passage 52A to be expanded in the axial direction, bringing the inner opening 59C, which is the connection portion with the first cylinder chamber 55A, closer to the first vane groove 56A.

[0103] Figure 9 is a perspective view of the first cylinder 21A of a modified example of the compressor 1 according to Embodiment 1. Figure 10 is a partially enlarged view of the suction passage 52A of the modified example of the compressor 1 according to Embodiment 1. The top of the throttling portion 59A may have a through-port 63 formed at its radially inward end, which penetrates the first cylinder 21A in the axial direction, as shown in Figures 9 and 10. The through-port 63 is a notched portion formed at the radially inward end of the top of the throttling portion 59A. The top of the throttling portion 59A is recessed radially outward at the through-port 63.

[0104] The through-hole 63 is an opening formed on the upper bearing 24A side of the first cylinder 21A. In the compression mechanism 20, the through-hole 63 is covered and closed by the plate surface of the upper bearing 24A.

[0105] [Detailed configuration of the internal intake passage 52B of the second cylinder 21B] Figure 11 is a perspective view of the second cylinder 21B of the compressor 1 according to Embodiment 1. Figure 12 is a partially enlarged view of the internal suction passage 52B of the compressor 1 according to Embodiment 1. Figure 13 is a conceptual diagram of the internal suction passage 52B of the compressor 1 according to Embodiment 1. Note that Figure 11 is a perspective view of the second cylinder 21B as seen from the partition plate 25 side. Also, Figure 13 is a conceptual diagram of the internal suction passage 52B as seen from the side where the lower bearing 24B is located. Next, the configuration of the internal suction passage 52B of the second cylinder 21B will be described in detail using Figures 11 to 13.

[0106] The second cylinder 21B has an internal intake passage 52B formed therein that leads from the upper surface of the second cylinder 21B to the second cylinder chamber 55B. The internal intake passage 52B has a communicating intake hole 62 that extends radially inward from the upper surface of the second cylinder 21B through the interior of the second cylinder 21B. The internal intake passage 52B also has a second throttling portion 60 formed radially inward of the communicating intake hole 62, which forms a space that connects the communicating intake hole 62 and the second cylinder chamber 55B. In other words, the internal intake passage 52B comprises a communicating intake hole 62 and a second throttling portion 60 formed radially inward of the communicating intake hole 62, which connects the communicating intake hole 62 and the second cylinder chamber 55B.

[0107] The communication suction hole 62 is a hole that extends radially inward from the upper surface of the second cylinder 21B through the inside of the second cylinder 21B. The communication suction hole 62 extends axially downward from the upper surface of the second cylinder 21B, and then extends radially inward from there. The communication suction hole 62 is a hole that connects the outside of the second cylinder 21B to the second throttling section 60. The communication suction hole 62 is a hole that connects the connection path 25A of the partition plate 25 (see Figure 4) to the second throttling section 60.

[0108] The second constricted portion 60 has a pair of second constricted portion side portions 60B that form both inner surfaces of the second constricted portion 60 and are formed to approach each other as they extend radially inward from the second cylinder 21B. The second constricted portion 60 is also composed of the pair of second constricted portion side portions 60B and has a second axial side opening 60D that opens at one end in the axial direction of the rotating shaft 40 and is closed by the partition plate 25. The second constricted portion 60 is also composed of the pair of second constricted portion side portions 60B and has a second inner opening 60C that opens radially inward from the second cylinder 21B to communicate with the second cylinder chamber 55B and is formed to connect with the second axial side opening 60D. The second constricted portion 60 also has a plate-shaped second closing wall portion 151 that is provided at the other end in the axial direction of the rotating shaft 40 to close the second constricted portion 60.

[0109] The second constricted portion 60 has an opening on the outer surface of the second cylinder 21B on the upper and radially inward sides, a constricted portion bottom 60A on the lower side, and a pair of second constricted portion side portions 60B on both inner sides that move closer to each other as they move radially inward. That is, the second constricted portion 60 has an opening on the partition plate 25 side of the second cylinder 21B and the inner circumferential wall 155 of the second cylinder chamber 55B, and a constricted portion bottom 60A on the lower bearing 24B side. The second constricted portion 60 has a pair of second constricted portion side portions 60B that face each other in the circumferential direction. The pair of second constricted portion side portions 60B are formed so that they move closer to each other as they move radially outward to inward.

[0110] When the second cylinder 21B is viewed in the axial direction, of the pair of second constriction side portions 60B, the second constriction side portion 60B1 on the side furthest from the second vane groove 56B in the circumferential direction of the second cylinder 21B is inclined to approach the second vane groove 56B as it moves from the radially outward direction inward. When the second cylinder 21B is viewed in plan, of the pair of second constriction side portions 60B, the second constriction side portion 60B1 on the side furthest from the second vane groove 56B is inclined with respect to the plane J2 on which the axis of the communication suction hole 62 extends, more so than the second constriction side portion 60B2 on the side closer to the second vane groove 56B.

[0111] The second constricted portion 60 has a second inner opening 60C and a second axial opening 60D. A pair of side portions 60B of the second constricted portion constitute the second axial opening 60D and the second inner opening 60C. The second inner opening 60C is an opening formed in the inner circumferential wall 155. The second inner opening 60C is an opening formed on the inner surface of the second cylinder 21B and is an opening that connects the internal space of the second constricted portion 60 with the second cylinder chamber 55B. As shown in Figure 13, the second cylinder 21B is formed such that the second inner opening 60C is biased towards the second vane groove 56B side with respect to the surface J2 on which the axis of the communication intake hole 62 extends.

[0112] The second shaft-side opening 60D is an opening formed on the outer surface of the second cylinder 21B on the partition plate 25 side. In the compression mechanism 20, the second shaft-side opening 60D is covered and closed by the plate surface of the partition plate 25. The second constriction section 60 is formed such that the second shaft-side opening 60D and the second inner opening 60C are connected in the axial and radial direction of the rotating shaft 40. That is, the second constriction section 60 is formed such that the second shaft-side opening 60D and the second inner opening 60C are connected at the radial inner circumferential end and the end on the partition plate 25 side of the second cylinder 21B.

[0113] The constriction bottom portion 60A is the part that closes one end of the second constriction portion 60 in the axial direction of the rotating shaft 40. The constriction bottom portion 60A is formed in a plate shape. The constriction bottom portion 60A forms the outer wall surface on the lower bearing 24B side of the second cylinder 21B in the axial direction of the rotating shaft 40. The constriction bottom portion 60A is a wall portion that connects the second constriction side portion 60B1 on the side furthest from the second vane groove 56B and the second constriction side portion 60B2 on the side closer to the second vane groove 56B at the end of the second constriction portion 60 on the lower bearing 24B side in the axial direction of the rotating shaft 40. The constriction bottom portion 60A is in contact with the lower bearing 24B in the compression mechanism 20.

[0114] The bottom of the constricted portion 60A contributes to improving the rigidity of the second cylinder 21B regardless of which axial end face the second cylinder 21B is provided on. However, from the viewpoint of machinability and rigidity improvement, it is preferable to provide it on the side opposite to the side where the communication intake hole 62 is formed.

[0115] In the axial direction of the rotating shaft 40, one end of the second constricted portion 60 is open by the second shaft side opening 60D, and the other end is closed by the constricted portion bottom 60A. In the radial direction of the rotating shaft 40, one end of the second constricted portion 60 is in communication with the communication intake hole 62, and the other end is in communication with the second cylinder chamber 55B.

[0116] In the inner circumferential wall 155 of the second cylinder 21B, the portion between the second vane groove 56B and the second inner opening 60C in the circumferential direction of the second cylinder 21B is defined as the intermediate wall portion 155B. The length of the intermediate wall portion 155B in the circumferential direction of the second cylinder 21B is defined as the circumferential length A2. The circumferential length A2 is the distance between the second vane groove 56B and the second inner opening 60C in the circumferential direction of the second cylinder 21B. In addition, in the second cylinder 21B, the thickness of the plate at the bottom 60A of the constricted portion in the axial direction of the rotating shaft 40 is defined as the thickness B2.

[0117] The second cylinder 21B is formed such that the circumferential length A2, which is the distance between the second vane groove 56B and the second inner opening 60C in the circumferential direction of the second cylinder 21B, is greater than the thickness B2, which is the thickness of the plate at the bottom 60A of the constricted portion in the axial direction of the rotating shaft 40. The second cylinder 21B is formed such that the thickness B2, which is the thickness of the plate at the bottom 60A of the constricted portion in the axial direction of the rotating shaft 40, is less than the circumferential length A2, which is the distance between the second vane groove 56B and the second inner opening 60C in the circumferential direction of the second cylinder 21B. The second cylinder 21B is formed such that the relationship "circumferential length A2 > thickness B2".

[0118] The intermediate wall portion 155B between the second vane groove 56B and the second inner opening 60C is, as described above, the wall of the portion constituting the circumferential length A2. The wall of the second cylinder 21B constituting the intermediate wall portion 155B is subjected to a pressing force from the second vane 50B due to the pressure difference between the second low-pressure chamber 57B and the second high-pressure chamber 58B. The constricted bottom portion 60A has a thickness B2 as described above. The constricted bottom portion 60A is subjected to a pressing force from the second vane 50B, but not as much as the wall of the portion constituting the intermediate wall portion 155B.

[0119] Therefore, the bottom of the constricted section 60A does not need to be as thick as the wall of the portion constituting the circumferential length A2. The compressor 1 can lighten the second cylinder 21B by making the bottom of the constricted section 60A thinner than the wall of the portion constituting the intermediate wall 155B. Furthermore, the bottom of the constricted section 60A does not need to be as thick as the wall of the portion constituting the circumferential length A2.

[0120] The refrigerant flowing in from the suction pipe 2 connected to the first cylinder 21A flows into the second high-pressure chamber 58B through the connection path 25A of the partition plate 25 and the internal suction passage 52B of the second cylinder 21B. The refrigerant flowing into the second high-pressure chamber 58B is compressed by the rotation of the second piston 22B inside the second high-pressure chamber 58B and discharged as high-pressure refrigerant from the second discharge passage 53B.

[0121] Furthermore, in the second high-pressure chamber 58B, the refrigerant is repeatedly drawn in, compressed, and exhausted. When the compressor 1 exhausts the refrigerant, there is a risk that the high-pressure refrigerant inside the sealed container 10 will flow back into the second high-pressure chamber 58B, which has finished compression and is now at a low pressure, from the second discharge passage 53B. In this case, the compressor 1 may experience a decrease in compressor efficiency due to the amount of refrigerant drawn in from the suction pipe 2 as the refrigerant that has flowed back into the second high-pressure chamber 58B enters the internal suction passage 52B. Therefore, in order to suppress the backflow of refrigerant into the second high-pressure chamber 58B when the compressor 1 is exhausted, it is desirable that the second inner opening 60C, which is the connection point between the internal suction passage 52B and the second cylinder chamber 55B, be close to the second vane groove 56B.

[0122] From the above, it is desirable for compressor 1 to expand the internal intake passage 52B in the axial direction of the second cylinder 21B in order to improve compressor efficiency. Furthermore, in order to improve compressor efficiency, it is effective for compressor 1 to have a second throttling section 60 at the inner circumference end of the internal intake passage 52B and to connect the internal intake passage 52B to the second cylinder chamber 55B at a position close to the second vane 50B.

[0123] On the other hand, if the communication suction hole 62 is enlarged or if the communication suction hole 62 is brought closer to the second vane groove 56B, the thickness of the wall between the communication suction hole 62 of the second cylinder 21B and the second vane groove 56B of the compressor 1 will decrease. In such a case, the compressor 1 may increase the risk of distortion of the second cylinder 21B due to external forces such as the pressing force of the second vane 50B against the second cylinder 21B caused by the differential pressure between the second low-pressure chamber 57B and the second high-pressure chamber 58B.

[0124] Therefore, the compressor 1 according to Embodiment 1 has a second throttling portion 60 in the internal suction passage 52B. The internal suction passage 52B is formed such that the second throttling portion 60 allows only one side of the second cylinder 21B in the axial direction to pass through, while the other side is walled by the bottom of the throttling portion 60A. The compressor 1 ensures the rigidity of the second cylinder 21B with the bottom of the throttling portion 60A, and the second throttling portion 60 allows the internal suction passage 52B to be expanded in the axial direction, bringing the second inner opening 60C, which is the connection portion with the second cylinder chamber 55B, closer to the second vane groove 56B.

[0125] Figure 14 is a perspective view of the second cylinder 21B of a modified example of the compressor 1 according to Embodiment 1. Figure 15 is a partially enlarged view of the internal suction passage 52B of the modified example of the compressor 1 according to Embodiment 1. The radially inward end of the throttling bottom 60A may form a second through-hole 63B that penetrates the second cylinder 21B in the axial direction, as shown in Figures 14 and 15. The second through-hole 63B is a notch formed at the radially inward end of the throttling bottom 60A. The throttling bottom 60A is recessed radially outward in the second through-hole 63B. That is, the throttling bottom 60A, which is the second closing wall 151, has a second through-hole 63B at its radially inward end that penetrates the second cylinder 21B in the axial direction.

[0126] The second through-hole 63B is an opening formed on the lower bearing 24B side of the second cylinder 21B. In the compression mechanism 20, the second through-hole 63B is covered and closed by the plate surface of the lower bearing 24B.

[0127] [Configuration of Refrigeration Cycle System 200] Figure 16 is a schematic diagram of a refrigeration cycle device 200 including a compressor 1 according to Embodiment 1. The refrigeration cycle device 200 includes a compressor 1, a heat exchanger from which the refrigerant compressed by the compressor 1 releases heat, a pressure reducer 203 such as an electric expansion valve that reduces the pressure of the refrigerant flowing out of the heat exchanger, and an evaporator from which the refrigerant flowing out of the pressure reducer 203 evaporates.

[0128] The refrigeration cycle unit 200 is used in a variety of applications, such as refrigerators or freezers, vending machines, air conditioning systems, refrigeration systems, and hot water supply systems. Figure 16 shows an example in which the refrigeration cycle unit 200 is used as an air conditioning system. Therefore, the refrigeration cycle unit 200 shown in Figure 16 is equipped with an indoor heat exchanger 204 that functions as a radiator during heating operation and an outdoor heat exchanger 202 that functions as an evaporator during heating operation.

[0129] Furthermore, the refrigeration cycle device 200 shown in Figure 16 is also capable of cooling operation. For this reason, the refrigeration cycle device 200 is equipped with a flow path switching device 201 such as a four-way switching valve. The flow path switching device 201 switches the heat exchanger connected to the discharge pipe 4, which is the refrigerant discharge port of the compressor 1, and switches the heat exchanger connected to the intake muffler 3, which is the refrigerant intake port of the compressor 1. During cooling operation, the indoor heat exchanger 204 functions as an evaporator, and the outdoor heat exchanger 202 functions as a heat radiator.

[0130] The refrigeration cycle device 200 includes a compressor 1, an outdoor heat exchanger 202 that performs heat exchange between outdoor air and refrigerant flowing inside, a pressure reducer 203 that reduces the pressure of the refrigerant flowing inside, and an indoor heat exchanger 204 that performs heat exchange between indoor air and refrigerant flowing inside.

[0131] The refrigeration cycle device 200 consists of a compressor 1, a flow path switching device 201, an outdoor heat exchanger 202, a pressure reducer 203, and an indoor heat exchanger 204, all connected via refrigerant piping to form a refrigerant circuit 210 through which the refrigerant circulates.

[0132] When the refrigeration cycle unit 200 is used as an air conditioning system, for example, the indoor heat exchanger 204 is mounted in the indoor unit. Also, for example, the flow path switching device 201, the outdoor heat exchanger 202, and the pressure reducer 203 are mounted in the outdoor unit. Furthermore, for example, R407C refrigerant, R410A refrigerant, or R32 refrigerant may be used in the refrigeration cycle unit 200, but the refrigerant used is not limited to these. The operation of the refrigeration cycle unit 200 during heating and cooling operations will be described below.

[0133] When the refrigeration cycle unit 200 performs heating operation, the flow path switching device 201 switches to the flow path shown by the solid line in Figure 16. As a result, the discharge pipe 4 of the compressor 1 is connected to the indoor heat exchanger 204, and the intake muffler 3 of the compressor 1 is connected to the outdoor heat exchanger 202. In other words, the indoor heat exchanger 204 functions as a heat radiator, and the outdoor heat exchanger 202 functions as an evaporator.

[0134] In this state, when the high-temperature, high-pressure gaseous refrigerant compressed by the compressor 1 is discharged from the compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the indoor heat exchanger 204. The high-temperature, high-pressure gaseous refrigerant that flows into the indoor heat exchanger 204 condenses while releasing heat into the indoor air, becoming a high-pressure liquid refrigerant and flowing out of the indoor heat exchanger 204. At this time, the indoor air is warmed by the heat released by the refrigerant. Note that some types of refrigerants, such as carbon dioxide refrigerant, do not condense when releasing heat. When a refrigerant that condenses when releasing heat is used, the heat exchanger may be called a condenser.

[0135] The high-pressure liquid refrigerant flowing out of the indoor heat exchanger 204 flows into the pressure reducer 203. The high-pressure liquid refrigerant flowing into the pressure reducer 203 is then reduced in pressure to become a low-temperature, low-pressure gas-liquid two-phase refrigerant, which flows out of the pressure reducer 203. The low-temperature, low-pressure gas-liquid two-phase refrigerant that flows out of the pressure reducer 203 flows into the outdoor heat exchanger 202. The low-temperature, low-pressure gas-liquid two-phase refrigerant that flows into the outdoor heat exchanger 202 absorbs heat from the outside air and evaporates, flowing out of the outdoor heat exchanger 202 as a low-pressure gaseous refrigerant or gas-liquid two-phase refrigerant.

[0136] The low-pressure gaseous refrigerant or gas-liquid two-phase refrigerant flowing out from the outdoor heat exchanger 202 is drawn into the intake muffler 3 of the compressor 1. The low-pressure gaseous refrigerant drawn into the intake muffler 3 of the compressor 1 is then compressed by the compression mechanism 20 of the compressor 1, becoming a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is then discharged again from the compressor 1. In other words, when the refrigeration cycle device 200 is operating in heating mode, the refrigerant circulates as shown by the solid arrows in Figure 16.

[0137] When the refrigeration cycle unit 200 performs cooling operation, the flow path switching device 201 switches to the flow path shown by the dashed line in Figure 16. As a result, the discharge pipe 4 of the compressor 1 is connected to the outdoor heat exchanger 202, and the intake muffler 3 of the compressor 1 is connected to the indoor heat exchanger 204. In other words, the outdoor heat exchanger 202 functions as a heat radiator, and the indoor heat exchanger 204 functions as an evaporator.

[0138] In this state, when the high-temperature, high-pressure gaseous refrigerant compressed by the compressor 1 is discharged from the compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the outdoor heat exchanger 202. The high-temperature, high-pressure gaseous refrigerant that flows into the outdoor heat exchanger 202 condenses while releasing heat into the outside air, becoming a high-pressure liquid refrigerant and flowing out of the outdoor heat exchanger 202.

[0139] The high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 202 flows into the pressure reducer 203. The high-pressure liquid refrigerant flowing into the pressure reducer 203 is then reduced in pressure to become a low-temperature, low-pressure gas-liquid two-phase refrigerant, which flows out of the pressure reducer 203. The low-temperature, low-pressure gas-liquid two-phase refrigerant that flows out of the pressure reducer 203 flows into the indoor heat exchanger 204. The low-temperature, low-pressure gas-liquid two-phase refrigerant that flows into the indoor heat exchanger 204 absorbs heat from the indoor air and evaporates, flowing out of the indoor heat exchanger 204 as a low-pressure gaseous refrigerant or gas-liquid two-phase refrigerant. At this time, the indoor air is cooled by the heat absorbed by the refrigerant.

[0140] The low-pressure gaseous refrigerant or gas-liquid two-phase refrigerant flowing out from the indoor heat exchanger 204 is drawn into the intake muffler 3 of the compressor 1. The low-pressure gaseous refrigerant drawn into the intake muffler 3 of the compressor 1 is then compressed by the compression mechanism 20 of the compressor 1, becoming a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is then discharged again from the compressor 1. In other words, when the refrigeration cycle device 200 is in cooling operation, the refrigerant circulates as shown by the dashed arrow in Figure 16.

[0141] [Effects of Compressor 1] The compressor 1 has a throttling section 59 in the refrigerant intake passage 52A formed in the first cylinder 21A. The throttling section 59 has a pair of throttling section side portions 59B that form both inner surfaces of the throttling section 59 and are formed to approach each other as they extend radially inward from the first cylinder 21A. The throttling section 59 is also composed of the pair of throttling section side portions 59B and has an axial-side opening 59D that opens at one end in the axial direction of the rotating shaft 40. The throttling section 59 is also composed of the pair of throttling section side portions 59B and has an inner opening 59C that opens radially inward from the first cylinder 21A to communicate with the first cylinder chamber 55A and is formed to connect with the axial-side opening 59D. The throttling section 59 also has a throttling section top portion 59A, which is a plate-shaped closing wall portion 150 provided at the other end in the axial direction of the rotating shaft 40 to close the throttling section 59. The constricted portion 59 expands the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 through the shaft-side opening 59D and the inner opening 59C, while ensuring the rigidity of the first cylinder 21A with the closing wall portion 150, thereby increasing the strength of the first cylinder 21A.

[0142] The compressor 1 ensures the rigidity of the first cylinder 21A by the closed wall portion 150 of the throttling portion 59, thereby increasing the strength of the first cylinder 21A. As a result, the compressor 1 can suppress deformation of the first cylinder 21A due to external forces such as the pressing force of the first vane 50A against the first cylinder 21A caused by the differential pressure between the first low-pressure chamber 57A and the first high-pressure chamber 58A, thereby increasing the strength of the first cylinder 21A.

[0143] The compressor 1 ensures the rigidity of the first cylinder 21A by the closed wall portion 150 of the throttling portion 59, thereby increasing the strength of the first cylinder 21A. Therefore, even when the suction pipe 2 is inserted into the suction passage 52A of the first cylinder 21A while shaking, the compressor 1 can suppress deformation of the first cylinder 21A.

[0144] In the constricted section 59, if closing wall sections 150 are provided at both ends in the axial direction of the rotating shaft 40, the opening area and volume of the constricted section 59 will decrease, resulting in increased pressure loss in the compressor 1 and making it difficult for the refrigerant to enter the first cylinder chamber 55A. The compressor 1 has an axial-side opening 59D at one end of the constricted section 59 and a closing wall section 150 at the other end in the axial direction of the rotating shaft 40. Therefore, the compressor 1 can increase the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 by using the axial-side opening 59D, while ensuring the rigidity of the first cylinder 21A with the closing wall section 150, thereby increasing the strength of the first cylinder 21A.

[0145] Furthermore, the first cylinder 21A has an intake passage 52A and a branch passage 52AA that branches off from the intake passage 52A. The second cylinder 21B has an internal intake passage 52B that leads from the upper surface of the second cylinder 21B to the second cylinder chamber 55B, and the partition plate 25 has a connecting path 25A that connects the branch passage 52AA and the internal intake passage 52B. Even if a two-cylinder rotary compressor is used for the compressor 1, the compressor 1 can increase the strength of the first cylinder 21A by ensuring the rigidity of the first cylinder 21A with the closing wall portion 150 while increasing the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40.

[0146] Furthermore, the compressor 1 has a second throttling section 60 in the internal refrigerant suction passage 52B formed in the second cylinder 21B. The second throttling section 60 has a pair of second throttling section side portions 60B that constitute both inner surfaces of the second throttling section 60 and are formed to move closer to each other as they are directed radially inward of the second cylinder 21B. The second throttling section 60 is also composed of the pair of second throttling section side portions 60B and has a second shaft-side opening 60D that opens at one end in the axial direction of the rotating shaft 40 and is closed by a partition plate 25. The second throttling section 60 is also composed of the pair of second throttling section side portions 60B and has a second inner opening 60C that opens radially inward of the second cylinder 21B to communicate with the second cylinder chamber 55B and is formed to connect with the second shaft-side opening 60D. Furthermore, the second constricted portion 60 has a constricted portion bottom portion 60A, which is a plate-shaped second closing wall portion 151 provided at the other end of the rotating shaft 40 in the axial direction to close the second constricted portion 60.

[0147] The second constriction section 60 expands the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 by the second shaft-side opening 60D and the second inner opening 60C, while ensuring the rigidity of the second cylinder 21B by the second closing wall section 151, thereby increasing the strength of the second cylinder 21B.

[0148] The compressor 1 ensures the rigidity of the second cylinder 21B by the second closing wall portion 151 of the second throttling portion 60, thereby increasing the strength of the second cylinder 21B. As a result, the compressor 1 can suppress deformation of the second cylinder 21B due to external forces such as the pressing force of the second vane 50B against the second cylinder 21B caused by the differential pressure between the second low-pressure chamber 57B and the second high-pressure chamber 58B, thereby increasing the strength of the second cylinder 21B.

[0149] Furthermore, the suction pipe 2 is press-fitted into the suction passage 52A of the first cylinder 21A. Even when the suction pipe 2 is press-fitted into the suction passage 52A of the first cylinder 21A, the compressor 1 has a throttling section 59 top section 59A which is a closing wall section 150, so deformation of the first cylinder 21A can be suppressed.

[0150] Furthermore, the top portion 59A of the constricted section, which is the closing wall portion 150, has a through portion 63 at its radially inward end that penetrates the first cylinder 21A in the axial direction. In the first cylinder 21A, the refrigerant that reaches the through portion 63 flows more easily to both sides in the axial direction of the first cylinder 21A, and this refrigerant flows from the lower surface of the upper bearing 24A to the upper surface of the partition plate 25 and into the first cylinder chamber 55A. Compared to a compressor 1 without the through portion 63, the amount of refrigerant inhaled increases due to the refrigerant passing through the through portion 63, thus increasing the refrigeration capacity and compression efficiency.

[0151] Furthermore, in a compressor, if high-pressure refrigerant flows back from outside the first discharge channel toward the low-pressure first cylinder chamber after the compressed refrigerant has been discharged, a wider circumferential intake channel will shorten the time the piston blocks the intake channel. In this case, the compressor may be more susceptible to the backflowing high-pressure refrigerant entering the intake channel, potentially reducing the amount of low-pressure refrigerant drawn in from the intake pipe to the compression mechanism, and thus lowering the compression efficiency.

[0152] The penetration portion 63 of the compressor 1 widens the suction passage 52A in the axial direction, rather than widening the opening in the circumferential direction. Compared to the case where the opening of the suction passage 52A is widened in the circumferential direction, the compressor 1 can ensure sufficient time for the piston 22 to block the suction passage 52A, thereby suppressing backflow of refrigerant into the suction passage 52A and preventing a decrease in compression efficiency.

[0153] Furthermore, the bottom portion 60A of the constricted section, which is the second closing wall portion 151, has a second penetration portion 63B at its radially inward end that penetrates the second cylinder 21B in the axial direction. In the second cylinder 21B, the refrigerant that reaches the second penetration portion 63B flows more easily to both sides in the axial direction of the second cylinder 21B, and this refrigerant flows into the second cylinder chamber 55B via the upper surface of the lower bearing 24B and the lower surface of the partition plate 25. Compared to the case where the compressor 1 does not have the second penetration portion 63B, the amount of refrigerant in the intake increases due to the refrigerant passing through the second penetration portion 63B, thus increasing the refrigeration capacity and compression efficiency.

[0154] Furthermore, the second penetration section 63B of the compressor 1 widens the suction passage 52A in the axial direction rather than widening the opening in the circumferential direction. Compared to the case where the opening of the suction passage 52A is widened in the circumferential direction, the compressor 1 can ensure sufficient occlusion time of the suction passage 52A by the piston 22, thereby suppressing backflow of refrigerant into the suction passage 52A and preventing a decrease in compression efficiency.

[0155] The refrigeration cycle device 200 according to Embodiment 1 is equipped with the compressor 1 according to Embodiment 1. Therefore, the refrigeration cycle device 200 can obtain the same effects as the compressor 1 according to Embodiment 1.

[0156] Embodiment 2. Figure 17 is a schematic longitudinal cross-sectional view showing the overall configuration of the compressor 1 according to Embodiment 2. Figure 18 is a schematic partial longitudinal cross-sectional view of the compression mechanism 20 according to Embodiment 2. Figure 19 is a partially enlarged view of the internal suction passage 52B of the compressor 1 according to Embodiment 2. Figure 20 is a partially enlarged view of the suction passage 52A of the compressor 1 according to Embodiment 2.

[0157] The compression mechanism 20 of Embodiment 2 will be described using Figures 17 to 20. Parts having the same configuration as the compression mechanism 20 in Figures 1 to 16 are denoted by the same reference numerals, and their descriptions are omitted. The following description will focus on the differences between Embodiment 2 and Embodiment 1, while configurations not described in Embodiment 2 are the same as in Embodiment 1. The compressor 1 is assumed to have the first cylinder 21A fixed to the sealed container 10, and the second cylinder 21B not fixed to the sealed container 10.

[0158] In the compressor 1 according to Embodiment 1, the suction pipe 2 was connected to the first cylinder 21A, whereas in the compressor 1 according to Embodiment 2, the suction pipe 2 is connected to the second cylinder 21B. Therefore, the structure of the first cylinder 21A and the structure of the second cylinder 21B in the compressor 1 according to Embodiment 2 are the opposite of those in the compressor 1 according to Embodiment 1. In addition, the second cylinder 21B of the compressor 1 according to Embodiment 2 has a branch passage 52AA that branches off from the suction passage 52A.

[0159] The first cylinder 21A has an internal intake passage 52B formed therein that leads from the lower surface of the first cylinder 21A to the first cylinder chamber 55A. The internal intake passage 52B has a communicating intake hole 62 that extends radially inward from the lower surface of the first cylinder 21A through the interior of the first cylinder 21A. The internal intake passage 52B also has a second throttling portion 60 formed radially inward of the communicating intake hole 62, which forms a space that connects the communicating intake hole 62 and the first cylinder chamber 55A. In other words, the internal intake passage 52B comprises a communicating intake hole 62 and a second throttling portion 60 formed radially inward of the communicating intake hole 62, which connects the communicating intake hole 62 and the first cylinder chamber 55A.

[0160] The communication suction hole 62 is a hole that extends radially inward from the lower surface of the first cylinder 21A through the inside of the first cylinder 21A. The communication suction hole 62 extends axially downward from the lower surface of the first cylinder 21A, and then extends radially inward from there. The communication suction hole 62 is a hole that connects the outside of the first cylinder 21A to the second throttling section 60. The communication suction hole 62 is a hole that connects the connection path 25A of the partition plate 25 (see Figure 4) to the second throttling section 60.

[0161] The top portion 160A of the constricted section contributes to improving the rigidity of the first cylinder 21A regardless of which axial end face the first cylinder 21A is provided on. However, from the viewpoint of machinability and rigidity improvement, it is preferable to provide it on the side opposite to the side where the communication intake hole 62 is formed.

[0162] The second constricted portion 60 has a pair of second constricted portion side portions 60B that form both inner surfaces of the second constricted portion 60 and are formed to approach each other as they extend radially inward from the first cylinder 21A. The second constricted portion 60 is also composed of the pair of second constricted portion side portions 60B and has a second axial side opening 60D that opens at one end in the axial direction of the rotating shaft 40 and is closed by the partition plate 25. The second constricted portion 60 is also composed of the pair of second constricted portion side portions 60B and has a second inner opening 60C that opens radially inward from the first cylinder 21A to communicate with the first cylinder chamber 55A and is formed to connect with the second axial side opening 60D. The second constricted portion 60 also has a plate-shaped second closing wall portion 151 provided at the other end in the axial direction of the rotating shaft 40 to close the second constricted portion 60.

[0163] In the axial direction of the rotating shaft 40, one end of the second constricted portion 60 is open by the second shaft side opening 60D, and the other end is closed by the constricted portion top 160A. In the radial direction of the rotating shaft 40, one end of the second constricted portion 60 is in communication with the communication intake hole 62, and the other end is in communication with the first cylinder chamber 55A.

[0164] The second cylinder 21B has an intake passage 52A that connects the outside of the second cylinder 21B to the second cylinder chamber 55B. The intake passage 52A extends radially inward from the outer circumferential surface of the second cylinder 21B and has an intake hole 61 to which the intake pipe 2 is connected on the outer circumferential surface, and a constricted portion 59 formed radially inward from the intake hole 61, which forms a space that connects the intake hole 61 and the second cylinder chamber 55B.

[0165] The intake passage 52A comprises an intake hole 61 extending radially inward from the outer circumferential surface 156 of the second cylinder 21B, and a throttling portion 59 formed radially inward of the intake hole 61, which connects the intake hole 61 with the second low-pressure chamber 57B. In other words, the intake passage 52A comprises an intake hole 61 and a throttling portion 59 formed radially inward of the intake hole 61, which connects the intake hole 61 with the second cylinder chamber 55B.

[0166] The intake hole 61 is a hole that extends radially inward from the outer circumferential surface 156 of the second cylinder 21B. The intake hole 61 is a hole that connects the outside of the second cylinder 21B with the throttling portion 59. The tip of the intake pipe 2 is inserted into the intake hole 61. The intake hole 61 is a hole that connects the intake pipe 2 with the throttling portion 59. The opening shape of the intake hole 61, which is the inlet of the intake passage 52A, should match the shape of the intake pipe 2.

[0167] The constricted portion 59 has a pair of constricted side portions 59B that form both inner surfaces of the constricted portion 59 and are formed to approach each other as they are directed radially inward of the second cylinder 21B. The constricted portion 59 is also composed of the pair of constricted side portions 59B and has an axial-side opening 59D that opens at one end in the axial direction of the rotating shaft 40. The constricted portion 59 is also composed of the pair of constricted side portions 59B and has an inner opening 59C that opens radially inward of the second cylinder 21B to communicate with the second cylinder chamber 55B and is formed to connect with the axial-side opening 59D. The constricted portion 59 also has a plate-shaped closing wall portion 150 provided at the other end in the axial direction of the rotating shaft 40 to close the constricted portion 59 in the axial direction of the rotating shaft 40.

[0168] The constricted portion 59 is open at one end by the shaft-side opening 59D in the axial direction of the rotating shaft 40, and closed at the other end by the constricted portion bottom 159A. The constricted portion bottom 159A contributes to improving the rigidity of the second cylinder 21B regardless of which axial end face the second cylinder 21B is provided on, but from the viewpoint of machinability and rigidity improvement, it is preferable to provide it on the side opposite to the side where the branched passage 52AA is formed.

[0169] The throttling section 59 has one end communicating with the intake hole 61 and the other end communicating with the second cylinder chamber 55B in the radial direction of the rotating shaft 40. In the compressor 1 of the second embodiment, the bottom portion 159A of the throttling section constitutes the closing wall portion 150 of the throttling section 59.

[0170] In the compressor 1, the suction pipe 2 is press-fitted into the suction passage 52A on the outer surface of the second cylinder 21B. The branch passage 52AA connects the suction passage 52A of the second cylinder 21B to the connection path 25A of the partition plate 25.

[0171] The partition plate 25 has a connecting path 25A that communicates with a branched passage 52AA that branches off from the suction passage 52A of the second cylinder 21B. The connecting path 25A also communicates with the internal suction passage 52B formed in the first cylinder 21A. The connecting path 25A connects the branched passage 52AA of the second cylinder 21B with the internal suction passage 52B of the first cylinder 21A. The connecting path 25A connects the internal suction passage 52B of the first cylinder 21A with the suction passage 52A of the second cylinder 21B.

[0172] Figure 21 is a partially enlarged view of the internal suction passage 52B of a modified example of the compressor 1 according to Embodiment 2. Figure 22 is a partially enlarged view of the suction passage 52A of a modified example of the compressor 1 according to Embodiment 2. As shown in Figure 21, the top portion 160A of the throttling section may have a second through-port 63B at its radially inward end that penetrates the first cylinder 21A in the axial direction. Also, as shown in Figure 22, the bottom portion 159A of the throttling section may have a through-port 63 at its radially inward end that penetrates the second cylinder 21B in the axial direction.

[0173] The constricted top portion 160A, which is the second closing wall portion 151, has a second through portion 63B at its radially inward end that penetrates the first cylinder 21A in the axial direction. In Embodiment 2, the second through portion 63B is an opening formed on the upper bearing 24A side of the first cylinder 21A. In the compression mechanism 20, the second through portion 63B is covered and closed by the plate surface of the upper bearing 24A.

[0174] The constricted bottom portion 159A, which is the closing wall portion 150, has a through portion 63 at its radially inward end that penetrates the second cylinder 21B in the axial direction. In Embodiment 2, the through portion 63 is an opening formed on the lower bearing 24B side of the second cylinder 21B. In the compression mechanism 20, the through portion 63 is covered and closed by the plate surface of the lower bearing 24B.

[0175] The refrigerant flowing in from the suction pipe 2 connected to the second cylinder 21B flows into the second high-pressure chamber 58B through the suction passage 52A, is compressed inside the second high-pressure chamber 58B by the rotation of the second piston 22B, and is discharged as high-pressure refrigerant from the second discharge passage 53B.

[0176] Similarly, the refrigerant flowing in from the suction pipe 2 connected to the second cylinder 21B flows into the first high-pressure chamber 58A through the connection path 25A of the partition plate 25 and the internal suction passage 52B of the first cylinder 21A. The refrigerant flowing into the first high-pressure chamber 58A is compressed by the rotation of the first piston 22A inside the first high-pressure chamber 58A and discharged as high-pressure refrigerant from the first discharge passage 53A.

[0177] Thus, since the refrigerant moves within the suction passage 52A of the compressor 1, a larger diameter of the suction pipe 2 of the compressor 1 reduces the flow pressure loss, therefore a larger diameter of the suction pipe 2 is desirable. Also, since the refrigerant moves within the suction passage 52A of the compressor 1, a larger diameter of the flow path within the suction passage 52A reduces the flow pressure loss, therefore a larger diameter of the flow path within the suction passage 52A is desirable. In other words, since the refrigerant moves within the suction passage 52A of the compressor 1, a larger cross-sectional area of ​​the flow path within the suction passage 52A reduces the flow pressure loss, therefore a larger cross-sectional area of ​​the flow path within the suction passage 52A is desirable.

[0178] Furthermore, in the second high-pressure chamber 58B, the refrigerant is repeatedly drawn in, compressed, and exhausted. When the compressor 1 exhausts the refrigerant, there is a risk that the high-pressure refrigerant inside the sealed container 10 will flow back into the second high-pressure chamber 58B, which has finished compression and is now at a low pressure, from the second discharge passage 53B. In this case, the compressor 1 may experience a decrease in compressor efficiency due to the amount of refrigerant drawn in from the suction pipe 2 decreasing as the refrigerant that has flowed back into the second high-pressure chamber 58B enters the suction passage 52A. Therefore, in order to suppress the backflow of refrigerant into the second high-pressure chamber 58B when the compressor 1 is exhausted, it is desirable that the inner opening 59C, which is the connection between the suction passage 52A and the second cylinder chamber 55B, be close to the second vane groove 56B.

[0179] From the above, it is desirable for the compressor 1 to expand the intake passage 52A in the axial direction of the second cylinder 21B in order to improve the compressor efficiency. Furthermore, in order to improve the compressor efficiency, it is effective for the compressor 1 to have a throttling section 59 at the inner circumference end of the intake passage 52A and to connect the intake passage 52A to the second cylinder chamber 55B at a position close to the second vane 50B.

[0180] On the other hand, if the intake hole 61 is enlarged or if the intake hole 61 is brought closer to the second vane groove 56B, the thickness of the wall between the intake hole 61 of the second cylinder 21B and the second vane groove 56B of the compressor 1 will decrease. In such cases, the compressor 1 may increase the risk of distortion of the second cylinder 21B due to external forces such as the press-fitting of the intake pipe 2 into the second cylinder 21B. Furthermore, the compressor 1 may increase the risk of distortion of the second cylinder 21B due to external forces such as the pressing force of the second vane 50B against the second cylinder 21B caused by the differential pressure between the second low-pressure chamber 57B and the second high-pressure chamber 58B.

[0181] Therefore, the intake passage 52A is formed such that it penetrates only one side of the second cylinder 21B in the axial direction at the throttling portion 59, while the other side is walled by the throttling portion bottom 159A. The compressor 1 ensures the rigidity of the second cylinder 21B with the throttling portion bottom 159A, and the throttling portion 59 expands the intake passage 52A in the axial direction, bringing the inner opening 59C, which is the connection point with the second cylinder chamber 55B, closer to the second vane groove 56B.

[0182] Similar to the intake passage 52A, the internal intake passage 52B is formed in the second throttling section 60 such that it penetrates only one axial side of the first cylinder 21A, while the other side is walled by the throttling section top 160A. The compressor 1 ensures the rigidity of the first cylinder 21A with the throttling section top 160A, and the second throttling section 60 expands the internal intake passage 52B in the axial direction, bringing the second inner opening 60C, which is the connection point with the first cylinder chamber 55A, closer to the first vane groove 56A.

[0183] [Effects of Compressor 1] The compressor 1 has a throttling section 59 in the refrigerant intake passage 52A formed in the second cylinder 21B. The throttling section 59 has a pair of throttling section side portions 59B that form both inner surfaces of the throttling section 59 and are formed to move closer to each other as they extend radially inward from the second cylinder 21B. The throttling section 59 is also composed of the pair of throttling section side portions 59B and has an axial-side opening 59D that opens at one end in the axial direction of the rotating shaft 40. The throttling section 59 is also composed of the pair of throttling section side portions 59B and has an inner opening 59C that opens radially inward from the second cylinder 21B to communicate with the second cylinder chamber 55B and is formed to connect with the axial-side opening 59D. The throttling section 59 also has a throttling section bottom portion 159A, which is a plate-shaped closing wall portion 150 provided at the other end in the axial direction of the rotating shaft 40 to close the throttling section 59. The constricted portion 59 expands the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 through the shaft-side opening 59D and the inner opening 59C, while ensuring the rigidity of the second cylinder 21B with the closing wall portion 150, thereby increasing the strength of the second cylinder 21B.

[0184] The compressor 1 ensures the rigidity of the second cylinder 21B by the closed wall portion 150 of the throttling portion 59, thereby increasing the strength of the second cylinder 21B. As a result, the compressor 1 can suppress deformation of the second cylinder 21B due to external forces such as the pressing force of the second vane 50B against the second cylinder 21B caused by the differential pressure between the second low-pressure chamber 57B and the second high-pressure chamber 58B, thereby increasing the strength of the second cylinder 21B.

[0185] The compressor 1 ensures the rigidity of the second cylinder 21B by the closed wall portion 150 of the throttling portion 59, thereby increasing the strength of the second cylinder 21B. Therefore, even when the suction pipe 2 is inserted into the suction passage 52A of the second cylinder 21B while shaking, the compressor 1 can suppress deformation of the second cylinder 21B.

[0186] If the throttling section 59 has closing wall sections 150 at both ends in the axial direction of the rotating shaft 40, the opening area and volume of the throttling section 59 will decrease, resulting in increased pressure loss in the compressor 1 and making it difficult for the refrigerant to enter the first cylinder chamber 55A. The compressor 1 has an axial-side opening 59D at one end of the throttling section 59 and a closing wall section 150 at the other end in the axial direction of the rotating shaft 40. Therefore, the compressor 1 can increase the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 by using the axial-side opening 59D, while ensuring the rigidity of the second cylinder 21B with the closing wall section 150, thereby increasing the strength of the second cylinder 21B.

[0187] Furthermore, the second cylinder 21B has an intake passage 52A and a branch passage 52AA that branches off from the intake passage 52A. The first cylinder 21A has an internal intake passage 52B that leads from the bottom surface of the first cylinder 21A to the first cylinder chamber 55A, and the partition plate 25 has a connecting path 25A that connects the branch passage 52AA and the internal intake passage 52B. Even if a two-cylinder rotary compressor is used for the compressor 1, the compressor 1 can increase the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40, while ensuring the rigidity of the second cylinder 21B with the closed wall portion 150, thereby increasing the strength of the second cylinder 21B.

[0188] Furthermore, the compressor 1 has a second throttling section 60 in the internal refrigerant suction passage 52B formed in the first cylinder 21A. The second throttling section 60 has a pair of second throttling section side portions 60B that constitute both inner surfaces of the second throttling section 60 and are formed to move closer to each other as they are directed radially inward of the first cylinder 21A. The second throttling section 60 is also composed of the pair of second throttling section side portions 60B and has a second axial opening 60D that opens at one end in the axial direction of the rotating shaft 40 and is closed by a partition plate 25. The second throttling section 60 is also composed of the pair of second throttling section side portions 60B and has a second inner opening 60C that opens radially inward of the first cylinder 21A to communicate with the first cylinder chamber 55A and is formed to connect with the second axial opening 60D. Furthermore, the second constricted portion 60 has a constricted portion top portion 160A, which is a plate-shaped second closing wall portion 151 provided at the other end in the axial direction of the rotating shaft 40 to close the second constricted portion 60.

[0189] The second constriction section 60 expands the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 by the second shaft-side opening 60D and the second inner opening 60C, while ensuring the rigidity of the first cylinder 21A by the second closing wall section 151, thereby increasing the strength of the first cylinder 21A.

[0190] The compressor 1 ensures the rigidity of the first cylinder 21A by the second closing wall portion 151 of the second throttling portion 60, thereby increasing the strength of the first cylinder 21A. As a result, the compressor 1 can suppress deformation of the first cylinder 21A due to external forces such as the pressing force of the first vane 50A against the first cylinder 21A caused by the differential pressure between the first low-pressure chamber 57A and the first high-pressure chamber 58A, thereby increasing the strength of the first cylinder 21A.

[0191] Furthermore, the suction pipe 2 is press-fitted into the suction passage 52A of the second cylinder 21B. Even when the suction pipe 2 is press-fitted into the suction passage 52A of the second cylinder 21B, the compressor 1 has a throttling section 59 with a throttling section bottom 60A which is a closing wall 150, so deformation of the second cylinder 21B can be suppressed.

[0192] Furthermore, the bottom portion 159A of the constricted section, which is the closed wall portion 150, has a through portion 63 at its radially inward end that penetrates the second cylinder 21B in the axial direction. In the second cylinder 21B, the refrigerant that reaches the through portion 63 flows more easily to both sides in the axial direction of the second cylinder 21B, and this refrigerant flows into the second cylinder chamber 55B via the upper surface of the lower bearing 24B and the lower surface of the partition plate 25. Compared to a compressor 1 without the through portion 63, the amount of refrigerant inhaled increases due to the refrigerant passing through the through portion 63, thus increasing the refrigeration capacity and compression efficiency.

[0193] Furthermore, in a compressor, if high-pressure refrigerant enters the second cylinder chamber from outside the second discharge channel after the compressed refrigerant has been discharged and the second cylinder chamber is now at low pressure, a wider circumferential intake channel will shorten the time the piston blocks the intake channel. In this case, the compressor becomes more susceptible to high-pressure refrigerant flowing back into the intake channel, which can reduce the amount of low-pressure refrigerant drawn in from the intake pipe to the compression mechanism, potentially lowering the compression efficiency.

[0194] The penetration portion 63 of the compressor 1 widens the suction passage 52A in the axial direction, rather than widening the opening in the circumferential direction. Compared to the case where the opening of the suction passage 52A is widened in the circumferential direction, the compressor 1 can ensure sufficient time for the piston 22 to block the suction passage 52A, thereby suppressing backflow of refrigerant into the suction passage 52A and preventing a decrease in compression efficiency.

[0195] Furthermore, the top portion 160A of the constricted section, which is the second closing wall portion 151, has a second penetration portion 63B at its radially inward end that penetrates the first cylinder 21A in the axial direction. In the first cylinder 21A, the refrigerant that reaches the second penetration portion 63B is more likely to flow to both sides in the axial direction of the first cylinder 21A, and this refrigerant flows into the first cylinder chamber 55A via the lower surface of the upper bearing 24A and the upper surface of the partition plate 25. Compared to a compressor 1 without the second penetration portion 63B, the amount of refrigerant inhaled increases due to the refrigerant passing through the second penetration portion 63B, thus increasing the refrigeration capacity and compression efficiency.

[0196] Furthermore, the second penetration section 63B of the compressor 1 widens the suction passage 52A in the axial direction rather than widening the opening in the circumferential direction. Compared to the case where the opening of the suction passage 52A is widened in the circumferential direction, the compressor 1 can ensure sufficient occlusion time of the suction passage 52A by the piston 22, thereby suppressing backflow of refrigerant into the suction passage 52A and preventing a decrease in compression efficiency.

[0197] Furthermore, in the compressor 1, the first cylinder 21A is fixed to the sealed container 10. For example, as described above, in the compressor 1, the first cylinder 21A is fixed to the sealed container 10, but the second cylinder 21B is not fixed to the sealed container 10. When fixing the first cylinder 21A to the sealed container 10, for example, by welding, distortion may occur in the first cylinder 21A.

[0198] Compressor 1 connects the suction pipe 2 to the second cylinder 21B, which is not connected to the sealed container 10. Compressor 1 may cause distortion in the second cylinder 21B by connecting the suction pipe 2 to the sealed container 10.

[0199] The compressor 1 connects the suction pipe 2 to the second cylinder 21B and fixes the first cylinder 21A to the sealed container 10. By having this configuration, the compressor 1 reduces the amount of strain on the first cylinder 21A and increases the amount of strain on the second cylinder 21B compared to the case where the first cylinder 21A is fixed to the sealed container 10 and the suction pipe 2 is connected to the first cylinder 21A.

[0200] Compared to the case where the first cylinder 21A is fixed to the sealed container 10 and the suction pipe 2 is joined to the first cylinder 21A, the compressor 1 can eliminate the imbalance in distortion between the first cylinder 21A and the second cylinder 21B, which occurred because the distortion due to assembly was biased towards the first cylinder 21A. Therefore, the compressor 1 can unify the target values ​​of the machining dimensions of the first cylinder 21A and the second cylinder 21B, taking into account the distortion due to assembly.

[0201] At the same time, by switching the insertion of the suction pipe 2 into the cylinder 21 from the first cylinder 21A to the second cylinder 21B, the assembly man-hours for the first cylinder 21A can be reduced. Note that the first cylinder 21A may be distorted by welding or other means when it is fixed to the sealed container 10. By reducing the assembly man-hours that were concentrated on the first cylinder 21A, the compressor 1 can reduce the variation in distortion of the assembly of the first cylinder 21A, and reduce the clearance for fitting the first vane groove 56A and the first vane 50A. As a result, the compressor 1 can reduce the amount of compressed refrigerant leakage from the first high-pressure chamber 58A and improve compressor efficiency.

[0202] The refrigeration cycle device 200 according to Embodiment 2 is equipped with the compressor 1 according to Embodiment 2. Therefore, the refrigeration cycle device 200 can obtain the same effects as the compressor 1 according to Embodiment 2.

[0203] Embodiment 3. Figure 23 is a schematic longitudinal cross-sectional view showing the overall configuration of the compressor 1 according to Embodiment 3. Figure 24 is a schematic partial longitudinal cross-sectional view of the compression mechanism 20 according to Embodiment 3. Figure 25 is a perspective view of the first cylinder 21A of the compressor 1 according to Embodiment 3. Figure 26 is a partially enlarged view of the suction passage 52A of the compressor 1 according to Embodiment 3.

[0204] The compression mechanism 20 of Embodiment 3 will be described using Figures 23 to 26. Note that parts having the same configuration as the compression mechanism 20 in Figures 1 to 22 are denoted by the same reference numerals, and their descriptions are omitted. Hereafter, the description will focus on the configurations of Embodiment 3 that differ from Embodiments 1 and 2, while configurations not described in Embodiment 3 are the same as those in Embodiments 1 or 2.

[0205] The compressor 1 in Embodiments 1 and 2 is a two-cylinder rotary compressor, whereas the compressor 1 in Embodiment 3 is a one-cylinder rotary compressor. The compressor 1 in Embodiment 3 has a first cylinder 21A in the compression mechanism 20.

[0206] The compression mechanism 20 comprises a first cylinder 21A, a first piston 22A, a first vane 50A, a first spring 51A, an upper bearing 24A, and a lower bearing 24B.

[0207] The upper bearing 24A is positioned to abut against the upper end surface of the first cylinder 21A and closes the first cylinder chamber 55A. The lower bearing 24B is positioned to abut against the lower end surface of the first cylinder 21A and closes the first cylinder chamber 55A.

[0208] The first cylinder 21A has an intake passage 52A that connects the outside of the first cylinder 21A to the first cylinder chamber 55A. The intake passage 52A extends radially inward from the outer circumferential surface of the first cylinder 21A and has an intake hole 61 to which the intake pipe 2 is connected on the outer circumferential surface, and a constricted portion 59 formed radially inward from the intake hole 61 that forms a space connecting the intake hole 61 and the first cylinder chamber 55A.

[0209] The compressor 1 has an intake passage 52A that leads from the outer circumferential surface 156 of the first cylinder 21A to the first cylinder chamber 55A. The intake passage 52A comprises an intake hole 61 extending radially inward from the outer circumferential surface 156 of the first cylinder 21A, and a throttling portion 59 formed radially inward of the intake hole 61 that connects the intake hole 61 to the first low-pressure chamber 57A. In other words, the intake passage 52A comprises an intake hole 61 and a throttling portion 59 formed radially inward of the intake hole 61 that connects the intake hole 61 to the first cylinder chamber 55A.

[0210] The constricted portion 59 has a pair of constricted side portions 59B that form both inner surfaces of the constricted portion 59 and are formed to approach each other as they are directed radially inward of the first cylinder 21A. The constricted portion 59 is also composed of the pair of constricted side portions 59B and has an axial-side opening 59D that opens at one end of the rotating shaft 40 in the axial direction. The constricted portion 59 is also composed of the pair of constricted side portions 59B and has an inner opening 59C that opens radially inward of the first cylinder 21A to communicate with the first cylinder chamber 55A and is formed to connect with the axial-side opening 59D. The constricted portion 59 also has a plate-shaped closing wall portion 150 provided at the other end of the rotating shaft 40 in the axial direction to close the constricted portion 59 in the axial direction of the rotating shaft 40.

[0211] The throttling portion 59 has an opening on the outer surface of the first cylinder 21A on the lower and radially inward sides, a throttling top portion 59A on the upper side, and throttling side portions 59B on both inner sides that move closer to each other as they move radially inward. That is, the throttling portion 59 has an opening on the lower bearing 24B side of the first cylinder 21A and the inner circumferential wall 155 of the first cylinder chamber 55A, with the throttling top portion 59A on the upper bearing 24A side. The throttling portion 59 has throttling side portions 59B that face each other in the circumferential direction. The throttling side portions 59B are formed so that they move closer to each other as they move radially outward to inward. In the compressor 1 of Embodiment 3, the throttling top portion 59A constitutes the closing wall portion 150 of the throttling portion 59.

[0212] The shaft-side opening 59D is an opening formed on the outer surface of the first cylinder 21A on the side of the lower bearing 24B. In the compression mechanism 20, the shaft-side opening 59D is covered and closed by the plate surface of the lower bearing 24B.

[0213] In the axial direction of the rotating shaft 40, one end of the constricted portion 59 is open by the shaft-side opening 59D, and the other end is closed by the top of the constricted portion 59A. In the radial direction of the rotating shaft 40, one end of the constricted portion 59 communicates with the intake hole 61, and the other end communicates with the first cylinder chamber 55A.

[0214] In the third embodiment of the compressor 1, the upper bearing 24A closes the upper end surface of the first cylinder 21A, and the lower bearing 24B closes the lower end surface of the first cylinder 21A. In the third embodiment of the compressor 1, the shaft-side opening 59D is closed by the lower bearing 24B, and the top portion 59A of the constricted section, which is the closing wall portion 150, is provided to be in contact with the upper bearing 24A.

[0215] Figure 27 is a perspective view of the first cylinder 21A of a modified example of the compressor 1 according to Embodiment 3. Figure 28 is a partially enlarged view of the suction passage 52A of the modified example of the compressor 1 according to Embodiment 3. The top of the constricted portion 59A may have a through portion 63 that penetrates the first cylinder 21A in the axial direction, as shown in Figures 27 and 28, at its radially inward end.

[0216] [Effects of Compressor 1] The compressor 1 has a throttling section 59 in the refrigerant intake passage 52A formed in the first cylinder 21A. The throttling section 59 has a pair of throttling section side portions 59B that form both inner surfaces of the throttling section 59 and are formed to move closer to each other as they extend radially inward from the first cylinder 21A. The throttling section 59 is also composed of the pair of throttling section side portions 59B and has an axial-side opening 59D that opens at one end in the axial direction of the rotating shaft 40. The throttling section 59 is also composed of the pair of throttling section side portions 59B and has an inner opening 59C that opens radially inward from the first cylinder 21A to communicate with the first cylinder chamber 55A and is formed to connect with the axial-side opening 59D. The throttling section 59 also has a throttling section top portion 59A, which is a plate-shaped closing wall portion 150 provided at the other end in the axial direction of the rotating shaft 40 to close the throttling section 59. The constricted portion 59 expands the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 through the shaft-side opening 59D and the inner opening 59C, while ensuring the rigidity of the first cylinder 21A with the closing wall portion 150, thereby increasing the strength of the first cylinder 21A.

[0217] The compressor 1 ensures the rigidity of the first cylinder 21A by the closed wall portion 150 of the throttling portion 59, thereby increasing the strength of the first cylinder 21A. As a result, the compressor 1 can suppress deformation of the first cylinder 21A due to external forces such as the pressing force of the first vane 50A against the first cylinder 21A caused by the differential pressure between the first low-pressure chamber 57A and the first high-pressure chamber 58A, thereby increasing the strength of the first cylinder 21A.

[0218] The compressor 1 ensures the rigidity of the first cylinder 21A by the closed wall portion 150 of the throttling portion 59, thereby increasing the strength of the first cylinder 21A. Therefore, even when the suction pipe 2 is inserted into the suction passage 52A of the first cylinder 21A while shaking, the compressor 1 can suppress deformation of the first cylinder 21A.

[0219] In the constricted section 59, if closing wall sections 150 are provided at both ends in the axial direction of the rotating shaft 40, the opening area and volume of the constricted section 59 will decrease, resulting in increased pressure loss in the compressor 1 and making it difficult for the refrigerant to enter the first cylinder chamber 55A. The compressor 1 has an axial-side opening 59D at one end of the constricted section 59 and a closing wall section 150 at the other end in the axial direction of the rotating shaft 40. Therefore, the compressor 1 can increase the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 by using the axial-side opening 59D, while ensuring the rigidity of the first cylinder 21A with the closing wall section 150, thereby increasing the strength of the first cylinder 21A.

[0220] Furthermore, in the compressor 1, the upper bearing 24A closes the upper end surface of the first cylinder 21A, and the lower bearing 24B closes the lower end surface of the first cylinder 21A. In addition, the shaft-side opening 59D of the compressor 1 is closed by the lower bearing 24B, and the closing wall portion 150 is provided so as to abut against the upper bearing 24A. The compressor 1 can increase the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 by the shaft-side opening 59D, while ensuring the rigidity of the first cylinder 21A by the closing wall portion 150, thereby increasing the strength of the first cylinder 21A.

[0221] Furthermore, the suction pipe 2 is press-fitted into the suction passage 52A of the first cylinder 21A. Even when the suction pipe 2 is press-fitted into the suction passage 52A of the first cylinder 21A, the compressor 1 has a throttling section 59 top section 59A which is a closing wall section 150, so deformation of the first cylinder 21A can be suppressed.

[0222] Furthermore, the top portion 59A of the constricted section, which is the closing wall portion 150, has a through portion 63 at its radially inward end that penetrates the first cylinder 21A in the axial direction. In the first cylinder 21A, the refrigerant that reaches the through portion 63 flows more easily to both sides in the axial direction of the first cylinder 21A, and this refrigerant flows from the lower surface of the upper bearing 24A to the upper surface of the partition plate 25 and into the first cylinder chamber 55A. Compared to a compressor 1 without the through portion 63, the amount of refrigerant inhaled increases due to the refrigerant passing through the through portion 63, thus increasing the refrigeration capacity and compression efficiency.

[0223] Furthermore, in a compressor, if high-pressure refrigerant enters the first cylinder chamber from outside the first discharge channel after the compressed refrigerant has been discharged and the first cylinder chamber is now at low pressure, a wider circumferential intake channel will shorten the time the piston blocks the intake channel. In this case, the compressor becomes more susceptible to high-pressure refrigerant flowing back into the intake channel, which can reduce the amount of low-pressure refrigerant drawn in from the intake pipe to the compression mechanism, potentially lowering the compression efficiency.

[0224] The penetration portion 63 of the compressor 1 widens the suction passage 52A in the axial direction, rather than widening the opening in the circumferential direction. Compared to the case where the opening of the suction passage 52A is widened in the circumferential direction, the compressor 1 can ensure sufficient time for the piston 22 to block the suction passage 52A, thereby suppressing backflow of refrigerant into the suction passage 52A and preventing a decrease in compression efficiency.

[0225] The refrigeration cycle device 200 according to Embodiment 3 is equipped with the compressor 1 according to Embodiment 3. Therefore, the refrigeration cycle device 200 can obtain the same effects as the compressor 1 according to Embodiment 3.

[0226] Embodiment 4. Figure 29 is a schematic longitudinal cross-sectional view showing the overall configuration of the compressor 1 according to Embodiment 4. Figure 30 is a schematic partial longitudinal cross-sectional view of the compression mechanism 20 according to Embodiment 4. The compression mechanism 20 of Embodiment 4 will be described using Figures 29 to 30. Note that parts having the same configuration as the compression mechanism 20 in Figures 1 to 28 are denoted by the same reference numerals and their descriptions are omitted. Hereafter, the description will focus on the configurations in Embodiment 4 that differ from those in Embodiment 3, and configurations not described in Embodiment 4 are the same as those in Embodiments 1 to 3.

[0227] The compressor 1 of Embodiment 4 differs from the compressor 1 of Embodiment 3 in the structure of the throttling section 59. The throttling section 59 in the compressor 1 of Embodiment 3 has a top throttling section 59A, whereas the throttling section 59 in the compressor 1 of Embodiment 4 has a bottom throttling section 59A1.

[0228] In Embodiment 4, the throttling portion 59 has an opening on the outer surface of the first cylinder 21A on the upper and radially inward sides, a throttling bottom portion 59A1 on the lower side, and throttling side portions 59B on both inner surfaces that move closer to each other as they extend radially inward. That is, the throttling portion 59 has an opening on the upper bearing 24A side of the first cylinder 21A and the inner circumferential wall 155 of the first cylinder chamber 55A, with the throttling bottom portion 59A1 on the lower bearing 24B side. In the compressor 1 of Embodiment 3, the throttling bottom portion 59A1 constitutes the closing wall portion 150 of the throttling portion 59.

[0229] The shaft-side opening 59D is an opening formed on the outer surface of the first cylinder 21A on the side of the upper bearing 24A. In the compression mechanism 20, the shaft-side opening 59D is covered and closed by the plate surface of the upper bearing 24A.

[0230] In the compressor 1 of Embodiment 4, the upper bearing 24A closes the upper end surface of the first cylinder 21A, and the lower bearing 24B closes the lower end surface of the first cylinder 21A. In the compressor 1 of Embodiment 4, the shaft-side opening 59D is closed by the upper bearing 24A, and the bottom portion 59A1 of the constricted section, which is the closing wall portion 150, is provided to be in contact with the lower bearing 24B.

[0231] The constricted portion 59 is open at one end by an axial-side opening 59D in the axial direction of the rotating shaft 40, and closed at the other end by a constricted portion bottom 59A1. In the radial direction of the rotating shaft 40, one end of the constricted portion 59 communicates with the intake hole 61, and the other end communicates with the first cylinder chamber 55A. The radially inward end of the constricted portion bottom 59A1 may form a through portion 63 that penetrates the first cylinder 21A in the axial direction.

[0232] [Effects of Compressor 1] The compressor 1 has a throttling section 59 in the refrigerant intake passage 52A formed in the first cylinder 21A. The throttling section 59 has a pair of throttling section side portions 59B that form both inner surfaces of the throttling section 59 and are formed to move closer to each other as they extend radially inward from the first cylinder 21A. The throttling section 59 is also composed of the pair of throttling section side portions 59B and has an axial-side opening 59D that opens at one end in the axial direction of the rotating shaft 40. The throttling section 59 is also composed of the pair of throttling section side portions 59B and has an inner opening 59C that opens radially inward from the first cylinder 21A to communicate with the first cylinder chamber 55A and is formed to connect with the axial-side opening 59D. The throttling section 59 also has a throttling section bottom portion 59A1, which is a plate-shaped closing wall portion 150, provided at the other end in the axial direction of the rotating shaft 40 to close the throttling section 59. The constricted portion 59 expands the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 through the shaft-side opening 59D and the inner opening 59C, while ensuring the rigidity of the first cylinder 21A with the closing wall portion 150, thereby increasing the strength of the first cylinder 21A.

[0233] The compressor 1 ensures the rigidity of the first cylinder 21A by the closed wall portion 150 of the throttling portion 59, thereby increasing the strength of the first cylinder 21A. As a result, the compressor 1 can suppress deformation of the first cylinder 21A due to external forces such as the pressing force of the first vane 50A against the first cylinder 21A caused by the differential pressure between the first low-pressure chamber 57A and the first high-pressure chamber 58A, thereby increasing the strength of the first cylinder 21A.

[0234] The compressor 1 ensures the rigidity of the first cylinder 21A by the closed wall portion 150 of the throttling portion 59, thereby increasing the strength of the first cylinder 21A. Therefore, even when the suction pipe 2 is inserted into the suction passage 52A of the first cylinder 21A while shaking, the compressor 1 can suppress deformation of the first cylinder 21A.

[0235] In the constricted section 59, if closing wall sections 150 are provided at both ends in the axial direction of the rotating shaft 40, the opening area and volume of the constricted section 59 will decrease, resulting in increased pressure loss in the compressor 1 and making it difficult for the refrigerant to enter the first cylinder chamber 55A. The compressor 1 has an axial-side opening 59D at one end of the constricted section 59 and a closing wall section 150 at the other end in the axial direction of the rotating shaft 40. Therefore, the compressor 1 can increase the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 by using the axial-side opening 59D, while ensuring the rigidity of the first cylinder 21A with the closing wall section 150, thereby increasing the strength of the first cylinder 21A.

[0236] Furthermore, in the compressor 1, the upper bearing 24A closes the upper end surface of the first cylinder 21A, and the lower bearing 24B closes the lower end surface of the first cylinder 21A. In addition, in the compressor 1, the shaft-side opening 59D is closed by the upper bearing 24A, and the closing wall portion 150 is provided to abut against the lower bearing 24B. The compressor 1 can increase the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 by the shaft-side opening 59D, while ensuring the rigidity of the first cylinder 21A by the closing wall portion 150, thereby increasing the strength of the first cylinder 21A.

[0237] The refrigeration cycle device 200 according to Embodiment 4 is equipped with the compressor 1 according to Embodiment 4. Therefore, the refrigeration cycle device 200 can obtain the same effects as the compressor 1 according to Embodiment 4.

[0238] The configurations shown in the above embodiments are examples, and can be combined with other known technologies, and parts of the configuration can be omitted or modified without departing from the gist of the invention. For example, in the embodiments, the first cylinder 21A is fixed to the sealed container 10 and the second cylinder 21B is not fixed to the sealed container 10, but the first cylinder 21A may not be fixed to the sealed container 10 and the second cylinder 21B may be fixed to the sealed container 10. Also, in the embodiments, the number of cylinders 21 is one or two, but there may be three or more. [Explanation of Symbols]

[0239] 1 Compressor, 2 Intake pipe, 3 Intake muffler, 4 Discharge piping, 6 Refrigerant oil, 10 Sealed container, 11 Head, 12 Body, 13 Bottom, 20 Compression mechanism, 21 Cylinder, 21A First cylinder, 21B Second cylinder, 22 Piston, 22A First piston, 22B Second piston, 23A First muffler, 23B Second muffler, 24A Upper bearing, 24B Lower bearing, 25 Partition plate, 25A Connection path, 30 Rotating electric machine, 31 Rotor, 32 Stator, 40 Rotating shaft, 40A First eccentric shaft section, 40B Second eccentric shaft section, 41 End section, 42 Oil supply hole, 43 First oil supply port, 44 Second oil supply port, 45 Centrifugal pump, 50 Vane, 50A First vane, 50B 51A Second vane, 51B First spring, 52A Second spring, 52AA Intake passage, 52AA Branch passage, 52B Internal intake passage, 53A First discharge passage, 53B Second discharge passage, 54A First spring hole, 54B Second spring hole, 55 Cylinder chamber, 55A First cylinder chamber, 55B Second cylinder chamber, 56 Vane groove, 56A First vane groove, 56B Second vane groove, 57A First low-pressure chamber, 57B Second low-pressure chamber, 58A First high-pressure chamber, 58B Second high-pressure chamber, 59 Constriction section, 59A Top of constriction section, 59A1 Bottom of constriction section, 59B Side of constriction section, 59B1 Side of constriction section, 59B2 Side of constriction section, 59C Inner opening, 59D Shaft-side opening, 60 Second constriction section, 60A Bottom of constriction section, 60B Side section of the second constriction, 60B1 Side section of the second constriction, 60B2 Side section of the second constriction, 60C Second inner opening, 60D Second shaft side opening, 61 Intake hole, 62 Communicating intake hole, 63 Through section, 63B Second through section, 122 Outer peripheral wall, 150 Closure wall section, 151 Second closure wall section, 155 Inner peripheral wall, 155A Intermediate wall section, 155B Intermediate wall section, 156 Outer peripheral surface, 159A Bottom of the constriction, 160A Top of the constriction, 200 Refrigeration cycle device, 201 Flow path switching device, 202 Outdoor heat exchanger, 203 Pressure reducer, 204 Indoor heat exchanger, 210 Refrigerant circuit.

Claims

1. A sealed container, A rotating electric machine placed inside the sealed container, A rotating shaft is placed inside the sealed container and is driven to rotate by the rotating electric machine, A compression mechanism is disposed within the sealed container and compresses the refrigerant by a driving force transmitted from the rotating electric machine via the rotating shaft, The suction pipe, which penetrates the sealed container and is connected to the compression mechanism, serves as a flow path for the refrigerant, Equipped with, The compression mechanism is A cylindrical shape comprising at least one cylinder forming a cylinder chamber inside, A piston is fitted onto the rotating shaft and housed in the cylinder chamber, and rotates eccentrically as the rotating shaft rotates to compress the refrigerant, The vanes are arranged in vane grooves formed to extend radially in the cylinder, and together with the piston, the cylinder chamber is divided into two spaces. An upper bearing and a lower bearing are arranged on the end face of the cylinder and close the cylinder chamber, It has, The cylinder includes, An intake passage is formed that connects the outside of the cylinder to the cylinder chamber. The aforementioned intake passage is The cylinder extends radially inward from its outer circumferential surface, and the outer circumferential surface has an intake hole to which the intake pipe is connected, A constricted portion is formed radially inward of the intake hole, forming a space that connects the intake hole and the cylinder chamber, It has, The aforementioned constricted portion is A pair of side surfaces of the constricted portion, which constitute both inner surfaces of the constricted portion and are formed to move closer to each other as they extend radially inward from the cylinder, The pair of constricted side portions comprises an axial opening that opens at one end in the axial direction of the rotating shaft, The pair of constricted side portions comprises an inner opening that opens radially inward on the cylinder side to communicate with the cylinder chamber and is formed to connect with the shaft side opening, A plate-shaped closing wall portion is provided at the other end of the rotating shaft in the axial direction, so as to close the constricted portion, A compressor having a compressor.

2. The at least one cylinder is A cylindrical first cylinder fixed to the sealed container and forming a first cylinder chamber that constitutes a part of the cylinder chamber, A cylindrical second cylinder is positioned below the first cylinder and forms a second cylinder chamber that constitutes a part of the cylinder chamber, Includes, The aforementioned upper bearing is It is positioned on the upper end surface of the first cylinder and closes the first cylinder chamber, The aforementioned lower bearing is It is positioned on the lower end surface of the second cylinder and closes the second cylinder chamber, The compression mechanism is A partition plate is provided between the first cylinder and the second cylinder, which closes the shaft-side opening, the first cylinder chamber and the second cylinder chamber. The first cylinder has, The aforementioned intake passage, A branch channel that branches off from the aforementioned intake channel, A structure has been formed, The second cylinder has, An internal intake passage is formed from the upper surface of the second cylinder to the second cylinder chamber. The aforementioned partition plate includes: The compressor according to claim 1, wherein a connecting path is formed to connect the branched passage and the internal suction passage.

3. The aforementioned internal intake passage is A communication suction hole extending radially inward from the upper surface of the second cylinder through the interior of the second cylinder, A second throttling portion is formed radially inward of the aforementioned communication intake hole, and forms a space that connects the communication intake hole and the second cylinder chamber, Equipped with, The second constricted portion is, A pair of second constriction side surfaces, which constitute both inner surfaces of the second constriction and are formed to move closer to each other as they extend radially inward from the second cylinder, The pair of second constricted side portions constitute a second shaft-side opening that opens at one end in the axial direction of the rotating shaft and is closed by the partition plate, The pair of second constriction side portions comprises a second inner opening that is formed to communicate with the second cylinder chamber on the radially inward side of the second cylinder and to connect with the second shaft side opening, At the other end of the rotating shaft in the axial direction, a plate-shaped second closing wall portion is provided to close the second constricted portion, The compressor according to claim 2, having the following features.

4. The at least one cylinder is A cylindrical first cylinder fixed to the sealed container and forming the first cylinder chamber which is the cylinder chamber, A cylindrical second cylinder is positioned below the first cylinder and forms the second cylinder chamber, which is the cylinder chamber. Includes, The aforementioned upper bearing is It is positioned on the upper end surface of the first cylinder and closes the first cylinder chamber, The aforementioned lower bearing is It is positioned on the lower end surface of the second cylinder and closes the second cylinder chamber, The compression mechanism is A partition plate is provided between the first cylinder and the second cylinder, which closes the shaft-side opening, the first cylinder chamber and the second cylinder chamber. The second cylinder has, The aforementioned intake passage, A branch channel that branches off from the aforementioned intake channel, A structure has been formed, The first cylinder has, An internal intake passage is formed from the lower surface of the first cylinder to the first cylinder chamber. The aforementioned partition plate includes: The compressor according to claim 1, wherein a connecting path is formed to connect the branched passage and the internal suction passage.

5. The aforementioned internal intake passage is A communication suction hole extending radially inward from the lower surface of the first cylinder through the interior of the first cylinder, A second throttling portion is formed radially inward of the aforementioned communication intake hole, and forms a space that connects the communication intake hole and the first cylinder chamber, Equipped with, The second constricted portion is, A pair of second constriction side surfaces are formed to constitute both inner surfaces of the second constriction, and are arranged to move closer to each other as they extend radially inward from the first cylinder, The pair of second constricted side portions constitute a second shaft-side opening that opens at one end in the axial direction of the rotating shaft and is closed by the partition plate, The pair of second constricted side portions comprises a second inner opening that opens radially inward of the first cylinder so as to communicate with the first cylinder chamber and is formed to connect with the second shaft side opening, At the other end of the rotating shaft in the axial direction, a plate-shaped second closing wall portion is provided to close the second constricted portion, The compressor according to claim 4, having the following features.

6. The aforementioned upper bearing The upper end surface of the cylinder is closed, The aforementioned lower bearing is The lower end surface of the cylinder is closed, The aforementioned shaft-side opening is It is blocked by the lower bearing, The aforementioned closing wall portion is The compressor according to claim 1, which is provided so as to be in contact with the upper bearing.

7. The aforementioned upper bearing The upper end surface of the cylinder is closed, The aforementioned lower bearing is The lower end surface of the cylinder is closed, The aforementioned shaft-side opening is It is blocked by the upper bearing, The aforementioned closing wall portion is The compressor according to claim 1, which is provided so as to be in contact with the lower bearing.

8. The compressor according to any one of claims 1 to 7, wherein the suction pipe is pressurized into the suction passage.

9. The compressor according to any one of claims 1 to 7, wherein the end of the closing wall portion on the radially inward side has a through portion that penetrates in the axial direction of the cylinder.

10. The compressor according to claim 3 or 5, wherein the end of the second closing wall portion on the radially inward side has a second penetrating portion that penetrates the cylinder in the axial direction.

11. A compressor according to any one of claims 1 to 7, An outdoor heat exchanger that performs heat exchange between the outdoor air and the refrigerant flowing inside, A pressure reducer for reducing the pressure of the refrigerant flowing inside, An indoor heat exchanger that performs heat exchange between indoor air and the refrigerant flowing inside, A refrigeration cycle device equipped with a refrigeration cycle system.

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