Compressor and refrigeration cycle apparatus

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

Compressor and refrigeration cycle device

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

[0002] Conventionally, a rotary compressor has been known that includes a motor element and a compression element driven by the motor element, which are hermetically sealed (see, for example, Patent Document 1). The compression element of this compressor includes a cylinder, upper and lower end plates disposed at both end surfaces of the cylinder, a piston disposed within the cylinder, and a vane that divides a space defined by the cylinder, the upper and lower end plates, and the piston into a high-pressure chamber and a low-pressure chamber. The cylinder also includes a suction hole extending radially inward from the outer circumferential surface of the cylinder and a notch formed radially inward of the suction hole to reduce resistance during refrigerant intake. The notch penetrates both end surfaces of the cylinder to increase the opening area of ​​a passage through which refrigerant flows from the suction hole to the low-pressure chamber, and also connects the suction hole to the low-pressure chamber.

[0003] Japanese Patent Application Publication No. 1-244191

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

[0005] The present disclosure is devised to solve the above-mentioned problems, and aims to provide a compressor and a refrigeration cycle device that can increase the strength of the cylinder.

[0006] A compressor according to the present disclosure includes a sealed container, a rotating electric machine arranged in the sealed container, a rotating shaft arranged in the sealed container and driven to rotate by the rotating electric machine, a compression mechanism arranged in the sealed container and compressing a refrigerant by a driving force transmitted from the rotating electric machine via the rotating shaft, and a suction pipe that penetrates the sealed container and is connected to the compression mechanism and serves as a flow path for the refrigerant, the compression mechanism including at least one cylinder formed in a cylindrical shape and forming an internal cylinder chamber, a piston that is fitted to the rotating shaft and housed in the cylinder chamber and rotates eccentrically as the rotating shaft rotates to compress the refrigerant, a vane that is arranged in a vane groove formed to extend radially of the cylinder and that, together with the piston, separates the cylinder chamber into two spaces, and upper and lower bearings that are arranged on end surfaces of the cylinder and close the cylinder chamber, an intake passage is formed that connects the outside of the cylinder with the cylinder chamber, the intake passage extends radially inward from the outer peripheral surface of the cylinder, and has an intake hole to which an intake pipe is connected on the outer peripheral surface, and a throttle portion formed radially inward of the intake hole and defining a space that connects the intake hole with the cylinder chamber, the throttle portion having a pair of throttle portion side portions that form both inner surfaces of the throttle portion and are formed so as to approach each other as they extend radially inward of the cylinder, a shaft-side opening formed by the pair of throttle portion side portions and opening at one end in the axial direction of the rotating shaft, an inner opening formed by the pair of throttle portion side portions and opening on the radially inward side of the cylinder so as to communicate with the cylinder chamber and formed so as to be continuous with the shaft-side opening, and a plate-shaped closing wall portion provided at the other end in the axial direction of the rotating shaft so as to close the throttle portion.

[0007] The refrigeration cycle device according to the present disclosure includes a compressor having the above-described configuration, an outdoor heat exchanger that exchanges heat between outdoor air and the refrigerant flowing inside, a pressure reducer that reduces the pressure of the refrigerant flowing inside, and an indoor heat exchanger that exchanges heat between indoor air and the refrigerant flowing inside.

[0008] The compressor and refrigeration cycle apparatus according to the present disclosure have a throttling portion in a refrigerant intake passage formed in a cylinder. The throttling portion has a pair of throttling portion side surfaces that form both inner surfaces of the throttling portion and are formed so as to approach each other as they extend radially inward of the cylinder. The throttling portion is formed by the pair of throttling portion side surfaces and has a shaft-side opening that opens at one end in the axial direction of the rotating shaft. The throttling portion is also formed by the pair of throttling portion side surfaces and has an inner opening that opens radially inward of the cylinder so as to communicate with the cylinder chamber and is formed so as to communicate with the shaft-side opening. The throttling portion has a plate-shaped blocking wall that is provided at the other end in the axial direction of the rotating shaft so as to block the throttling portion. The throttling portion has the shaft-side opening and the inner opening to expand the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft, while the blocking wall ensures the rigidity of the cylinder, thereby increasing the strength of the cylinder.

[0009] 1 is a schematic longitudinal sectional view showing the overall configuration of a compressor according to a first embodiment; FIG. 2 is a schematic transverse sectional view of a first cylinder portion of a compression mechanism according to the first embodiment; FIG. 3 is a schematic transverse sectional view of a second cylinder portion of a compression mechanism according to the first embodiment; FIG. 4 is a schematic partial longitudinal sectional view of a compression mechanism according to the first embodiment; FIG. 5 is a perspective view of a first cylinder of a compressor according to the first embodiment; FIG. 6 is a partial enlarged view of an intake passage of a compressor according to the first embodiment; FIG. 7 is a conceptual view of an intake passage of a compressor according to the first embodiment; FIG. 8 is a side view of the first cylinder of a compressor according to the first embodiment, viewed from the inner circumferential surface side; FIG. 9 is a perspective view of a first cylinder of a modified example of a compressor according to the first embodiment; FIG. 10 is a partial enlarged view of an intake passage of a modified example of a compressor according to the first embodiment; FIG. 11 is a perspective view of a second cylinder of a compressor according to the first embodiment; FIG. 12 is a conceptual view of an internal intake passage of a compressor according to the first embodiment; FIG. 13 is a schematic configuration diagram of a refrigeration cycle device including a compressor according to the first embodiment; FIG. 14 is a schematic longitudinal sectional view showing the overall configuration of a compressor according to a second embodiment; FIG. 15 is a schematic partial longitudinal sectional view of a compression mechanism according to the second embodiment. 1 is a partial enlarged view of an internal intake passage of a compressor according to embodiment 2. FIG. 2 is a partial enlarged view of an intake passage of a compressor according to embodiment 2. FIG. 3 is a partial enlarged view of an internal intake passage of a modified example of the compressor according to embodiment 2. FIG. 4 is a partial enlarged view of an intake passage of a modified example of the compressor according to embodiment 2. FIG. 5 is a schematic longitudinal sectional view showing the overall configuration of a compressor according to embodiment 3. FIG. 6 is a schematic partial longitudinal sectional view of a compression mechanism according to embodiment 3. FIG. 7 is a perspective view of a first cylinder of the compressor according to embodiment 3. FIG. 8 is a partial enlarged view of an intake passage of a compressor according to embodiment 3. FIG. 9 is a perspective view of a first cylinder of the modified example of the compressor according to embodiment 3. FIG. 10 is a partial enlarged view of an intake passage of a modified example of the compressor according to embodiment 3. FIG. 11 is a schematic longitudinal sectional view showing the overall configuration of a compressor according to embodiment 4. FIG. 12 is a schematic partial longitudinal sectional view of a compression mechanism according to embodiment 4.

[0010] A compressor and a refrigeration cycle device according to an embodiment will be described below with reference to the drawings. Note that in the following drawings, including FIG. 1, the relative dimensional relationships and shapes of the components may differ from those in reality. In the following drawings, the same reference numerals denote the same or equivalent components, and this applies throughout the entire specification. To facilitate understanding, terms indicating directions (e.g., "up," "down," "right," "left," "front," "rear," etc.) are used as appropriate, but these notations are merely used for the convenience of explanation and do not limit the arrangement or orientation of the device or components.

[0011] Embodiment 1. [Configuration of Compressor 1] Fig. 1 is a schematic vertical cross-sectional view showing the overall configuration of a compressor 1 according to Embodiment 1. The compressor 1, which is a hermetic compressor, will be described using Fig. 1. As shown in Fig. 1, the compressor 1 according to Embodiment 1 is a rolling piston compressor as an example of a compressor according to the present disclosure. The compressor 1 draws in a low-temperature, low-pressure refrigerant, compresses the drawn refrigerant, and discharges a high-temperature, high-pressure refrigerant.

[0012] The compressor 1 is a two-cylinder rotary compressor, and is a fluid machine that discharges low-pressure gas refrigerant drawn into the compressor 1 as high-pressure gas refrigerant. Note that the two-cylinder rotary compressor is an example, and rotary compressors of other structures, such as a one-cylinder rotary compressor, may also be used.

[0013] The compressor 1 includes a sealed container 10, a compression mechanism 20, a rotating electric machine 30 disposed within the sealed container 10, and a rotating shaft 40 disposed within the sealed container 10 and driven to rotate by the rotating electric machine 30. The compressor 1 also includes a suction pipe 2, a discharge pipe 4, a suction muffler 3, and a centrifugal pump 45. The compressor 1 accommodates, inside the sealed container 10, the compression mechanism 20 that compresses the refrigerant, the rotating electric machine 30 that drives the compression mechanism 20, and the rotating shaft 40 that connects the compression mechanism 20 and the rotating electric machine 30. The compressor 1 has the compression mechanism 20 housed in a lower portion within the sealed container 10, and the rotating electric machine 30 housed in an upper portion within the sealed container 10.

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

[0015] The sealed container 10 includes a substantially cylindrical body 12, a substantially hemispherical or bottomed cylindrical head 11, and a substantially hemispherical or bottomed cylindrical bottom 13. The body 12 forms the outer shell of the middle part of the compressor 1, with the head 11 attached to its upper part and the bottom 13 attached to its lower part. The head 11 forms the outer shell of the upper part of the compressor 1. The bottom 13 forms the outer shell of the lower part of the compressor 1. For example, the sealed container 10 is constructed such that the head 11 is welded to the upper part of the body 12, and the bottom 13 is welded to the lower part of the body 12.

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

[0017] A stator 32 of the rotating electrical machine 30 is attached to the inner circumferential surface of the body portion 12. A compression mechanism 20 is attached to the inner circumferential surface of the body portion 12. The compressor 1 of the first embodiment 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 configured such that the compression mechanism 20 is attached to the inner circumferential surface of the body portion 12, below the position where the stator 32 is attached.

[0018] The head portion 11 constituting the upper portion of the sealed container 10 is formed, for example, in a substantially bowl shape, as shown in Fig. 1. A discharge pipe 4 that 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 of the discharge pipe 4 and the head portion 11 is joined by, for example, brazing or resistance welding.

[0019] The bottom 13 constituting the lower part of the sealed container 10 is formed, for example, in a substantially bowl shape, as shown in FIG. 1 . Refrigerating machine oil 6, which is a lubricating oil, is stored in the bottom 13 of the sealed container 10. That is, the refrigerating machine oil 6 is stored inside the sealed container 10. The compressor 1 is provided with a centrifugal pump 45 (described later) that pumps up the refrigerating machine oil 6 at the bottom of the rotating shaft 40. The centrifugal pump 45 pumps up the refrigerating machine oil 6 stored in the bottom 13 of the sealed container 10 as the rotating shaft 40 rotates, and supplies it to each sliding part of the compression mechanism 20. In the compressor 1, the refrigerating machine oil 6 is supplied to the compression mechanism 20, etc., reducing friction at the sliding parts of the compression mechanism 20, etc. This ensures mechanical lubrication of the compression mechanism 20 in the compressor 1.

[0020] (Compression mechanism 20) Fig. 2 is a schematic cross-sectional view of the first cylinder 21A portion of the compression mechanism 20 according to the first embodiment. Fig. 3 is a schematic cross-sectional view of the second cylinder 21B portion of the compression mechanism 20 according to the first embodiment. Fig. 4 is a schematic partial vertical cross-sectional view of the compression mechanism 20 according to the first embodiment. Note that Figs. 2 and 3 are cross-sectional views of the compression mechanism 20 as viewed from the side where the rotating electric machine 30 is disposed. The compression mechanism 20 will be described using Figs. 1 to 4. The compression mechanism 20 is connected to the suction pipe 2 and compresses the refrigerant.

[0021] The compression mechanism 20 is disposed within the sealed container 10 and compresses the refrigerant using 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 using 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 the first embodiment, the refrigerant that flows into the suction muffler 3 is supplied to the compression mechanism 20 via the suction pipe 2. That is, the compression mechanism 20 draws in the external refrigerant via the suction pipe 2 and compresses the refrigerant. The refrigerant compressed by the compression mechanism 20 is released into the sealed container 10. As described above, the compressor 1 of the first embodiment employs a rolling piston type compression mechanism as the compression mechanism 20.

[0023] Compression mechanism 20 includes at least one cylinder 21 formed in a cylindrical shape and defining a cylinder chamber 55 therein, and a piston 22 fitted to rotary shaft 40 and housed in cylinder chamber 55, rotating eccentrically with rotation of rotary shaft 40 to compress the refrigerant. Compression mechanism 20 also includes a vane 50 disposed in a vane groove 56 formed to extend radially of cylinder 21 and separating cylinder chamber 55 into two spaces together with piston 22. Compression mechanism 20 also includes an upper bearing 24A and a lower bearing 24B disposed on an end face of cylinder 21 and closing cylinder chamber 55.

[0024] The compression mechanism 20 includes 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 and defines a first cylinder chamber 55A. The first cylinder 21A has the first cylinder chamber 55A therein, which compresses the refrigerant. The first cylinder 21A is a cylindrical member formed in a cylindrical shape with both ends in the axial direction of the rotating shaft 40 open. The first cylinder 21A is hollow and has a through-hole formed in its center that is concentric with the axis of the rotating shaft 40. The through-hole of the first cylinder 21A is closed by an upper bearing 24A arranged in contact with the upper end surface of the first cylinder 21A and a partition plate 25 arranged in contact with the lower end surface of the first cylinder 21A, thereby forming the first cylinder chamber 55A. The first cylinder 21A is fixed to the sealed container 10.

[0026] The first cylinder chamber 55A accommodates a first eccentric shaft portion 40A of a rotating shaft 40 (described later) that performs eccentric motion inside the first cylinder chamber 55A, and a first piston 22A that fits onto the first eccentric shaft portion 40A of the rotating shaft 40. The first cylinder chamber 55A also accommodates a first vane 50A that partitions the first cylinder chamber 55A and is formed between an inner peripheral wall 155 of the first cylinder chamber 55A and an outer peripheral wall 122 of the first piston 22A.

[0027] 2 and 4, the first cylinder 21A is formed with a suction passage 52A through which the refrigerant is drawn from the suction pipe 2, and a first discharge passage 53A through which the refrigerant is discharged to the discharge pipe 4 via the internal space of the sealed container 10. In addition, the first cylinder 21A is formed with a branch passage 52AA branching from the suction passage 52A, as shown in FIG.

[0028] In the compressor 1, the suction pipe 2 is press-fitted into the suction passage 52A on the outer peripheral surface of the first cylinder 21A. The branch passage 52AA connects the suction passage 52A of the first cylinder 21A to a connection passage 25A of the partition plate 25, which will be described later. That is, the branch passage 52AA connects to the connection passage 25A of the partition plate 25. The detailed configurations 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 in the axial and radial directions of the first cylinder 21A. One end of the first vane groove 56A in the radial direction of the first cylinder 21A opens into 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, passes through the first cylinder 21A in the axial direction, and communicates with the first vane groove 56A. The first vane 50A is housed in the first vane groove 56A, and the first spring 51A is housed in the first spring hole 54A.

[0031] The first piston 22A is fitted to the first eccentric shaft portion 40A of the rotating shaft 40 and rotates eccentrically together 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 attached to the outer periphery 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. The first piston 22A is configured to rotate inside the first cylinder 21A eccentrically with respect to the center of rotation of the rotary shaft 40. Hereinafter, the rotational motion eccentrically with respect to the center of rotation of the rotary 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 rotary 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 phase shift of 180 degrees relative to the rotational phase when the second piston 22B rotates inside the second cylinder 21B.

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

[0035] The first vane 50A is disposed between the intake passage 52A and the first discharge passage 53A in the circumferential direction of the first cylinder 21A. The first vane 50A is disposed in a first vane groove 56A formed to extend radially of 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 peripheral wall 122 of the first piston 22A.

[0037] The upper bearing 24A is disposed so as 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 rotary shaft 40. The upper bearing 24A is provided with a valve (not shown) that releases the refrigerant compressed by the first cylinder 21A and the first piston 22A. When this valve opens, the compressor 1 can communicate the space defined 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 that discharges the refrigerant compressed by the first cylinder 21A and the first piston 22A. The first muffler 23A is provided with a refrigerant discharge portion (not shown) that functions as a valve. As a result, in the compressor 1, the refrigerant compressed by the first cylinder 21A and the first piston 22A is discharged into the internal space of the first muffler 23A, and then released into the inside of the sealed container 10 from the refrigerant discharge portion.

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

[0040] The second cylinder 21B has a second cylinder chamber 55B therein that compresses the refrigerant, and is a cylindrical member formed in a cylindrical shape with both ends in the axial direction of the rotating shaft 40 open. The second cylinder 21B is formed in a hollow cylindrical shape with a through-hole formed in the center that is concentric with the axis of the rotating shaft 40. The through-hole of the second cylinder 21B is closed by a lower bearing 24B arranged in contact with the lower end surface of the second cylinder 21B and a partition plate 25 arranged in contact with the upper end surface 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 cylinder chamber 55.

[0041] The second cylinder chamber 55B accommodates a second eccentric shaft portion 40B of the rotating shaft 40 (described later), which performs eccentric motion inside the second cylinder chamber 55B, and a second piston 22B fitted to the second eccentric shaft portion 40B of the rotating shaft 40. The second cylinder chamber 55B also accommodates a second vane 50B that partitions the second cylinder chamber 55B and is formed between an inner peripheral wall 155 of the second cylinder chamber 55B and an outer peripheral wall 122 of the second piston 22B.

[0042] 3 and 4 , the second cylinder 21B is formed with an internal suction passage 52B through which refrigerant is drawn from the upper 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 connected to the connection passage 25A of the partition plate 25. In the compression mechanism 20, the branch passage 52AA of the first cylinder 21A, the connection passage 25A of the partition plate 25, and the internal suction passage 52B of the second cylinder 21B are connected to each other, and refrigerant is drawn from the suction pipe 2 into 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 in the axial and radial directions of the second cylinder 21B. One end of the second vane groove 56B in the radial direction of the second cylinder 21B opens to 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, passes through the second cylinder 21B in the axial direction, and communicates 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 to the second eccentric shaft portion 40B of the rotating shaft 40 and rotates eccentrically together 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 attached to the outer periphery 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. The 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 rotary 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 phase shift of -180 degrees relative to the rotational phase when the first piston 22A rotates inside the first cylinder 21A.

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

[0049] The second vane 50B is disposed between the internal intake passage 52B and the second discharge passage 53B in the circumferential direction of the second cylinder 21B. The second vane 50B is disposed in a second vane groove 56B formed to extend radially of 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 intake 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 attached to the tip of the second spring 51B against the outer peripheral wall 122 of the second piston 22B.

[0051] The lower bearing 24B is disposed so as 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 rotary shaft 40. The lower bearing 24B is provided with a valve (not shown) that releases the refrigerant compressed by the second cylinder 21B and the second piston 22B. When this valve opens, the compressor 1 can communicate the space formed by the second cylinder 21B and the second piston 22B with the internal space of the second muffler 23B (described later).

[0052] The lower bearing 24B is provided with a second muffler 23B that discharges refrigerant compressed by the second cylinder 21B and the second piston 22B. The internal space of the 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 inside of the sealed container 10 from a refrigerant discharge port (not shown) of the first muffler 23A.

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

[0054] A connection path 25A is formed in the partition plate 25. The connection path 25A communicates with a branch path 52AA branching from the suction path 52A of the first cylinder 21A. The connection path 25A also communicates with an internal suction path 52B formed in the second cylinder 21B. The connection path 25A is a through-hole formed in the partition plate 25. The connection path 25A connects the branch path 52AA of the first cylinder 21A with the internal suction path 52B of the second cylinder 21B. The connection path 25A connects the suction path 52A of the first cylinder 21A with the internal suction path 52B of the second cylinder 21B.

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

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

[0057] In the rotating electric machine 30, power is supplied from an external power source to the stator 32, causing the rotor 31 to rotate inside the stator 32. In the rotating electric machine 30, current is supplied from a power source (not shown) to windings provided on a laminated core of the stator 32, causing a rotating magnetic field to be formed in the stator 32. As a result, in the rotating electric machine 30, for example, the rotating magnetic field of the stator 32 acts on a permanent magnet provided in 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] (Rotating shaft 40) The rotating shaft 40 transmits the power of the rotating electric machine 30 to the compression mechanism 20. The rotating shaft 40 is connected to the rotating electric machine 30 and rotates by 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 the first embodiment, the upper end side 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 rotor 31. The rotating shaft 40 shown in FIG. 1 rotates around an axis extending in the vertical direction of the page. The lower end side of the rotating shaft 40 is connected to the compression mechanism 20. More specifically, the lower end side of the rotating shaft 40 is rotatably supported by an upper bearing 24A and a lower bearing 24B of the compression mechanism 20.

[0060] 1, in the compressor 1 of the first embodiment, the rotating shaft 40 has a first eccentric shaft portion 40A and a second eccentric shaft portion 40B between a portion rotatably supported by the upper bearing 24A and a portion 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 portion of the rotating shaft 40.

[0061] The rotating shaft 40 has the first piston 22A connected to the first eccentric shaft portion 40A so as to be capable of eccentric rotation, and the second piston 22B connected to the second eccentric shaft portion 40B so as to be capable of eccentric rotation. That is, the rotating shaft 40 has the first piston 22A and the second piston 22B connected to it so as to be capable of eccentric rotation between a portion rotatably supported by the upper bearing 24A and a portion rotatably supported by the lower bearing 24B.

[0062] As a result, in the compressor 1, the rotating shaft 40 also rotates in conjunction with the rotation of the rotor 31, and the first piston 22A and the second piston 22B perform eccentric rotational motion. In the compressor 1, the refrigerant is compressed by the first cylinder 21A and the first piston 22A, and the refrigerant is compressed 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] An oil supply hole 42 is formed in the rotating shaft 40 at an end 41, which is one end 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 a first end. In the compressor 1 of the first embodiment, the end 41 is the lower end of the rotating shaft 40. The oil supply hole 42 extends along the center of rotation of the rotating shaft 40.

[0064] The rotating shaft 40 is also formed with a first oil fill port 43 and a second oil fill port 44. The first oil fill port 43 and the second oil fill port 44 serve as flow paths for supplying the refrigeration oil 6 sucked into the oil fill hole 42 to the sliding parts of the compression mechanism 20. One end of each of the first oil fill port 43 and the second oil fill port 44 communicates with the oil fill hole 42. The other end of each of the first oil fill port 43 and the second oil fill port 44 opens at a location on the outer circumferential surface of the rotating shaft 40 that faces the compression mechanism 20. In the compressor 1 of the first embodiment, the other end of the first oil fill port 43 opens at a location that faces the upper bearing 24A of the compression mechanism 20. The other end of the second oil fill port 44 opens at a location that faces the lower bearing 24B of the compression mechanism 20.

[0065] (Suction Pipe 2) The suction pipe 2 passes through the sealed container 10 and is connected to the compression mechanism 20, forming 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 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 suction muffler 3. The suction pipe 2 may be a circular pipe having a circular cross section, or may be a non-circular pipe having an elliptical or oval cross section.

[0066] (Discharge Pipe 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] (Suction muffler 3) The suction muffler 3 functions as a muffler that reduces refrigerant noise and the like generated when the refrigerant flows into the compressor 1. The suction muffler 3 also functions as an accumulator that can store liquid refrigerant. The suction muffler 3 is connected to the suction pipe 2 and communicates with the suction pipe 2.

[0068] (Centrifugal Pump 45) The centrifugal pump 45 is provided inside the oil supply hole 42 of the rotating shaft 40. The centrifugal pump 45 is formed, for example, by twisting a plate-like member. The centrifugal pump 45 is a fluid machine that uses centrifugal force generated by the rotational motion of the rotating shaft 40 to suck up the refrigeration oil 6 as lubricating oil stored in the bottom 13 of the sealed container 10.

[0069] Refrigerant oil 6 pumped up into oil feed hole 42 by centrifugal pump 45 is supplied to sliding parts of compression mechanism 20. Specifically, a portion of refrigerant oil 6 pumped up into oil feed hole 42 passes through first oil feed port 43 and is supplied to sliding parts between upper bearing 24A and rotating shaft 40 of compression mechanism 20. Furthermore, a portion of refrigerant oil 6 pumped up into oil feed hole 42 passes through second oil feed port 44 and is supplied to sliding parts between lower bearing 24B and rotating shaft 40 of compression mechanism 20. As refrigerant oil 6, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, polyol ester-based lubricating oil, or the like is used.

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

[0071] A portion of the gaseous refrigerant that has flowed 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 through a valve in the upper bearing 24A. The high-temperature, high-pressure gaseous refrigerant that has flowed into the internal space of the first muffler 23A is discharged into the internal space of the sealed container 10 from a refrigerant discharge port (not shown) provided in the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant that has been discharged into the internal space of the sealed container 10 then moves to the upper part of the space within the sealed container 10 through gaps, etc., in the rotating electrical 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 via a valve in the lower bearing 24B. The high-temperature, high-pressure gaseous refrigerant that has flowed into the internal space of the second muffler 23B passes through a refrigerant flow path (not shown) from the internal space of the second muffler 23B and is sent into the internal space of the first muffler 23A.

[0073] The high-temperature, high-pressure gaseous refrigerant sent into the first muffler 23A is discharged from a refrigerant discharge portion (not shown) provided in the first muffler 23A into the internal space of the sealed container 10. Then, the high-temperature, high-pressure gaseous refrigerant discharged into the internal space of the sealed container 10 moves to the upper part of the space within the sealed container 10 through gaps, etc., of the rotating electrical machine 30, etc., and is discharged from the discharge pipe 4.

[0074] Furthermore, refrigeration oil 6 stored in bottom 13 within sealed container 10 is sucked up from the lower end of oil supply hole 42 by centrifugal pump 45, which rotates together with rotating shaft 40. Refrigeration oil 6 sucked up from the lower end of oil supply hole 42 flows as lubricating oil between upper bearing 24A and rotating shaft 40 from first oil supply port 43. Refrigeration oil 6 also flows from second oil supply port 44 between lower bearing 24B and rotating shaft 40. By refrigeration oil 6 flowing between these, rotating shaft 40 can smoothly transmit rotational driving force to first piston 22A and second piston 22B.

[0075] Furthermore, a portion of the refrigeration oil 6 that flows from the first oil supply port 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. A portion of the refrigeration oil 6 that flows from the second oil supply port 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 refrigeration oil 6 is used to smoothly rotate the first piston 22A and the second piston 22B, but a portion of the refrigeration oil 6 is compressed together with the low-pressure gaseous refrigerant and is discharged in a state contained in the high-temperature, high-pressure gaseous refrigerant.

[0076] [Detailed Configuration of Intake Flow Passage 52A of First Cylinder 21A] Fig. 5 is a perspective view of the first cylinder 21A of the compressor 1 according to the first embodiment. Fig. 6 is a partial enlarged view of the intake flow passage 52A of the compressor 1 according to the first embodiment. Fig. 7 is a conceptual diagram of the intake flow passage 52A of the compressor 1 according to the first embodiment. Note that Fig. 5 is a perspective view of the first cylinder 21A as seen from the partition plate 25 side. Also, Fig. 7 is a conceptual diagram of the intake flow passage 52A as seen from the side where the rotating electrical machine 30 is disposed. Next, the configuration of the intake flow passage 52A of the first cylinder 21A will be described in detail with reference to Figs. 5 to 7.

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

[0078] The first cylinder 21A is formed with an intake passage 52A that connects the outside of the first cylinder 21A with 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 peripheral surface of the first cylinder 21A and has an intake hole 61 on the outer peripheral surface to which the intake pipe 2 is connected, and a throttle portion 59 that forms a space that connects the intake hole 61 with the first cylinder chamber 55A.

[0079] 6 and 7, intake passage 52A includes an intake hole 61 extending radially inward from outer peripheral surface 156 of first cylinder 21A, and a throttle portion 59 formed radially inward of intake hole 61 to connect intake hole 61 to first low-pressure chamber 57A. That is, intake passage 52A includes intake hole 61 and a throttle portion 59 formed radially inward of intake hole 61 to connect intake hole 61 to first cylinder chamber 55A.

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

[0081] The opening shape of the suction hole 61, which serves as the entrance to the suction flow path 52A, may be any shape that matches the shape of the suction pipe 2. Even if the opening shape of the suction hole 61 of the suction flow path 52A is non-circular to match the shape of the suction pipe 2, the shape of the throttle portion 59, which will be described later, can be formed.

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

[0083] The throttle portion 59 opens to the outer surface of the first cylinder 21A on the lower side and radially inward side, has a throttle portion top portion 59A on the upper side, and has a pair of throttle portion side portions 59B that approach each other radially inward on both inner surfaces. That is, the throttle portion 59 opens to the partition plate 25 side of the first cylinder 21A and the inner circumferential wall 155 of the first cylinder chamber 55A, and has the throttle portion top portion 59A on the upper bearing 24A side. The throttle portion 59 has a pair of throttle portion side portions 59B that face each other circumferentially. The pair of throttle portion side portions 59B are formed to approach each other radially inward from the radially outward. In the compressor 1 of the first embodiment, the throttle portion top portion 59A constitutes the blocking wall portion 150 of the throttle portion 59.

[0084] When the first cylinder 21A is viewed in the axial direction, of the pair of throttle portion side surfaces 59B, the throttle portion side surface 59B1 that is farther from the first vane groove 56A in the circumferential direction of the first cylinder 21A is inclined so as to approach the first vane groove 56A as it moves from the outer side to the inner side in the radial direction. As shown in Figure 7, when the first cylinder 21A is viewed in a plan view, of the pair of throttle portion side surfaces 59B, the throttle portion side surface 59B1 that is farther from the first vane groove 56A is inclined more with respect to the axis J1 of the intake passage 52A than the throttle portion side surface 59B2 that is closer to the first vane groove 56A.

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

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

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

[0088] The constriction top portion 59A contributes to improving the rigidity of the first cylinder 21A regardless of whether it is provided on either axial end face of the first cylinder 21A, but from the standpoint of processability and improved rigidity, it is preferable to provide it on the face opposite to the side on which the branch flow path 52AA is formed.

[0089] One end of the throttle portion 59 is open at a shaft-side opening 59D in the axial direction of the rotary shaft 40, and the other end is closed by a throttle top portion 59A. In the radial direction of the rotary shaft 40, one end of the throttle portion 59 communicates with the suction hole 61, and the other end communicates with the first cylinder chamber 55A.

[0090] 8 is a side view seen from the inner peripheral surface side of the first cylinder 21A of the compressor 1 according to Embodiment 1. The dimensions of the intake passage 52A of the first cylinder 21A will be described with reference to FIGS.

[0091] In the inner peripheral 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 constriction top portion 59A in the axial direction of the rotating shaft 40 is defined as thickness B. In the first cylinder 21A, the diameter of the suction hole 61 is defined as diameter C.

[0092] The first cylinder 21A is formed so that a 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 a thickness B, which is the plate thickness of the tapered portion top portion 59A in the axial direction of the rotating shaft 40. In other words, the first cylinder 21A is formed so that the thickness B, which is the plate thickness of the tapered portion top portion 59A in the axial direction of the rotating shaft 40, is smaller 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 so that the relationship of "circumferential length A > thickness B" is satisfied.

[0093] As described above, the intermediate wall portion 155A between the first vane groove 56A and the inner opening 59C is a wall that constitutes the circumferential length A. The wall of the first cylinder 21A that constitutes the intermediate wall portion 155A receives 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 constricted portion top portion 59A constitutes the thickness B as described above. Although the constricted portion top portion 59A receives a pressing force from the first vane 50A, it receives less pressing force from the first vane 50A than the wall that constitutes the intermediate wall portion 155A.

[0094] Therefore, the wall thickness of the constriction top portion 59A is not required to be greater than that of the wall of the portion that defines the circumferential length A. In the compressor 1, by making the constriction top portion 59A thinner than that of the wall of the portion that defines the intermediate wall portion 155A, the weight of the first cylinder 21A can be reduced. Furthermore, the wall thickness of the constriction top portion 59A is not required to be greater than that of the wall of the portion that defines the circumferential length A. In the compressor 1, by making the constriction top portion 59A thinner than the wall of the portion that defines the intermediate wall portion 155A, the diameter of the suction hole 61 formed in the first cylinder 21A can be increased compared to when this configuration is not included.

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

[0096] First cylinder 21A is formed to satisfy the relationship "diameter C > thickness B," which allows for a larger area for forming suction hole 61 compared to when this relationship is not met. In other words, first cylinder 21A is formed to satisfy the relationship "diameter C > thickness B," which allows for a larger diameter for suction hole 61 formed in first cylinder 21A compared to when this relationship is not met.

[0097] The refrigerant flowing in through the suction pipe 2 connected to the first cylinder 21A flows through the suction passage 52A into the first high-pressure chamber 58A, 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. In this way, 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 passage pressure loss, so it is desirable that the diameter of the suction pipe 2 be large.

[0098] Furthermore, since the refrigerant moves inside the suction flow path 52A in the compressor 1, the larger the flow path diameter inside the suction flow path 52A, the smaller the flow path pressure loss, so it is desirable that the flow path diameter inside the suction flow path 52A be large. That is, since the refrigerant moves inside the suction flow path 52A in the compressor 1, the larger the flow path cross-sectional area of ​​the suction flow path 52A, the smaller the flow path pressure loss, so it is desirable that the flow path cross-sectional area of ​​the suction flow path 52A be large.

[0099] Furthermore, the first high-pressure chamber 58A repeatedly draws in, compresses, and discharges refrigerant, and in the compressor 1, there is a risk that, during refrigerant discharge, high-pressure refrigerant within the sealed container 10 may flow back from the first discharge passage 53A into the first high-pressure chamber 58A, which has finished compression and is now at a low pressure. In this case, the refrigerant that has flowed back into the first high-pressure chamber 58A may enter the suction passage 52A, reducing the amount of refrigerant suctioned from the suction pipe 2 and decreasing compressor efficiency. Therefore, in the compressor 1, in order to prevent refrigerant from flowing back into the first high-pressure chamber 58A during refrigerant discharge, it is desirable that the inner opening 59C, which connects the suction passage 52A and the first cylinder chamber 55A, be close to the first vane groove 56A.

[0100] For these reasons, it is desirable to expand intake passage 52A in the axial direction of first cylinder 21A in order to improve the compressor efficiency of compressor 1. Furthermore, in order to improve the compressor efficiency of compressor 1, it is effective to provide a throttle portion 59 at the inner peripheral end of intake passage 52A and connect intake passage 52A to first cylinder chamber 55A at a position close to first vane 50A.

[0101] On the other hand, if the suction hole 61 is enlarged or moved closer to the first vane groove 56A, the wall thickness between the suction hole 61 of the first cylinder 21A and the first vane groove 56A in the compressor 1 becomes thinner. In this case, the compressor 1 may increase the risk of distortion of the first cylinder 21A due to an external force, such as when the suction pipe 2 is pressed into the first cylinder 21A. Furthermore, in this case, the compressor 1 may increase the risk of distortion of the first cylinder 21A due to an external force, such as a pressing force of the first vane 50A against the first cylinder 21A, which is generated by the pressure difference between the first low-pressure chamber 57A and the first high-pressure chamber 58A.

[0102] Therefore, compressor 1 according to the first embodiment has a throttling portion 59 in intake passage 52A. At throttling portion 59, intake passage 52A is formed in a shape in which throttling portion 59 penetrates only one axial surface of first cylinder 21A and the other surface is walled by throttling portion top portion 59A. In compressor 1, throttling portion top portion 59A ensures the rigidity of first cylinder 21A, and throttling portion 59 enables suction passage 52A to be expanded in the axial direction while bringing inner opening 59C, which serves as a connection portion with first cylinder chamber 55A, closer to first vane groove 56A.

[0103] Fig. 9 is a perspective view of a first cylinder 21A according to a modified example of the compressor 1 of Embodiment 1. Fig. 10 is a partially enlarged view of an intake passage 52A according to a modified example of the compressor 1 of Embodiment 1. The radially inner end of the constriction top portion 59A may form a through-portion 63 that penetrates the first cylinder 21A in the axial direction, as shown in Figs. 9 and 10 . The through-portion 63 is a notch formed in the radially inner end of the constriction top portion 59A. The constriction top portion 59A is recessed radially outward at the through-portion 63.

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

[0105] [Detailed Configuration of Internal Intake Flow Passage 52B of Second Cylinder 21B] FIG. 11 is a perspective view of the second cylinder 21B of the compressor 1 according to the first embodiment. FIG. 12 is a partially enlarged view of the internal intake flow passage 52B of the compressor 1 according to the first embodiment. FIG. 13 is a conceptual diagram of the internal intake flow passage 52B of the compressor 1 according to the first embodiment. Note that FIG. 11 is a perspective view of the second cylinder 21B as seen from the partition plate 25 side. Also, FIG. 13 is a conceptual diagram of the internal intake flow passage 52B as seen from the side where the lower bearing 24B is disposed. Next, the configuration of the internal intake flow passage 52B of the second cylinder 21B will be described in detail with reference to FIGS. 11 to 13.

[0106] An internal suction passage 52B is formed in the second cylinder 21B, communicating from the top surface of the second cylinder 21B to the second cylinder chamber 55B. The internal suction passage 52B has a communicating suction hole 62 that extends radially inward from the top surface of the second cylinder 21B through the interior of the second cylinder 21B. The internal suction passage 52B also has a second throttle portion 60 that is formed radially inward of the communicating suction hole 62 and defines a space that communicates between the communicating suction hole 62 and the second cylinder chamber 55B. That is, the internal suction passage 52B includes the communicating suction hole 62 and the second throttle portion 60 that is formed radially inward of the communicating suction hole 62 and defines communication between the communicating suction hole 62 and the second cylinder chamber 55B.

[0107] The communicating suction hole 62 is a hole that extends radially inward from the top surface of the second cylinder 21B through the interior of the second cylinder 21B. The communicating suction hole 62 extends axially downward from the top surface of the second cylinder 21B and then further extends radially inward from there. The communicating suction hole 62 is a hole that communicates between the outside of the second cylinder 21B and the second throttling portion 60. The communicating suction hole 62 is a hole that communicates between the connection path 25A of the partition plate 25 (see FIG. 4 ) and the second throttling portion 60.

[0108] The second throttling portion 60 has a pair of second throttling portion side surfaces 60B that form both inner surfaces of the second throttling portion 60 and are formed so as to approach each other as they move radially inward of the second cylinder 21B. The second throttling portion 60 is formed by the pair of second throttling portion side surfaces 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 the partition plate 25. The second throttling portion 60 is also formed by the pair of second throttling portion side surfaces 60B and has a second inner opening 60C that opens to the radially inward side of the second cylinder 21B so as to communicate with the second cylinder chamber 55B and is formed so as to communicate with the second shaft-side opening 60D. The second throttling 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 so as to close the second throttling portion 60.

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

[0110] When the second cylinder 21B is viewed in the axial direction, of the pair of second throttle portion side surfaces 60B, the second throttle portion side surface 60B1 that is farther from the second vane groove 56B in the circumferential direction of the second cylinder 21B is inclined so as to approach the second vane groove 56B as it moves from the outer side to the inner side in the radial direction. When the second cylinder 21B is viewed in a plan view, of the pair of second throttle portion side surfaces 60B, the second throttle portion side surface 60B1 that is farther from the second vane groove 56B is inclined more with respect to the plane J2 along which the axis of the communicating suction hole 62 extends than the second throttle portion side surface 60B2 that is closer to the second vane groove 56B.

[0111] The second throttle portion 60 has a second inner opening 60C and a second shaft-side opening 60D. A pair of second throttle portion side surfaces 60B define the second shaft-side 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 in the inner surface of the second cylinder 21B and connects the internal space of the second throttle portion 60 with the second cylinder chamber 55B. As shown in FIG. 13 , the second cylinder 21B is formed such that the second inner opening 60C is biased toward the second vane groove 56B with respect to a plane J2 along which the axis of the communicating suction hole 62 extends.

[0112] The second shaft-side opening 60D is an opening formed in the outer surface of the second cylinder 21B on the partition plate 25 side. The second shaft-side opening 60D is covered and closed by the plate surface of the partition plate 25 in the compression mechanism 20. The second throttle portion 60 is formed so that the second shaft-side opening 60D and the second inner opening 60C are continuous with each other in the axial and radial directions of the rotating shaft 40. In other words, the second throttle portion 60 is formed so that the second shaft-side opening 60D and the second inner opening 60C are continuous with each other at the radial inner end of the second cylinder 21B and at the end on the partition plate 25 side.

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

[0114] The constriction bottom 60A contributes to improving the rigidity of the second cylinder 21B regardless of whether it is provided on either axial end face of the second cylinder 21B, but from the standpoint of workability and improved rigidity, it is preferable to provide it on the face opposite to the side on which the communicating suction hole 62 is formed.

[0115] One end of the second throttle portion 60 is open at a second shaft-side opening 60D in the axial direction of the rotary shaft 40, and the other end is closed at a throttle bottom 60A. One end of the second throttle portion 60 is connected to the communicating suction hole 62 in the radial direction of the rotary shaft 40, and the other end is connected to 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 of the constriction bottom portion 60A in the axial direction of the rotating shaft 40 is defined as the thickness B2.

[0117] The second cylinder 21B is formed so that a 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 a thickness B2, which is the plate thickness of the tapered portion bottom 60A in the axial direction of the rotating shaft 40. The second cylinder 21B is formed so that the thickness B2, which is the plate thickness of the tapered portion bottom 60A in the axial direction of the rotating shaft 40, is smaller 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 so that the relationship of "circumferential length A2 > thickness B2" is satisfied.

[0118] As described above, the intermediate wall portion 155B between the second vane groove 56B and the second inner opening 60C is a wall that constitutes the circumferential length A2. The wall of the second cylinder 21B that constitutes the intermediate wall portion 155B receives 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 portion bottom portion 60A constitutes the thickness B2 as described above. Although the constricted portion bottom portion 60A receives a pressing force from the second vane 50B, it receives less pressing force from the second vane 50B than the wall that constitutes the intermediate wall portion 155B.

[0119] Therefore, the thickness of the wall of the constricted portion bottom portion 60A is not required to be greater than that of the wall of the portion that defines the circumferential length A2. By making the thickness of the constricted portion bottom portion 60A thinner than that of the wall of the portion that defines the intermediate wall portion 155B, the weight of the second cylinder 21B can be reduced in the compressor 1. Furthermore, the thickness of the wall of the constricted portion bottom portion 60A is not required to be greater than that of the wall of the portion that defines 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 flow path 52B of the second cylinder 21B. The refrigerant that has flowed into the second high-pressure chamber 58B 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 flow path 53B.

[0121] Furthermore, the second high-pressure chamber 58B repeatedly draws in, compresses, and discharges refrigerant, and in the compressor 1, there is a risk that, during refrigerant discharge, high-pressure refrigerant within the sealed container 10 may flow back from the second discharge passage 53B into the second high-pressure chamber 58B, which has been compressed and is now at a low pressure. In this case, the refrigerant that has flowed back into the second high-pressure chamber 58B may enter the internal suction passage 52B, reducing the amount of refrigerant drawn from the suction pipe 2 and reducing compressor efficiency. Therefore, in the compressor 1, in order to prevent refrigerant from flowing back into the second high-pressure chamber 58B during refrigerant discharge, it is desirable that the second inner opening 60C, which connects the internal suction passage 52B and the second cylinder chamber 55B, be close to the second vane groove 56B.

[0122] For the above reasons, it is desirable to expand the internal intake passage 52B in the axial direction of the second cylinder 21B in order to improve the compressor efficiency of the compressor 1. Furthermore, in order to improve the compressor efficiency of the compressor 1, it is effective to provide a second throttle portion 60 at the inner peripheral end of the internal intake passage 52B and 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 communicating suction hole 62 is enlarged or brought closer to the second vane groove 56B, the wall thickness between the communicating suction hole 62 of the second cylinder 21B and the second vane groove 56B will be thinner in the compressor 1. In such a case, the compressor 1 may increase the risk of distortion of the second cylinder 21B due to an external force, such as a pressing force of the second vane 50B against the second cylinder 21B, which is generated by the pressure difference between the second low-pressure chamber 57B and the second high-pressure chamber 58B.

[0124] Therefore, the compressor 1 according to the first embodiment has a second throttle portion 60 in the internal intake passage 52B. The internal intake passage 52B is formed in a shape in which the second throttle portion 60 penetrates only one axial surface of the second cylinder 21B, and the other surface is walled by a throttle bottom portion 60A. In the compressor 1, the throttle bottom portion 60A ensures the rigidity of the second cylinder 21B, and the second throttle portion 60 expands the internal intake passage 52B in the axial direction, thereby bringing the second inner opening 60C, which serves as a connection portion with the second cylinder chamber 55B, closer to the second vane groove 56B.

[0125] FIG. 14 is a perspective view of a second cylinder 21B according to a modification of the compressor 1 of the first embodiment. FIG. 15 is a partially enlarged view of an internal intake passage 52B according to a modification of the compressor 1 of the first embodiment. The radially inner end of the constricted portion bottom portion 60A may form a second through-portion 63B penetrating the second cylinder 21B in the axial direction, as shown in FIGS. 14 and 15 . The second through-portion 63B is a notch formed in the radially inner end of the constricted portion bottom portion 60A. The constricted portion bottom portion 60A is recessed radially outward at the second through-portion 63B. That is, the constricted portion bottom portion 60A, which is the second blocking wall portion 151, has a radially inner end that has the second through-portion 63B penetrating the second cylinder 21B in the axial direction.

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

[0127] 16 is a schematic configuration diagram of a refrigeration cycle apparatus 200 including the compressor 1 according to Embodiment 1. The refrigeration cycle apparatus 200 includes the compressor 1, a radiator in which the refrigerant compressed by the compressor 1 radiates heat, a pressure reducer 203 such as an electric expansion valve that reduces the pressure of the refrigerant flowing out from the radiator, and an evaporator in which the refrigerant flowing out from the pressure reducer 203 evaporates.

[0128] The refrigeration cycle apparatus 200 is used for various purposes, such as a refrigerator or a freezer, a vending machine, an air conditioner, a freezing apparatus, a hot water supply apparatus, etc. Fig. 16 shows an example in which the refrigeration cycle apparatus 200 is used as an air conditioner. For this reason, the refrigeration cycle apparatus 200 shown in Fig. 16 includes 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] 16 is also capable of cooling operation. For this purpose, the refrigeration cycle apparatus 200 is provided 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 suction muffler 3, which is the refrigerant suction 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 radiator.

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

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

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

[0133] When the refrigeration cycle apparatus 200 performs heating operation, the flow path switching device 201 switches to the flow path shown by the solid line in Fig. 16. As a result, in the refrigeration cycle apparatus 200, the discharge pipe 4 of the compressor 1 is connected to the indoor heat exchanger 204, and the suction 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 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, the high-temperature, high-pressure gaseous refrigerant flows into the indoor heat exchanger 204. The high-temperature, high-pressure gaseous refrigerant that has flowed into the indoor heat exchanger 204 condenses while releasing heat to the indoor air, and flows out of the indoor heat exchanger 204 as a high-pressure liquid refrigerant. 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 refrigerants, do not condense when releasing heat. When a refrigerant that condenses when releasing heat is used, the radiator may also be called a condenser.

[0135] The high-pressure liquid refrigerant that flows out of the indoor heat exchanger 204 flows into the pressure reducer 203. The high-pressure liquid refrigerant that flows into the pressure reducer 203 is reduced in pressure by the pressure reducer 203 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant, which flows out of the pressure reducer 203. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows out of the pressure reducer 203 flows into the outdoor heat exchanger 202. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the outdoor heat exchanger 202 absorbs heat from the outdoor air and evaporates, and flows out of the outdoor heat exchanger 202 as a low-pressure gaseous refrigerant or a two-phase gas-liquid 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 suction muffler 3 of the compressor 1. The low-pressure gaseous refrigerant drawn into the suction muffler 3 of the compressor 1 is compressed by the compression mechanism 20 of the compressor 1 to become high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is discharged again from the compressor 1. That is, when the refrigeration cycle apparatus 200 performs heating operation, the refrigerant circulates as shown by the solid arrows in FIG.

[0137] When the refrigeration cycle apparatus 200 performs cooling operation, the flow path switching device 201 switches to the flow path shown by the dashed line in Fig. 16. As a result, in the refrigeration cycle apparatus 200, the discharge pipe 4 of the compressor 1 is connected to the outdoor heat exchanger 202, and the suction 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 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, the high-temperature, high-pressure gaseous refrigerant flows into the outdoor heat exchanger 202. The high-temperature, high-pressure gaseous refrigerant that has flowed into the outdoor heat exchanger 202 condenses while releasing heat to the outdoor air, and flows out of the outdoor heat exchanger 202 as a high-pressure liquid refrigerant.

[0139] The high-pressure liquid refrigerant that flows out of the outdoor heat exchanger 202 flows into the pressure reducer 203. The high-pressure liquid refrigerant that flows into the pressure reducer 203 is reduced in pressure by the pressure reducer 203 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant, which flows out of the pressure reducer 203. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows out of the pressure reducer 203 flows into the indoor heat exchanger 204. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the indoor heat exchanger 204 absorbs heat from the indoor air and evaporates, and flows out of the indoor heat exchanger 204 as a low-pressure gaseous refrigerant or a two-phase gas-liquid 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 suction muffler 3 of the compressor 1. The low-pressure gaseous refrigerant drawn into the suction muffler 3 of the compressor 1 is compressed by the compression mechanism 20 of the compressor 1 to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is discharged again from the compressor 1. That is, when the refrigeration cycle apparatus 200 performs cooling operation, the refrigerant circulates as shown by the dashed arrows in FIG.

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

[0142] In the compressor 1, the blocking wall portion 150 of the throttle portion 59 ensures the rigidity of the first cylinder 21A, thereby increasing the strength of the first cylinder 21A. Therefore, 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 generated by the pressure difference between the first low-pressure chamber 57A and the first high-pressure chamber 58A, thereby increasing the strength of the first cylinder 21A.

[0143] In compressor 1, the rigidity of first cylinder 21A is ensured by blocking wall portion 150 of throttle portion 59, and the strength of first cylinder 21A can be increased. Therefore, in compressor 1, even when suction pipe 2 is inserted into suction flow path 52A of first cylinder 21A while being shaken, deformation of first cylinder 21A can be suppressed.

[0144] If the blocking wall portions 150 are provided at both ends of the throttle portion 59 in the axial direction of the rotating shaft 40, the opening area and volume of the throttle portion 59 will be reduced, 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 a shaft-side opening portion 59D at one end of the throttle portion 59 in the axial direction of the rotating shaft 40, and a blocking wall portion 150 at the other end. Therefore, in the compressor 1, the shaft-side opening portion 59D increases the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40, while the blocking wall portion 150 ensures the rigidity of the first cylinder 21A, thereby increasing the strength of the first cylinder 21A.

[0145] The first cylinder 21A is formed with an intake passage 52A and a branch passage 52AA branching from the intake passage 52A. The second cylinder 21B is formed with an internal intake passage 52B that communicates from the top surface of the second cylinder 21B to a second cylinder chamber 55B, and the partition plate 25 is formed with a connection path 25A that connects the branch passage 52AA to the internal intake passage 52B. Even when a two-cylinder rotary compressor is used as 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 rotary shaft 40 while ensuring the rigidity of the first cylinder 21A with the blocking wall 150, thereby increasing the strength of the first cylinder 21A.

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

[0147] The second throttling portion 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 blocking wall portion 151, thereby increasing the strength of the second cylinder 21B.

[0148] In the compressor 1, the second blocking wall portion 151 of the second throttle portion 60 ensures the rigidity of the second cylinder 21B, thereby increasing the strength of the second cylinder 21B. Therefore, 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 generated by the pressure difference between the second low pressure chamber 57B and the second high pressure chamber 58B, thereby increasing the strength of the second cylinder 21B.

[0149] In addition, the intake pipe 2 is press-fitted into the intake passage 52A of the first cylinder 21A. Even when the intake pipe 2 is press-fitted into the intake passage 52A of the first cylinder 21A, the compressor 1 can suppress deformation of the first cylinder 21A because the throttle portion 59 has the throttle portion top portion 59A, which is the blocking wall portion 150.

[0150] Furthermore, the radially inner end of the throttle top portion 59A, which is the blocking wall portion 150, has a through-hole 63 that penetrates the first cylinder 21A in the axial direction. In the first cylinder 21A, the refrigerant that reaches the through-hole 63 is more likely to flow to both sides of the first cylinder 21A in the axial direction, and flows into the first cylinder chamber 55A along the lower surface of the upper bearing 24A and the upper surface of the partition plate 25. Compared to a compressor 1 that does not have the through-hole 63, the refrigerant that passes through the through-hole 63 increases the amount of refrigerant drawn in, resulting in increased refrigeration capacity and improved compression efficiency.

[0151] In the compressor, if high-pressure refrigerant flows back from the outside of the first discharge passage toward the low-pressure first cylinder chamber after the compressed refrigerant is discharged from the first cylinder chamber, a circumferentially wide suction passage shortens the time the piston blocks the suction passage. In this case, the backflowing high-pressure refrigerant is more likely to enter the suction passage, reducing the amount of low-pressure refrigerant suctioned into the compression mechanism from the suction pipe, which may result in a decrease in compression efficiency.

[0152] The through-holes 63 of the compressor 1 do not widen the opening of the intake passage 52A in the circumferential direction, but widen the opening of the intake passage 52A in the axial direction. Compared to when the opening of the intake passage 52A is widened in the circumferential direction, the compressor 1 can ensure a sufficient period of time for the piston 22 to close the intake passage 52A, thereby suppressing backflow of refrigerant into the intake passage 52A and suppressing a decrease in compression efficiency.

[0153] Furthermore, the radially inner end of the constriction bottom portion 60A, which is the second blocking wall portion 151, has a second through-portion 63B that penetrates the second cylinder 21B in the axial direction. In the second cylinder 21B, the refrigerant that reaches the second through-portion 63B is more likely to flow to both sides of the second cylinder 21B in the axial direction, and flows into the second cylinder chamber 55B along the upper surface of the lower bearing 24B and the lower surface of the partition plate 25. Compared to a compressor 1 that does not have the second through-portion 63B, the refrigerant passing through the second through-portion 63B increases the amount of refrigerant drawn in, resulting in increased refrigeration capacity and improved compression efficiency.

[0154] Furthermore, the second through-holes 63B of the compressor 1 do not widen the opening of the intake passage 52A in the circumferential direction, but widen the opening of the intake passage 52A in the axial direction. Compared to when the opening of the intake passage 52A is widened in the circumferential direction, the compressor 1 can ensure a sufficient period of time for the piston 22 to close the intake passage 52A, thereby suppressing backflow of refrigerant into the intake passage 52A and suppressing a decrease in compression efficiency.

[0155] The refrigeration cycle apparatus 200 according to the first embodiment includes the compressor 1 according to the first embodiment. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the compressor 1 according to the first embodiment.

[0156] Embodiment 2 Fig. 17 is a schematic vertical cross-sectional view showing the overall configuration of a compressor 1 according to embodiment 2. Fig. 18 is a schematic partial vertical cross-sectional view of a compression mechanism 20 according to embodiment 2. Fig. 19 is a partial enlarged view of an internal intake passage 52B of the compressor 1 according to embodiment 2. Fig. 20 is a partial enlarged view of an intake passage 52A of the compressor 1 according to embodiment 2.

[0157] The compression mechanism 20 of the second embodiment will be described using Figures 17 to 20. Note that parts having the same configuration as those in the compression mechanism 20 of Figures 1 to 16 are assigned the same reference numerals, and descriptions thereof will be omitted. The following description will focus on the configuration of the second embodiment that is different from the first embodiment, and configurations not described in the second embodiment are the same as those in the first embodiment. Note that the compressor 1 has a first cylinder 21A fixed to the sealed container 10, and a second cylinder 21B that is not fixed to the sealed container 10.

[0158] In compressor 1 according to embodiment 1, suction pipe 2 is connected to first cylinder 21A, whereas in compressor 1 according to embodiment 2, suction pipe 2 is connected to second cylinder 21B. Therefore, in compressor 1 according to embodiment 2, the structures of first cylinder 21A and second cylinder 21B are reversed from those of compressor 1 according to embodiment 1. Furthermore, second cylinder 21B of compressor 1 according to embodiment 2 is formed with branch flow path 52AA branching from suction flow path 52A.

[0159] An internal suction passage 52B is formed in the first cylinder 21A, communicating from the underside of the first cylinder 21A to the first cylinder chamber 55A. The internal suction passage 52B has a communicating suction hole 62 that extends radially inward from the underside of the first cylinder 21A through the interior of the first cylinder 21A. The internal suction passage 52B also has a second throttle portion 60 formed radially inward of the communicating suction hole 62, forming a space that communicates between the communicating suction hole 62 and the first cylinder chamber 55A. That is, the internal suction passage 52B includes the communicating suction hole 62 and the second throttle portion 60 formed radially inward of the communicating suction hole 62, communicating between the communicating suction hole 62 and the first cylinder chamber 55A.

[0160] The communicating suction hole 62 is a hole that extends radially inward from the lower surface of the first cylinder 21A through the interior of the first cylinder 21A. The communicating suction hole 62 extends axially downward from the lower surface of the first cylinder 21A and then further extends radially inward from there. The communicating suction hole 62 is a hole that communicates between the outside of the first cylinder 21A and the second throttling portion 60. The communicating suction hole 62 is a hole that communicates between the connection path 25A of the partition plate 25 (see FIG. 4 ) and the second throttling portion 60.

[0161] The constriction top portion 160A contributes to improving the rigidity of the first cylinder 21A regardless of whether it is provided on either axial end face of the first cylinder 21A, but from the standpoint of processability and improved rigidity, it is preferable to provide it on the face opposite to the side on which the communicating suction hole 62 is formed.

[0162] The second throttling portion 60 has a pair of second throttling portion side surfaces 60B that form both inner surfaces of the second throttling portion 60 and are formed so as to approach each other as they move radially inward of the first cylinder 21A. The second throttling portion 60 is formed by the pair of second throttling portion side surfaces 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 the partition plate 25. The second throttling portion 60 is also formed by the pair of second throttling portion side surfaces 60B and has a second inner opening 60C that opens on the radially inward side of the first cylinder 21A so as to communicate with the first cylinder chamber 55A and is formed so as to communicate with the second shaft-side opening 60D. The second throttling 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 so as to close the second throttling portion 60.

[0163] One end of the second throttle portion 60 is open at the second shaft-side opening 60D in the axial direction of the rotary shaft 40, and the other end is closed by the throttle portion top portion 160A. In the radial direction of the rotary shaft 40, one end of the second throttle portion 60 communicates with the communicating suction hole 62, and the other end communicates with the first cylinder chamber 55A.

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

[0165] Intake flow path 52A includes an intake hole 61 extending radially inward from outer peripheral surface 156 of second cylinder 21B, and a throttle portion 59 formed radially inward of intake hole 61 to connect intake hole 61 to second low-pressure chamber 57B. That is, intake flow path 52A includes an intake hole 61 and a throttle portion 59 formed radially inward of intake hole 61 to connect intake hole 61 to second cylinder chamber 55B.

[0166] The suction hole 61 is a hole that extends radially inward from the outer peripheral surface 156 of the second cylinder 21B. The suction hole 61 is a hole that connects the outside of the second cylinder 21B with the throttle portion 59. The tip of the suction pipe 2 is inserted into the suction hole 61. The suction hole 61 is a hole that connects the suction pipe 2 with the throttle portion 59. The opening shape of the suction hole 61, which serves as the entrance to the suction flow path 52A, may be any shape that matches the shape of the suction pipe 2.

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

[0168] One end of the throttle portion 59 is opened by a shaft-side opening 59D, and the other end is closed by a throttle portion bottom 159A in the axial direction of the rotating shaft 40. The throttle portion bottom 159A contributes to improving the rigidity of the second cylinder 21B regardless of whether it is provided on either axial end face of the second cylinder 21B, but from the viewpoint of workability and improving rigidity, it is preferable to provide it on the face opposite to the side on which the branch flow path 52AA is formed.

[0169] The restrictor portion 59 has one end communicating with the suction hole 61 and the other end communicating with the second cylinder chamber 55B in the radial direction of the rotary shaft 40. In the compressor 1 of the second embodiment, the restrictor portion bottom 159A forms the blocking wall portion 150 of the restrictor portion 59.

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

[0171] A connection path 25A is formed in the partition plate 25, which communicates with a branch path 52AA branching from the suction path 52A of the second cylinder 21B. The connection path 25A also communicates with an internal suction path 52B formed in the first cylinder 21A. The connection path 25A connects the branch path 52AA of the second cylinder 21B with the internal suction path 52B of the first cylinder 21A. The connection path 25A connects the internal suction path 52B of the first cylinder 21A with the suction path 52A of the second cylinder 21B.

[0172] Fig. 21 is a partial enlarged view of an internal intake passage 52B of a modified example of the compressor 1 according to Embodiment 2. Fig. 22 is a partial enlarged view of an intake passage 52A of a modified example of the compressor 1 according to Embodiment 2. As shown in Fig. 21 , the radially inner end of the constriction top portion 160A may form a second through-portion 63B that penetrates in the axial direction of the first cylinder 21A. Also, as shown in Fig. 22 , the radially inner end of the constriction bottom portion 159A may form a through-portion 63 that penetrates in the axial direction of the second cylinder 21B.

[0173] The radially inner end of the constriction top portion 160A, which is the second blocking wall portion 151, has a second through portion 63B that penetrates the first cylinder 21A in the axial direction. In the second embodiment, 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 blocked by the plate surface of the upper bearing 24A.

[0174] The radially inner end of the constriction bottom 159A, which is the blocking wall 150, has a through-hole 63 that penetrates the second cylinder 21B in the axial direction. In the second embodiment, the through-hole 63 is an opening formed on the lower bearing 24B side of the second cylinder 21B. In the compression mechanism 20, the through-hole 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 flow path 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 flow path 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 flow path 52B of the first cylinder 21A. The refrigerant that has flowed into the first high-pressure chamber 58A 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 flow path 53A.

[0177] As described above, 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 path pressure loss, and therefore it is desirable to have a larger diameter of the suction pipe 2. Also, since the refrigerant moves inside the suction passage 52A of the compressor 1, the larger the flow path diameter inside the suction passage 52A, the smaller the flow path pressure loss, and therefore it is desirable to have a larger flow path diameter inside the suction passage 52A. In other words, since the refrigerant moves inside the suction passage 52A of the compressor 1, the larger the flow path cross-sectional area of ​​the suction passage 52A, the smaller the flow path pressure loss, and therefore it is desirable to have a larger flow path cross-sectional area of ​​the suction passage 52A.

[0178] Furthermore, the second high-pressure chamber 58B repeatedly draws in, compresses, and discharges refrigerant, and in the compressor 1, there is a risk that, during refrigerant discharge, high-pressure refrigerant in the sealed container 10 may flow back from the second discharge passage 53B into the second high-pressure chamber 58B, which has finished compression and is now at a low pressure. In this case, the refrigerant that has flowed back into the second high-pressure chamber 58B may enter the suction passage 52A, reducing the amount of refrigerant drawn from the suction pipe 2 and reducing compressor efficiency. Therefore, in the compressor 1, in order to prevent refrigerant from flowing back into the second high-pressure chamber 58B during refrigerant discharge, it is desirable that the inner opening 59C, which connects the suction passage 52A and the second cylinder chamber 55B, be close to the second vane groove 56B.

[0179] For these reasons, it is desirable to expand intake passage 52A in the axial direction of second cylinder 21B in order to improve the compressor efficiency of compressor 1. Furthermore, in order to improve the compressor efficiency of compressor 1, it is effective to provide a throttle portion 59 at the inner peripheral end of intake passage 52A and connect intake passage 52A to second cylinder chamber 55B at a position close to second vane 50B.

[0180] On the other hand, if the suction hole 61 is enlarged or moved closer to the second vane groove 56B, the wall thickness between the suction hole 61 of the second cylinder 21B and the second vane groove 56B becomes thinner in the compressor 1. In such a case, the compressor 1 may increase the risk of distortion of the second cylinder 21B due to an external force, such as when the suction pipe 2 is pressed into the second cylinder 21B. Furthermore, the compressor 1 may increase the risk of distortion of the second cylinder 21B due to an external force, such as a pressing force of the second vane 50B against the second cylinder 21B, which is generated by the pressure difference between the second low-pressure chamber 57B and the second high-pressure chamber 58B.

[0181] Therefore, intake passage 52A is formed in a shape such that it penetrates only one axial surface of second cylinder 21B at throttle portion 59, and the other surface is walled by throttle bottom portion 159A. In compressor 1, throttle bottom portion 159A ensures the rigidity of second cylinder 21B, and throttle portion 59 expands intake passage 52A in the axial direction, while allowing inner opening 59C, which serves as a connection portion with second cylinder chamber 55B, to be brought closer to second vane groove 56B.

[0182] Similar to intake passage 52A, internal intake passage 52B is formed in a shape in which second throttle section 60 penetrates only one axial surface of first cylinder 21A, with the other surface being walled by throttle top section 160A. In compressor 1, throttle top section 160A ensures the rigidity of first cylinder 21A, and second throttle section 60 expands internal intake passage 52B in the axial direction while bringing second inner opening 60C, which serves as a connection section with first cylinder chamber 55A, closer to first vane groove 56A.

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

[0184] In the compressor 1, the blocking wall portion 150 of the throttle portion 59 ensures the rigidity of the second cylinder 21B, thereby increasing the strength of the second cylinder 21B. Therefore, 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 generated by the pressure difference between the second low-pressure chamber 57B and the second high-pressure chamber 58B, thereby increasing the strength of the second cylinder 21B.

[0185] In compressor 1, the rigidity of second cylinder 21B is ensured by blocking wall portion 150 of throttle portion 59, and the strength of second cylinder 21B can be increased. Therefore, in compressor 1, even when suction pipe 2 is inserted into suction flow path 52A of second cylinder 21B while shaking, deformation of second cylinder 21B can be suppressed.

[0186] If the blocking wall portions 150 are provided at both ends of the throttle portion 59 in the axial direction of the rotating shaft 40, the opening area and volume of the throttle portion 59 will be reduced, 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 the shaft-side opening portion 59D at one end of the throttle portion 59 in the axial direction of the rotating shaft 40, and the blocking wall portion 150 at the other end. Therefore, in the compressor 1, the shaft-side opening portion 59D increases the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40, while the blocking wall portion 150 ensures the rigidity of the second cylinder 21B, thereby increasing the strength of the second cylinder 21B.

[0187] Second cylinder 21B is formed with suction passage 52A and branch passage 52AA branching from suction passage 52A. First cylinder 21A is formed with internal suction passage 52B that connects the underside of first cylinder 21A to first cylinder chamber 55A, and partition plate 25 is formed with connection path 25A that connects branch passage 52AA and internal suction passage 52B. Even when a two-cylinder rotary compressor is used for compressor 1, compressor 1 can increase the opening area of ​​the passage through which the refrigerant passes in the axial direction of rotary shaft 40 while ensuring the rigidity of second cylinder 21B with blocking wall 150, thereby increasing the strength of second cylinder 21B.

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

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

[0190] In the compressor 1, the second blocking wall portion 151 of the second throttling portion 60 ensures the rigidity of the first cylinder 21A, thereby increasing the strength of the first cylinder 21A. Therefore, 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 generated by the pressure difference between the first low-pressure chamber 57A and the first high-pressure chamber 58A, thereby increasing the strength of the first cylinder 21A.

[0191] In addition, the intake pipe 2 is press-fitted into the intake passage 52A of the second cylinder 21B. Even when the intake pipe 2 is press-fitted into the intake passage 52A of the second cylinder 21B, the compressor 1 can suppress deformation of the second cylinder 21B because the throttle portion 59 is provided with the throttle portion bottom portion 60A, which is the blocking wall portion 150.

[0192] Furthermore, the radially inner end of the constriction bottom 159A, which is the blocking wall 150, has a through-hole 63 that penetrates the second cylinder 21B in the axial direction. In the second cylinder 21B, the refrigerant that reaches the through-hole 63 is more likely to flow to both sides of the second cylinder 21B in the axial direction, and flows into the second cylinder chamber 55B along the upper surface of the lower bearing 24B and the lower surface of the partition plate 25. Compared to a compressor 1 that does not have the through-hole 63, the refrigerant that passes through the through-hole 63 increases the amount of refrigerant drawn in, resulting in increased refrigeration capacity and improved compression efficiency.

[0193] In the compressor, when high-pressure refrigerant flows into the low-pressure second cylinder chamber from the outside of the second discharge passage after the compressed refrigerant is discharged, if the suction passage is wide in the circumferential direction, the piston will block the suction passage for a short time. In this case, the compressor is more likely to allow high-pressure refrigerant to flow back into the suction passage, which may reduce the amount of low-pressure refrigerant drawn into the compression mechanism from the suction pipe, resulting in a decrease in compression efficiency.

[0194] The through-holes 63 of the compressor 1 do not widen the opening of the intake passage 52A in the circumferential direction, but widen the opening of the intake passage 52A in the axial direction. Compared to when the opening of the intake passage 52A is widened in the circumferential direction, the compressor 1 can ensure a sufficient period of time for the piston 22 to close the intake passage 52A, thereby suppressing backflow of refrigerant into the intake passage 52A and suppressing a decrease in compression efficiency.

[0195] Furthermore, the radially inner end of the throttle top portion 160A, which is the second blocking wall portion 151, has a second through-portion 63B that penetrates the first cylinder 21A in the axial direction. In the first cylinder 21A, the refrigerant that reaches the second through-portion 63B is more likely to flow to both sides of the first cylinder 21A in the axial direction, and flows into the first cylinder chamber 55A along the lower surface of the upper bearing 24A and the upper surface of the partition plate 25. Compared to a compressor 1 that does not have the second through-portion 63B, the refrigerant that passes through the second through-portion 63B increases the amount of refrigerant drawn in, resulting in increased refrigeration capacity and improved compression efficiency.

[0196] Furthermore, the second through-holes 63B of the compressor 1 do not widen the opening of the intake passage 52A in the circumferential direction, but widen the opening of the intake passage 52A in the axial direction. Compared to when the opening of the intake passage 52A is widened in the circumferential direction, the compressor 1 can ensure a sufficient period of time for the piston 22 to close the intake passage 52A, thereby suppressing backflow of refrigerant into the intake passage 52A and suppressing 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, and the second cylinder 21B is not fixed to the sealed container 10. When the first cylinder 21A is fixed to the sealed container 10, for example, by welding, distortion may occur in the first cylinder 21A.

[0198] In the compressor 1, the intake pipe 2 is joined to the second cylinder 21B that is not joined to the sealed container 10. In the compressor 1, joining the intake pipe 2 to the sealed container 10 may cause distortion in the second cylinder 21B.

[0199] In compressor 1, suction pipe 2 is joined to second cylinder 21B, and first cylinder 21A is fixed to sealed container 10. By having this configuration, compressor 1 reduces the amount of distortion of first cylinder 21A and increases the amount of distortion of second cylinder 21B compared to when first cylinder 21A is fixed to sealed container 10 and suction pipe 2 is joined to first cylinder 21A.

[0200] In the compressor 1, compared to when the first cylinder 21A is fixed to the sealed container 10 and the suction pipe 2 is joined to the first cylinder 21A, the imbalance in distortion between the first cylinder 21A and the second cylinder 21B that occurs when distortion due to assembly is concentrated on the first cylinder 21A can be eliminated. Therefore, in the compressor 1, it is possible to unify the target values ​​of the processing dimensions of the first cylinder 21A and the second cylinder 21B, taking into account distortion due to assembly.

[0201] At the same time, by shifting the insertion of the suction pipe 2 into the cylinder 21 from the first cylinder 21A to the second cylinder 21B, the number of assembly steps for the first cylinder 21A can be reduced. Note that the first cylinder 21A may be distorted by welding or other processes when it is fixed to the sealed container 10. By reducing the number of assembly steps previously concentrated on the first cylinder 21A, the compressor 1 reduces the variation in distortion during assembly of the first cylinder 21A and can reduce the clearance required for fitting the first vane groove 56A and the first vane 50A. Therefore, the compressor 1 can reduce the amount of compressed refrigerant leaking from the first high-pressure chamber 58A, improving compressor efficiency.

[0202] The refrigeration cycle apparatus 200 according to the second embodiment includes the compressor 1 according to the second embodiment. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the compressor 1 according to the second embodiment.

[0203] Embodiment 3 Fig. 23 is a schematic vertical cross-sectional view showing the overall configuration of a compressor 1 according to embodiment 3. Fig. 24 is a schematic partial vertical cross-sectional view of a compression mechanism 20 according to embodiment 3. Fig. 25 is a perspective view of a first cylinder 21A of the compressor 1 according to embodiment 3. Fig. 26 is a partial enlarged view of an intake flow path 52A of the compressor 1 according to embodiment 3.

[0204] The compression mechanism 20 of the third embodiment will be described with reference to Figures 23 to 26. Note that parts having the same configuration as those in the compression mechanism 20 of Figures 1 to 22 are given the same reference numerals, and descriptions thereof will be omitted. The following description will focus on the configuration of the third embodiment that differs from the first and second embodiments, and configurations not described in the third embodiment are the same as those in the first or second embodiment.

[0205] While the compressors 1 of the first and second embodiments are two-cylinder rotary compressors, the compressor 1 according to the third embodiment is a one-cylinder rotary compressor. The compressor 1 according to the third embodiment has a first cylinder 21A in the compression mechanism 20.

[0206] The compression mechanism 20 includes 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 disposed so as to abut against the upper end surface of the first cylinder 21A, and closes the first cylinder chamber 55A. The lower bearing 24B is disposed so as to abut against the lower end surface of the first cylinder 21A, and closes the first cylinder chamber 55A.

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

[0209] The compressor 1 has an intake passage 52A that communicates from the outer peripheral surface 156 of the first cylinder 21A to the first cylinder chamber 55A. The intake passage 52A includes an intake hole 61 that extends radially inward from the outer peripheral surface 156 of the first cylinder 21A, and a throttle portion 59 that is formed radially inward of the intake hole 61 and that connects the intake hole 61 to the first low-pressure chamber 57A. That is, the intake passage 52A includes the intake hole 61 and the throttle portion 59 that is formed radially inward of the intake hole 61 and that connects the intake hole 61 to the first cylinder chamber 55A.

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

[0211] The throttle portion 59 opens to the outer surface of the first cylinder 21A on the lower side and radially inward side, has a throttle top portion 59A on the upper side, and has throttle side portions 59B that approach each other as they extend radially inward. That is, the throttle portion 59 opens to the lower bearing 24B side of the first cylinder 21A and the inner circumferential wall 155 of the first cylinder chamber 55A, and has the throttle top portion 59A on the upper bearing 24A side. The throttle portion 59 has throttle side portions 59B that face each other in the circumferential direction. The throttle side portions 59B are formed to approach each other as they extend radially inward from the outer side. In the compressor 1 of the third embodiment, the throttle top portion 59A constitutes the blocking wall portion 150 of the throttle portion 59.

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

[0213] One end of the throttle portion 59 is open at a shaft-side opening 59D in the axial direction of the rotary shaft 40, and the other end is closed by a throttle top portion 59A. In the radial direction of the rotary shaft 40, one end of the throttle portion 59 communicates with the suction hole 61, and the other end communicates with the first cylinder chamber 55A.

[0214] In compressor 1 of embodiment 3, upper bearing 24A closes the upper end surface of first cylinder 21A, and lower bearing 24B closes the lower end surface of first cylinder 21A. In compressor 1 of embodiment 3, shaft side opening 59D is closed by lower bearing 24B, and restrictor top portion 59A, which is closing wall 150, is provided to abut against upper bearing 24A.

[0215] Fig. 27 is a perspective view of a first cylinder 21A of a modified example of the compressor 1 according to Embodiment 3. Fig. 28 is a partial enlarged view of an intake passage 52A of a modified example of the compressor 1 according to Embodiment 3. The radially inner end of the constriction top portion 59A may form a through portion 63 that penetrates the first cylinder 21A in the axial direction, as shown in Figs. 27 and 28 .

[0216] [Operation and Effect of Compressor 1] The compressor 1 has a throttle portion 59 in a refrigerant intake passage 52A formed in the first cylinder 21A. The throttle portion 59 has a pair of throttle portion side portions 59B that form both inner surfaces of the throttle portion 59 and are formed to approach each other as they extend radially inward of the first cylinder 21A. The throttle portion 59 also has a shaft-side opening 59D formed by the pair of throttle portion side portions 59B and opening at one end in the axial direction of the rotating shaft 40. The throttle portion 59 also has an inner opening 59C formed by the pair of throttle portion side portions 59B, opening radially inward of the first cylinder 21A so as to communicate with the first cylinder chamber 55A and formed to communicate with the shaft-side opening 59D. The throttle portion 59 also has a throttle portion top portion 59A, which is a plate-shaped blocking wall portion 150 provided at the other end in the axial direction of the rotating shaft 40, to block the throttle portion 59. The constriction portion 59 expands the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 by using the shaft side opening 59D and the inner opening 59C, while ensuring the rigidity of the first cylinder 21A by using the blocking wall portion 150, thereby increasing the strength of the first cylinder 21A.

[0217] In the compressor 1, the blocking wall portion 150 of the throttle portion 59 ensures the rigidity of the first cylinder 21A, thereby increasing the strength of the first cylinder 21A. Therefore, 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 generated by the pressure difference between the first low-pressure chamber 57A and the first high-pressure chamber 58A, thereby increasing the strength of the first cylinder 21A.

[0218] In compressor 1, the rigidity of first cylinder 21A is ensured by blocking wall portion 150 of throttle portion 59, and the strength of first cylinder 21A can be increased. Therefore, in compressor 1, even when suction pipe 2 is inserted into suction flow path 52A of first cylinder 21A while being shaken, deformation of first cylinder 21A can be suppressed.

[0219] If the blocking wall portions 150 are provided at both ends of the throttle portion 59 in the axial direction of the rotating shaft 40, the opening area and volume of the throttle portion 59 will be reduced, 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 a shaft-side opening portion 59D at one end of the throttle portion 59 in the axial direction of the rotating shaft 40, and a blocking wall portion 150 at the other end. Therefore, in the compressor 1, the shaft-side opening portion 59D increases the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40, while the blocking wall portion 150 ensures the rigidity of the first cylinder 21A, thereby increasing the strength of the first cylinder 21A.

[0220] In addition, 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 lower bearing 24B, and the blocking wall 150 is provided to abut against the upper bearing 24A. In the compressor 1, the shaft side opening 59D increases the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40, while the blocking wall 150 ensures the rigidity of the first cylinder 21A, thereby increasing the strength of the first cylinder 21A.

[0221] In addition, the intake pipe 2 is press-fitted into the intake passage 52A of the first cylinder 21A. Even when the intake pipe 2 is press-fitted into the intake passage 52A of the first cylinder 21A, the compressor 1 can suppress deformation of the first cylinder 21A because the throttle portion 59 has the throttle portion top portion 59A, which is the blocking wall portion 150.

[0222] Furthermore, the radially inner end of the throttle top portion 59A, which is the blocking wall portion 150, has a through-hole 63 that penetrates the first cylinder 21A in the axial direction. In the first cylinder 21A, the refrigerant that reaches the through-hole 63 is more likely to flow to both sides of the first cylinder 21A in the axial direction, and flows into the first cylinder chamber 55A along the lower surface of the upper bearing 24A and the upper surface of the partition plate 25. Compared to a compressor 1 that does not have the through-hole 63, the refrigerant that passes through the through-hole 63 increases the amount of refrigerant drawn in, resulting in increased refrigeration capacity and improved compression efficiency.

[0223] In the compressor, when high-pressure refrigerant flows into the low-pressure first cylinder chamber from the outside of the first discharge passage after the compressed refrigerant is discharged, if the suction passage is wide in the circumferential direction, the piston will block the suction passage for a short time. In this case, the compressor is more likely to allow high-pressure refrigerant to flow back into the suction passage, which may reduce the amount of low-pressure refrigerant drawn into the compression mechanism from the suction pipe, resulting in a decrease in compression efficiency.

[0224] The through-holes 63 of the compressor 1 do not widen the opening of the intake passage 52A in the circumferential direction, but widen the opening of the intake passage 52A in the axial direction. Compared to when the opening of the intake passage 52A is widened in the circumferential direction, the compressor 1 can ensure a sufficient period of time for the piston 22 to close the intake passage 52A, thereby suppressing backflow of refrigerant into the intake passage 52A and suppressing a decrease in compression efficiency.

[0225] The refrigeration cycle apparatus 200 according to the third embodiment includes the compressor 1 according to the third embodiment. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the compressor 1 according to the third embodiment.

[0226] Fourth Embodiment Fig. 29 is a schematic longitudinal sectional view showing the overall configuration of a compressor 1 according to a fourth embodiment. Fig. 30 is a schematic partial longitudinal sectional view of a compression mechanism 20 according to the fourth embodiment. The compression mechanism 20 according to the fourth embodiment will be described using Figs. 29 and 30. Note that parts having the same configuration as those in the compression mechanism 20 of Figs. 1 to 28 are given the same reference numerals, and their description will be omitted. The following description will focus on the configuration of the fourth embodiment that differs from the third embodiment, and the configuration not described in the fourth embodiment is the same as that of the first to third embodiments.

[0227] The compressor 1 of the fourth embodiment differs from the compressor 1 of the third embodiment in the structure of the throttling portion 59. The throttling portion 59 in the compressor 1 of the third embodiment has a throttling portion top portion 59A, whereas the throttling portion 59 in the compressor 1 of the fourth embodiment has a throttling portion bottom portion 59A1.

[0228] The throttle portion 59 of the fourth embodiment has an upper side and a radially inner side that open to the outer surface of the first cylinder 21A, a throttle portion bottom 59A1 on the lower side, and throttle portion side portions 59B on both inner surfaces that approach each other radially inward. That is, the throttle portion 59 opens to the upper bearing 24A side of the first cylinder 21A and the inner circumferential wall 155 of the first cylinder chamber 55A, and has the throttle portion bottom 59A1 on the lower bearing 24B side. In the compressor 1 of the third embodiment, the throttle portion bottom 59A1 forms the closing wall portion 150 of the throttle portion 59.

[0229] The shaft-side opening 59D is an opening formed in the outer surface of the first cylinder 21A on the upper bearing 24A side. 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 compressor 1 of embodiment 4, upper bearing 24A closes the upper end surface of first cylinder 21 A, and lower bearing 24B closes the lower end surface of first cylinder 21 A. In compressor 1 of embodiment 4, shaft side opening 59D is closed by upper bearing 24A, and restrictor bottom 59A1, which is closing wall 150, is provided to abut against lower bearing 24B.

[0231] One end of the throttle portion 59 is open at a shaft-side opening 59D in the axial direction of the rotating shaft 40, and the other end is closed by a throttle portion bottom 59A1. One end of the throttle portion 59 is connected to the suction hole 61 in the radial direction of the rotating shaft 40, and the other end is connected to the first cylinder chamber 55A. The throttle portion bottom 59A1 may have a radially inner end that forms a through-portion 63 that passes through the first cylinder 21A in the axial direction.

[0232] [Operation and Effect of Compressor 1] The compressor 1 has a throttle portion 59 in a refrigerant intake passage 52A formed in the first cylinder 21A. The throttle portion 59 has a pair of throttle portion side surfaces 59B that form both inner surfaces of the throttle portion 59 and are formed so as to approach each other as they extend radially inward of the first cylinder 21A. The throttle portion 59 also has a shaft-side opening 59D formed by the pair of throttle portion side surfaces 59B and opening at one end in the axial direction of the rotating shaft 40. The throttle portion 59 also has an inner opening 59C formed by the pair of throttle portion side surfaces 59B and opening radially inward of the first cylinder 21A so as to communicate with the first cylinder chamber 55A and formed so as to communicate with the shaft-side opening 59D. The throttle portion 59 also has a throttle portion bottom 59A1, which is a plate-shaped blocking wall 150 provided at the other end in the axial direction of the rotating shaft 40 so as to close the throttle portion 59. The constriction portion 59 expands the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 by using the shaft side opening 59D and the inner opening 59C, while ensuring the rigidity of the first cylinder 21A by using the blocking wall portion 150, thereby increasing the strength of the first cylinder 21A.

[0233] In the compressor 1, the blocking wall portion 150 of the throttle portion 59 ensures the rigidity of the first cylinder 21A, thereby increasing the strength of the first cylinder 21A. Therefore, 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 generated by the pressure difference between the first low-pressure chamber 57A and the first high-pressure chamber 58A, thereby increasing the strength of the first cylinder 21A.

[0234] In compressor 1, the rigidity of first cylinder 21A is ensured by blocking wall portion 150 of throttle portion 59, and the strength of first cylinder 21A can be increased. Therefore, in compressor 1, even when suction pipe 2 is inserted into suction flow path 52A of first cylinder 21A while being shaken, deformation of first cylinder 21A can be suppressed.

[0235] If the blocking wall portions 150 are provided at both ends of the throttle portion 59 in the axial direction of the rotating shaft 40, the opening area and volume of the throttle portion 59 will be reduced, 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 a shaft-side opening portion 59D at one end of the throttle portion 59 in the axial direction of the rotating shaft 40, and a blocking wall portion 150 at the other end. Therefore, in the compressor 1, the shaft-side opening portion 59D increases the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40, while the blocking wall portion 150 ensures the rigidity of the first cylinder 21A, thereby increasing the strength of the first cylinder 21A.

[0236] In addition, 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 blocking wall 150 is provided to abut against the lower bearing 24B. In the compressor 1, the shaft side opening 59D increases the opening area of ​​the passage through which the refrigerant passes in the axial direction of the rotating shaft 40, while the blocking wall 150 ensures the rigidity of the first cylinder 21A, thereby increasing the strength of the first cylinder 21A.

[0237] The refrigeration cycle apparatus 200 according to the fourth embodiment includes the compressor 1 according to the fourth embodiment. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the compressor 1 according to the fourth embodiment.

[0238] The configurations shown in the above embodiments are merely examples, and may be combined with other known techniques, or part of the configuration may be omitted or modified without departing from the spirit 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. Furthermore, although the number of cylinders 21 is one or two in the embodiments, it may be three or more.

[0239] REFERENCE SIGNS LIST 1 Compressor, 2 Intake pipe, 3 Intake muffler, 4 Discharge piping, 6 Refrigerating machine 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 portion, 40B Second eccentric shaft portion, 41 End, 42 Oil supply hole, 43 First oil supply port, 44 Second oil supply port, 45 Centrifugal pump, 50 Vane, 50A First vane, 50B Second vane, 51A first spring, 51B second spring, 52A 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 throttle portion, 59A throttle portion top portion, 59A1 throttle portion bottom portion, 59B throttle portion side portion, 59B1 throttle portion side portion, 59B2 throttle portion side portion, 59C inner opening, 59D shaft side opening, 60 second throttle portion, 60A Bottom of constricted portion, 60B Second side portion of constricted portion, 60B1 Second side portion of constricted portion, 60B2 Second side portion of constricted portion, 60C Second inner opening, 60D Second shaft side opening, 61 Suction hole, 62 Communication suction hole, 63 Penetration portion, 63B Second penetration portion, 122 Outer circumferential wall, 150 Blocking wall portion, 151 Second blocking wall portion, 155 Inner circumferential wall, 155A Intermediate wall portion, 155B Intermediate wall portion, 156 Outer circumferential surface, 159A Bottom of constricted portion, 160A Top of constricted portion, 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 and a rotating electric machine disposed in the sealed container; a rotating shaft disposed within the sealed container and rotated by the rotating electric machine; a compression mechanism disposed within the sealed container and configured to compress a refrigerant by a driving force transmitted from the rotating electric machine via the rotary shaft; a suction pipe that penetrates the sealed container and is connected to the compression mechanism, and that serves as a flow path for the refrigerant; Equipped with The compression mechanism includes: At least one cylinder formed in a cylindrical shape and defining a cylinder chamber therein; a piston fitted to the rotary shaft and housed in the cylinder chamber, which rotates eccentrically in accordance with the rotation of the rotary shaft to compress the refrigerant; a vane disposed in a vane groove formed to extend in a radial direction of the cylinder, the vane separating the cylinder chamber into two spaces together with the piston; an upper bearing and a lower bearing disposed on an end surface of the cylinder and closing the cylinder chamber; and The cylinder includes: an intake passage that connects the outside of the cylinder with the cylinder chamber is formed; The intake passage is an intake hole extending radially inward from an outer peripheral surface of the cylinder, the intake pipe being connected to the outer peripheral surface; a throttle portion formed radially inward of the suction hole to define a space that connects the suction hole with the cylinder chamber; and The narrowed portion is a pair of constriction side surfaces that form both inner surfaces of the constriction and are formed so as to approach each other as they extend radially inward of the cylinder; a shaft-side opening formed by the pair of tapered portion side surfaces and opening at one end of the rotating shaft in the axial direction; an inner opening formed by the pair of tapered portion side surfaces, the inner opening opening being open radially inward of the cylinder so as to communicate with the cylinder chamber and connected to the shaft-side opening; a plate-shaped closing wall portion provided at the other end of the rotating shaft in the axial direction so as to close the throttle portion; A compressor having

2. The at least one cylinder comprises: 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 disposed below the first cylinder and defining a second cylinder chamber that constitutes a part of the cylinder chamber; Including, The upper bearing is a first cylinder chamber that is disposed on an upper end surface of the first cylinder and that closes the first cylinder chamber; The lower bearing is a second cylinder chamber that is disposed on a lower end surface of the second cylinder and closes the second cylinder chamber; The compression mechanism includes: a partition plate disposed between the first cylinder and the second cylinder and closing the shaft side opening, the first cylinder chamber, and the second cylinder chamber; The first cylinder has the intake passage; a branch flow path branching from the intake flow path; is formed, The second cylinder has an internal intake passage is formed that communicates from an upper surface of the second cylinder to the second cylinder chamber; The partition plate has: The compressor according to claim 1 , further comprising a connecting path that connects the branch passage and the internal suction passage.

3. The internal intake passage is a communicating suction hole extending radially inward from an upper surface of the second cylinder through the interior of the second cylinder; a second throttle portion formed radially inward of the communicating suction hole and defining a space that communicates between the communicating suction hole and the second cylinder chamber; Equipped with The second narrowed portion is a pair of second throttle portion side surfaces that constitute both inner surfaces of the second throttle portion and are formed so as to approach each other as they extend radially inward of the second cylinder; a second shaft-side opening formed by the pair of second narrowed portion side surfaces, opening at one end of the rotary shaft in the axial direction, and closed by the partition plate; a second inner opening formed by the pair of second throttle portion side surfaces, opening radially inward of the second cylinder so as to communicate with the second cylinder chamber, and formed so as to communicate with the second shaft side opening; a plate-shaped second closing wall portion provided at the other end of the rotary shaft in the axial direction so as to close the second throttle portion; 3. The compressor of claim 2, further comprising:

4. The at least one cylinder comprises: a cylindrical first cylinder fixed to the sealed container and forming a first cylinder chamber that is the cylinder chamber; a cylindrical second cylinder disposed below the first cylinder and defining a second cylinder chamber that is the cylinder chamber; Including, The upper bearing is a first cylinder chamber that is disposed on an upper end surface of the first cylinder and that closes the first cylinder chamber; The lower bearing is a second cylinder chamber that is disposed on a lower end surface of the second cylinder and closes the second cylinder chamber; The compression mechanism includes: a partition plate disposed between the first cylinder and the second cylinder and closing the shaft side opening, the first cylinder chamber, and the second cylinder chamber; The second cylinder has the intake passage; a branch flow path branching from the intake flow path; is formed, The first cylinder has an internal intake passage is formed that communicates from a lower surface of the first cylinder to the first cylinder chamber; The partition plate has: The compressor according to claim 1 , further comprising a connecting path that connects the branch passage and the internal suction passage.

5. The internal intake passage is a communicating suction hole extending radially inward from a lower surface of the first cylinder through the interior of the first cylinder; a second throttle portion formed radially inward of the communicating suction hole and defining a space that communicates between the communicating suction hole and the first cylinder chamber; Equipped with The second narrowed portion is a pair of second throttle portion side surfaces that constitute both inner surfaces of the second throttle portion and are formed so as to approach each other as they extend radially inward of the first cylinder; a second shaft-side opening formed by the pair of second narrowed portion side surfaces, opening at one end of the rotary shaft in the axial direction, and closed by the partition plate; a second inner opening formed by the pair of second throttle portion side surfaces, opening radially inward of the first cylinder so as to communicate with the first cylinder chamber, and formed so as to communicate with the second shaft side opening; a plate-shaped second closing wall portion provided at the other end of the rotary shaft in the axial direction so as to close the second throttle portion; 5. The compressor according to claim 4, further comprising:

6. The upper bearing The upper end surface of the cylinder is closed, The lower bearing is The lower end surface of the cylinder is closed, The shaft side opening is The lower bearing is closed, The blocking wall portion is The compressor according to claim 1, wherein the upper bearing is provided so as to abut against the upper bearing.

7. The upper bearing The upper end surface of the cylinder is closed, The lower bearing is The lower end surface of the cylinder is closed, The shaft side opening is is closed by the upper bearing, The blocking wall portion is The compressor according to claim 1, wherein the lower bearing is provided so as to abut against the lower bearing.

8. 8. The compressor according to claim 1, wherein the suction pipe is press-fitted into the suction passage.

9. The compressor according to any one of claims 1 to 7, wherein the blocking wall portion has a through-portion at a radially inner end portion thereof that passes through the cylinder in the axial direction.

10. The compressor according to claim 3 or 5, wherein the second blocking wall portion has a second through-portion at a radially inner end portion thereof that passes through the cylinder in the axial direction.

11. A compressor according to any one of claims 1 to 7; an outdoor heat exchanger that exchanges heat between outdoor air and the refrigerant flowing therein; a pressure reducer that reduces the pressure of the refrigerant flowing therethrough; an indoor heat exchanger that exchanges heat between indoor air and the refrigerant flowing therein; A refrigeration cycle device comprising: