WO2024232007A1

WO2024232007A1 - Compressor and refrigeration cycle apparatus

Info

Publication number: WO2024232007A1
Application number: PCT/JP2023/017415
Authority: WO
Inventors: 拓真塚本
Original assignee: 三菱電機株式会社
Filing date: 2023-05-09
Publication date: 2024-11-14

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

This disclosure relates to a compressor and a refrigeration cycle device.

Conventionally, a rotary compressor has been known in which an electric motor element and a compression element driven by the electric motor element are sealed (see, for example, Patent Document 1). The compression element of this compressor includes a cylinder, an upper end plate and a lower end plate arranged on both end faces of the cylinder, a piston arranged inside the cylinder, and a vane that divides the space formed by the cylinder, the upper end plate, the lower end plate, and the piston into a high pressure chamber and a low pressure chamber. The cylinder also has a suction hole formed to extend radially inward from the outer circumferential surface of the cylinder, and a notch formed on the radially inner side of the suction hole to reduce resistance when refrigerant is sucked in. The notch is formed to penetrate both end faces of the cylinder to increase the opening area of the passage through which the refrigerant flows from the suction hole to the low pressure chamber, and connects the suction hole to the low pressure chamber.

Japanese Patent Application Publication No. 1-244191

However, in the compressor of Patent Document 1, the cutouts are 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 vanes caused by the pressure difference between the high-pressure chamber and the low-pressure chamber.

The present disclosure aims to solve the problems described above and provide a compressor and a refrigeration cycle device that can increase the strength of the cylinder.

The compressor according to the present disclosure comprises 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 has at least one cylinder formed in a cylindrical shape and forming a cylinder chamber therein, a piston that is fitted to the rotating shaft and stored 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 the end faces of the cylinder and close the cylinder chamber. The cylinder has a cylinder An intake passage is formed that connects the outside of the cylinder with the cylinder chamber, and the intake passage extends radially inward from the outer peripheral surface of the cylinder. The intake passage has an intake hole to which the intake pipe is connected on the outer peripheral surface, and a constricted portion formed radially inward of the intake hole to form a space that connects the intake hole with the cylinder chamber. The constricted portion has a pair of constricted portion side portions that form both inner surfaces of the constricted portion and are formed so as to approach each other as they move radially inward of the cylinder, a shaft side opening formed by the pair of constricted portion side portions and opening at one end in the axial direction of the rotating shaft, an inner opening formed by the pair of constricted portion side portions that opens on the radially inward side of the cylinder so as to communicate with the cylinder chamber and is formed to connect with the shaft side opening, and a plate-shaped blocking wall portion provided at the other end in the axial direction of the rotating shaft to block the constricted portion.

The refrigeration cycle device disclosed herein includes a compressor having the above-described configuration, an outdoor heat exchanger that exchanges heat between the 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 the indoor air and the refrigerant flowing inside.

The compressor and refrigeration cycle device 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 portions that form both inner surfaces of the throttling portion and are formed so as to approach each other as they move radially inward of the cylinder. The throttling portion is also formed of a pair of throttling portion side portions 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 of a pair of throttling portion side portions and has an inner opening that opens to the radially inward side 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 portion provided at the other end in the axial direction of the rotating shaft so as to block the throttling portion. The throttling portion can increase the strength of the cylinder by ensuring the rigidity of the cylinder through the blocking wall portion while expanding the opening area of the passage through which the refrigerant passes in the axial direction of the rotating shaft by the shaft side opening and the inner opening.

1 is a schematic vertical cross-sectional view showing an overall configuration of a compressor according to a first embodiment. 2 is a schematic cross-sectional view of a first cylinder portion of the compression mechanism according to the first embodiment. FIG. 3 is a schematic cross-sectional view of a second cylinder portion of the compression mechanism according to the first embodiment. FIG. 1 is a schematic partial vertical cross-sectional view of a compression mechanism according to a first embodiment; FIG. 2 is a perspective view of a first cylinder of the compressor according to the first embodiment. 2 is a partial enlarged view of a suction passage of the compressor according to the first embodiment. FIG. 2 is a conceptual diagram of a suction passage of the compressor according to the first embodiment. FIG. 2 is a side view of the first cylinder of the compressor according to the first embodiment, as viewed from the inner circumferential surface side. FIG. FIG. 11 is a perspective view of a first cylinder of a modified example of the compressor according to the first embodiment. FIG. 4 is a partial enlarged view of an intake passage of a modified example of the compressor according to the first embodiment. FIG. 2 is a perspective view of a second cylinder of the compressor according to the first embodiment. 2 is a partial enlarged view of an internal intake passage of the compressor according to the first embodiment. FIG. 2 is a conceptual diagram of an internal intake passage of the compressor according to the first embodiment. FIG. FIG. 11 is a perspective view of a second cylinder of a modified example of the compressor according to the first embodiment. FIG. 4 is a partial enlarged view of an internal intake passage of a modified example of the compressor according to the first embodiment. 1 is a schematic configuration diagram of a refrigeration cycle device including a compressor according to a first embodiment. FIG. 11 is a schematic vertical cross-sectional view showing the overall configuration of a compressor according to a second embodiment. FIG. 11 is a schematic partial vertical cross-sectional view of a compression mechanism according to a second embodiment. FIG. 11 is a partial enlarged view of an internal intake passage of a compressor according to a second embodiment. FIG. 11 is a partial enlarged view of a suction passage of a compressor according to a second embodiment. FIG. 11 is a partial enlarged view of an internal intake passage of a modified example of the compressor according to the second embodiment. FIG. 11 is a partial enlarged view of a suction passage of a modified example of the compressor according to the second embodiment. FIG. 11 is a schematic vertical cross-sectional view showing the overall configuration of a compressor according to a third embodiment. FIG. 11 is a schematic partial vertical cross-sectional view of a compression mechanism according to a third embodiment. FIG. 11 is a perspective view of a first cylinder of a compressor according to a third embodiment. FIG. 11 is a partial enlarged view of a suction passage of a compressor according to a third embodiment. FIG. 11 is a perspective view of a first cylinder of a modified example of the compressor according to the third embodiment. FIG. 11 is a partial enlarged view of an intake passage of a modified example of the compressor according to the third embodiment. FIG. 11 is a schematic vertical cross-sectional view showing the overall configuration of a compressor according to a fourth embodiment. FIG. 11 is a schematic partial vertical cross-sectional view of a compression mechanism according to a fourth embodiment.

Below, a compressor and a refrigeration cycle device according to an embodiment will be described 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 the actual ones. Furthermore, in the following drawings, the same reference numerals are used to denote the same or equivalent objects, and this applies throughout the entire specification. Furthermore, to facilitate understanding, directional terms (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 parts.

Embodiment 1.
[Configuration of Compressor 1]
Fig. 1 is a schematic vertical cross-sectional view showing an overall configuration of a compressor 1 according to a first embodiment. The compressor 1, which is a hermetic compressor, will be described with reference to Fig. 1. As shown in Fig. 1, the compressor 1 according to the first embodiment is a rolling piston type 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.

Compressor 1 is a two-cylinder rotary compressor, and is a fluid machine that draws low-pressure gas refrigerant into compressor 1 and discharges it as high-pressure gas refrigerant. Note that the two-cylinder rotary compressor is just one example, and rotary compressors of other structures, such as a one-cylinder rotary compressor, may also be used.

The compressor 1 comprises a sealed container 10, a compression mechanism 20, a rotating electric machine 30 arranged in the sealed container 10, and a rotating shaft 40 arranged in the sealed container 10 and driven to rotate by the rotating electric machine 30. The compressor 1 also comprises 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, a compression mechanism 20 that compresses the refrigerant, a rotating electric machine 30 that drives the compression mechanism 20, and a rotating shaft 40 that connects the compression mechanism 20 and the rotating electric machine 30. The compressor 1 is arranged such that the compression mechanism 20 is housed in a lower portion of the sealed container 10, and the rotating electric machine 30 is housed in an upper portion of the sealed container 10.

(Sealed container 10)
The sealed container 10 constitutes the outer shell and external appearance of the compressor 1. The sealed container 10 that constitutes the outer shell of the compressor 1 accommodates a compression mechanism 20, a rotating electric machine 30, a rotating shaft 40, and the like.

The sealed container 10 comprises a body 12 having a substantially cylindrical shape, a head 11 having a substantially hemispherical or bottomed cylindrical shape, and a bottom 13 having a substantially hemispherical or bottomed cylindrical shape. The body 12 forms the outer shell of the middle part of the compressor 1, with the head 11 attached to the upper part and the bottom 13 attached to the 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 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.

A suction pipe 2 for supplying 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.

The stator 32 of the rotating electric machine 30 is attached to the inner circumferential surface of the body portion 12. The 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 often has the compression mechanism 20 attached to the inner circumferential surface of the body portion 12, below the position where the stator 32 is attached.

The head 11 that constitutes the upper part of the sealed container 10 is formed, for example, in a roughly 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 11 of the sealed container 10. The fixed portion between the discharge pipe 4 and the head 11 is joined, for example, by brazing or resistance welding.

The bottom 13 constituting the lower part of the sealed container 10 is formed, for example, in a roughly bowl shape, as shown in FIG. 1. The bottom 13 of the sealed container 10 stores refrigeration oil 6, which is a lubricating oil. That is, the inside of the sealed container 10 stores refrigeration oil 6. The compressor 1 is provided with a centrifugal pump 45 (described later) that pumps up the refrigeration oil 6 at the bottom of the rotating shaft 40. The centrifugal pump 45 pumps up the refrigeration oil 6 stored at 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, this refrigeration oil 6 is supplied to the compression mechanism 20, etc., and friction at the sliding parts of the compression mechanism 20, etc. is reduced. As a result, the compressor 1 ensures mechanical lubrication of the compression mechanism 20.

(Compression mechanism 20)
Fig. 2 is a schematic cross-sectional view of a first cylinder 21A portion of the compression mechanism 20 according to the first embodiment. Fig. 3 is a schematic cross-sectional view of a 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 with reference to Figs. 1 to 4. The compression mechanism 20 is connected to the suction pipe 2 and compresses the refrigerant.

The compression mechanism 20 is disposed within the sealed container 10 and compresses the refrigerant using the 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.

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 this 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.

The compression mechanism 20 has at least one cylinder 21 formed in a cylindrical shape and forming a cylinder chamber 55 therein, and a piston 22 fitted to the rotating shaft 40 and housed in the cylinder chamber 55, rotating eccentrically as the rotating shaft 40 rotates to compress the refrigerant. The compression mechanism 20 also has a vane 50 that is disposed in a vane groove 56 formed to extend radially of the cylinder 21 and that, together with the piston 22, separates the cylinder chamber 55 into two spaces. The compression mechanism 20 also has an upper bearing 24A and a lower bearing 24B that are disposed on the end face of the cylinder 21 and close the cylinder chamber 55.

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.

The first cylinder 21A is cylindrical and forms a first cylinder chamber 55A. The first cylinder 21A is a cylindrical member having the first cylinder chamber 55A inside for compressing the refrigerant and formed into a cylindrical shape with both ends in the axial direction of the rotating shaft 40 open. The first cylinder 21A is formed into a hollow cylindrical shape and has a through hole in the 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, forming the first cylinder chamber 55A. The first cylinder 21A is fixed to the sealed container 10.

The first cylinder chamber 55A contains a first eccentric shaft portion 40A of the rotating shaft 40, which performs eccentric motion inside the first cylinder chamber 55A (described later), and a first piston 22A fitted to the first eccentric shaft portion 40A of the rotating shaft 40. The first cylinder chamber 55A also contains a first vane 50A that divides 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.

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

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

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 the first cylinder chamber 55A and communicates with the first cylinder chamber 55A, and the other end has a first spring hole 54A.

The first spring hole 54A is formed at the radially outer end of the first vane groove 56A of the first cylinder 21A, and passes through the first cylinder 21A in the axial direction to communicate 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.

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.

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

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.

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 inside the first vane groove 56A. The shape of the first vane 50A is a roughly rectangular parallelepiped shape in which the thickness in the circumferential direction of the first cylinder chamber 55A when attached to the first vane groove 56A is smaller than the length in the radial direction of the first cylinder chamber 55A and the axial direction of the first cylinder chamber 55A.

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 in the radial direction 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 is connected to the intake passage 52A, and the first high pressure chamber 58A is connected to 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.

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.

The upper bearing 24A is positioned 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 rotating 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 connect the space formed by the first cylinder 21A and the first piston 22A to the internal space of the first muffler 23A, which will be described later.

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 section (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 from the refrigerant discharge section into the inside of the sealed container 10.

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

The second cylinder 21B is a cylindrical member having a second cylinder chamber 55B therein for compressing the refrigerant, and is formed into a cylindrical shape with both ends in the axial direction of the rotating shaft 40 open. The second cylinder 21B is formed into a hollow cylindrical shape, and a through hole concentric with the axis of the rotating shaft 40 is formed in the center. This 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, forming the second cylinder chamber 55B. The first cylinder chamber 55A and the second cylinder chamber 55B are collectively referred to as the cylinder chamber 55.

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

3 and 4, the second cylinder 21B is formed with an internal intake passage 52B through which the refrigerant is drawn from the upper surface of the second cylinder 21B, and a second discharge passage 53B through the internal space of the sealed container 10 to the discharge pipe 4. The internal intake 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 intake passage 52B of the second cylinder 21B are connected, and the refrigerant is drawn from the intake pipe 2 to the internal intake passage 52B. The detailed configuration of the internal intake passage 52B will be described later.

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 into the second cylinder chamber 55B and communicates with the second cylinder chamber 55B, and the other end has a second spring hole 54B.

The second spring hole 54B is formed at the radially outer end of the second vane groove 56B of the second cylinder 21B, and passes through the second cylinder 21B in the axial direction, communicating with the second vane groove 56B. The second vane groove 56B houses the second vane 50B, and the second spring hole 54B houses the second spring 51B. The first vane groove 56A and the second vane groove 56B are collectively referred to as the vane groove 56.

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.

The second piston 22B rotates freely within the second cylinder 21B. This second piston 22B is configured to perform eccentric rotational motion within the second cylinder 21B. The second piston 22B rotates eccentrically within the second cylinder chamber 55B due to the rotation of the rotating shaft 40.

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.

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 inside the second vane groove 56B. The shape of the second vane 50B is a substantially rectangular parallelepiped shape in which the thickness in the circumferential direction of the second cylinder chamber 55B when attached to the second vane groove 56B is smaller than the length in the radial direction of the second cylinder chamber 55B and the axial direction of the second cylinder chamber 55B.

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 in the radial direction 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 is connected to the internal intake passage 52B, and the second high pressure chamber 58B is connected to 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.

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.

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 rotating 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, which will be described later.

The lower bearing 24B is provided with a second muffler 23B that discharges the refrigerant compressed by the second cylinder 21B and the second piston 22B. The internal space of the second muffler 23B is connected to the internal space of the first muffler 23A through 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 through the refrigerant flow path (not shown) formed in the compression mechanism 20. The refrigerant that flows into the internal space of the first muffler 23A is then discharged into the inside of the sealed container 10 from the refrigerant discharge portion (not shown) of the first muffler 23A.

The partition plate 25 is formed in a plate or column 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, and closes 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 the shaft side opening 59D (see FIG. 6) and the second shaft side opening 60D (see FIG. 12), the first cylinder chamber 55A, and the second cylinder chamber 55B, which will be described later.

The partition plate 25 is formed with a connection path 25A that communicates with a branched flow path 52AA branching off from the intake flow path 52A of the first cylinder 21A. The connection path 25A also communicates with an internal intake flow 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 communicates between the branched flow path 52AA of the first cylinder 21A and the internal intake flow path 52B of the second cylinder 21B. The connection path 25A communicates between the intake flow path 52A of the first cylinder 21A and the internal intake flow path 52B of the second cylinder 21B.

(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 by 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. For example, a brushless DC motor is used as the rotating electric machine 30.

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 into a hollow cylindrical shape when viewed from above. The rotor 31 is rotatably mounted inside the stator 32, and rotates by magnetic action.

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 the laminated core of the stator 32, causing a rotating magnetic field to form 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.

(Rotation 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.

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 about 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 the upper bearing 24A and the lower bearing 24B of the compression mechanism 20.

As shown in FIG. 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.

The rotating shaft 40 has the first piston 22A connected to the first eccentric shaft portion 40A so as to be capable of eccentric rotational movement, and the second piston 22B connected to the second eccentric shaft portion 40B so as to be capable of eccentric rotational movement. In other words, the rotating shaft 40 has the first piston 22A and the second piston 22B connected to it so as to be capable of eccentric rotational movement between a portion rotatably supported by the upper bearing 24A and a portion rotatably supported by the lower bearing 24B.

As a result, in the compressor 1, the rotating shaft 40 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 sucked in from the outside using the power of the rotating electric machine 30 transmitted by the rotating shaft 40.

The rotating shaft 40 has an oil supply hole 42 formed at the 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 the first end. In the compressor 1 of this embodiment 1, the end 41 is the lower end of the rotating shaft 40. The oil supply hole 42 extends along the center of rotation of the rotating shaft 40.

The rotating shaft 40 is also formed with a first oil supply port 43 and a second oil supply port 44. The first oil supply port 43 and the second oil supply port 44 are flow paths that supply the refrigeration oil 6 sucked into the oil supply hole 42 to the sliding parts of the compression mechanism 20. One end of the first oil supply port 43 and the second oil supply port 44 is connected to the oil supply hole 42. The other end of the first oil supply port 43 and the second oil supply 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 supply port 43 opens at a location that faces the upper bearing 24A of the compression mechanism 20. The other end of the second oil supply port 44 opens at a location that faces the lower bearing 24B of the compression mechanism 20.

(Suction pipe 2)
The suction pipe 2 passes through the sealed container 10 and is connected to the compression mechanism 20, and serves as a refrigerant flow path. The suction pipe 2 supplies refrigerant into the sealed container 10. As described above, the suction pipe 2 is connected to the body 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-sectional shape, or may be a non-circular pipe having a cross-sectional shape such as an ellipse or an oval.

(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 and high-pressure refrigerant inside the sealed container 10 to the outside of the sealed container 10.

(Intake 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.

(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-shaped member. The centrifugal pump 45 is a fluid machine that sucks up the refrigeration oil 6 as a lubricant oil stored in the bottom 13 of the sealed container 10 by centrifugal force generated by the rotational motion of the rotating shaft 40.

The refrigeration oil 6 pumped up to the oil supply hole 42 by the centrifugal pump 45 is supplied to the sliding parts of the compression mechanism 20. Specifically, a portion of the refrigeration oil 6 pumped up to the oil supply hole 42 is supplied to the sliding parts between the upper bearing 24A and the rotating shaft 40 of the compression mechanism 20 through the first oil supply port 43. Also, a portion of the refrigeration oil 6 pumped up to the oil supply hole 42 is supplied to the sliding parts between the lower bearing 24B and the rotating shaft 40 of the compression mechanism 20 through the second oil supply port 44. As the refrigeration oil 6, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, and polyol ester-based lubricating oils are used.

[Operation of Compressor 1]
In the compressor 1, the first piston 22A and the second piston 22B perform an eccentric rotational motion, whereby the refrigerant is drawn into the inside of the compressor 1. Specifically, in the compressor 1, the first piston 22A and the second piston 22B perform an eccentric rotational motion, whereby the low-pressure refrigerant outside the compressor 1 flows into the suction muffler 3. Then, in the compressor 1, the low-pressure gaseous refrigerant out of the low-pressure refrigerant that has flowed into the suction muffler 3 flows into the compression mechanism 20 of the compressor 1 via the suction pipe 2.

A portion of the gaseous refrigerant that flows 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 the valve of the upper bearing 24A. The high-temperature, high-pressure gaseous refrigerant that flows into the internal space of the first muffler 23A is discharged into the internal space of the sealed container 10 from a refrigerant discharge section (not shown) provided in the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant that is discharged into the internal space of the sealed container 10 then moves to the upper part of the space inside the sealed container 10 through gaps in the rotating electric machine 30, etc., and is discharged from the discharge pipe 4.

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

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

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

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. Further, 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.

[Detailed configuration of intake 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 passage 52A of the compressor 1 according to the first embodiment. Fig. 7 is a conceptual diagram of the intake passage 52A of the compressor 1 according to the first embodiment. Fig. 5 is a perspective view of the first cylinder 21A as viewed from the partition plate 25 side. Fig. 7 is a conceptual diagram of the intake passage 52A as viewed from the side where the rotating electric machine 30 is disposed. Next, the configuration of the intake passage 52A of the first cylinder 21A will be described in detail with reference to Figs. 5 to 7.

The compressor 1 has an intake passage 52A that connects from the outer circumferential 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 connects from the top 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.

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

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

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 to the throttling 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 to the throttling portion 59.

The opening shape of the suction hole 61, which is the entrance to the suction flow passage 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 passage 52A is non-circular to match the shape of the suction pipe 2, the shape of the narrowing portion 59 described below can be formed.

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

The throttling portion 59 opens to the outer surface of the first cylinder 21A on the lower side and the radially inner side, has a throttling portion top portion 59A on the upper side, and has a pair of throttling portion side portions 59B that approach each other as both inner surfaces move radially inward. That is, the throttling 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 throttling portion top portion 59A on the upper bearing 24A side. The throttling portion 59 has a pair of throttling portion side portions 59B that face each other in the circumferential direction. The pair of throttling portion side portions 59B are formed so as to approach each other as they move from the radially outer side to the radially inner side. In the compressor 1 of embodiment 1, the throttling portion top portion 59A forms the blocking wall portion 150 of the throttling portion 59.

When the first cylinder 21A is viewed in the axial direction, of the pair of throttle side portions 59B, the throttle side portion 59B1 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 radially outward to the radially inward direction. As shown in FIG. 7, when the first cylinder 21A is viewed in a plan view, of the pair of throttle side portions 59B, the throttle side portion 59B1 farther from the first vane groove 56A is inclined more with respect to the axis J1 of the intake passage 52A than the throttle side portion 59B2 closer to the first vane groove 56A.

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

The shaft side opening 59D is an opening formed on 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 throttling portion 59 is formed so that the shaft side opening 59D and the inner opening 59C are connected in the axial and radial directions of the rotating shaft 40. In other words, the throttling portion 59 is formed so that the shaft side opening 59D and the inner opening 59C are connected at the radial inner end of the first cylinder 21A and the end on the partition plate 25 side.

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

The tapered portion top portion 59A contributes to improving the rigidity of the first cylinder 21A regardless of which side of the axial end face the tapered portion 59A is provided on. However, from the standpoint of workability and improved rigidity, it is preferable to provide it on the side opposite the side on which the branch flow path 52AA is formed.

One end of the constriction 59 opens into the shaft side opening 59D in the axial direction of the rotating shaft 40, and the other end is closed by the constriction top 59A. One end of the constriction 59 communicates with the suction hole 61 in the radial direction of the rotating shaft 40, and the other end communicates with the first cylinder chamber 55A.

FIG. 8 is a side view of the first cylinder 21A of the compressor 1 according to the first embodiment, seen from the inner circumferential surface side. The dimensions of the intake passage 52A of the first cylinder 21A will be explained using FIG. 6 and FIG. 8.

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.

The first cylinder 21A is formed so that the circumferential length A, which is the distance between the first vane groove 56A and the inner opening 59C in the circumferential direction of the first cylinder 21A, is greater than the thickness B, which is the 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.

As described above, the intermediate wall portion 155A between the first vane groove 56A and the inner opening 59C is a wall of the portion 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 constriction top portion 59A constitutes the thickness B as described above. The constriction top portion 59A receives a pressing force from the first vane 50A, but receives less pressing force from the first vane 50A than the wall of the portion that constitutes the intermediate wall portion 155A.

Therefore, the constriction top portion 59A does not need to be thicker than the wall of the portion that constitutes the circumferential length A. The compressor 1 can reduce the weight of the first cylinder 21A by making the constriction top portion 59A thinner than the wall of the portion that constitutes the intermediate wall portion 155A. Also, the constriction top portion 59A does not need to be thicker than the wall of the portion that constitutes the circumferential length A. The compressor 1 can increase the diameter of the suction hole 61 formed in the first cylinder 21A compared to a case where this configuration is not included by making the constriction top portion 59A thinner than the wall of the portion that constitutes the intermediate wall portion 155A.

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

The first cylinder 21A is formed so that the relationship "diameter C > thickness B" is satisfied, and therefore the range of the suction hole 61 can be made larger than when this relationship does not exist. In other words, the first cylinder 21A is formed so that the relationship "diameter C > thickness B" is satisfied, and therefore the diameter of the suction hole 61 formed in the first cylinder 21A can be made larger than when this relationship does not exist.

The refrigerant flowing in from 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 pipe diameter of the suction pipe 2 of the compressor 1, the smaller the flow passage pressure loss, so it is desirable for the pipe diameter of the suction pipe 2 to be large.

In addition, since the refrigerant moves inside the intake passage 52A of the compressor 1, the larger the flow passage diameter inside the intake passage 52A, the smaller the flow passage pressure loss, so it is desirable that the flow passage diameter inside the intake passage 52A be large. In other words, since the refrigerant moves inside the intake passage 52A of the compressor 1, the larger the flow passage cross-sectional area of the intake passage 52A, the smaller the flow passage pressure loss, so it is desirable that the flow passage cross-sectional area of the intake passage 52A be large.

In addition, the first high pressure chamber 58A repeatedly draws in, compresses, and exhausts the refrigerant, and when the refrigerant is exhausted, the high pressure refrigerant inside the sealed container 10 may flow back from the first discharge passage 53A into the first high pressure chamber 58A, which has been compressed 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 intake passage 52A, reducing the amount of refrigerant sucked in from the intake pipe 2 and decreasing the compressor efficiency. Therefore, in order to prevent the refrigerant from flowing back into the first high pressure chamber 58A when the refrigerant is exhausted, it is preferable that the inner opening 59C, which is the connection between the intake passage 52A and the first cylinder chamber 55A, is close to the first vane groove 56A.

In view of the above, it is desirable for the compressor 1 to expand the intake passage 52A in the axial direction of the first cylinder 21A in order to improve the compressor efficiency. Also, in order to improve the compressor efficiency of the compressor 1, it is effective to provide a constriction 59 at the inner end of the intake passage 52A and connect the intake passage 52A to the first cylinder chamber 55A at a position close to the first vane 50A.

On the other hand, when the suction hole 61 is enlarged and when the suction hole 61 is brought closer to the first vane groove 56A, the thickness of the wall between the suction hole 61 of the first cylinder 21A and the first vane groove 56A of the compressor 1 becomes thinner. In such a case, the compressor 1 may increase the risk of distortion of the first cylinder 21A due to external forces such as the pressure of the suction pipe 2 being pressed into the first cylinder 21A. In addition, in such a case, the compressor 1 may increase the risk of distortion of the first cylinder 21A due to external forces such as the pressing force of the first vane 50A against the first cylinder 21A caused by the pressure difference between the first low pressure chamber 57A and the first high pressure chamber 58A.

The compressor 1 according to the first embodiment has a throttling portion 59 in the intake passage 52A. The intake passage 52A is formed in a shape in which the throttling portion 59 penetrates only one side of the first cylinder 21A in the axial direction, and the other side is walled by the throttling portion top portion 59A. The throttling portion top portion 59A ensures the rigidity of the first cylinder 21A, and the throttling portion 59 can expand the intake passage 52A in the axial direction while bringing the inner opening 59C, which is the connection portion with the first cylinder chamber 55A, closer to the first vane groove 56A.

FIG. 9 is a perspective view of the first cylinder 21A of a modified example of the compressor 1 according to the first embodiment. FIG. 10 is a partially enlarged view of the intake passage 52A of a modified example of the compressor 1 according to the first embodiment. The constriction top portion 59A may have a through portion 63 formed at the radially inner end thereof, penetrating the first cylinder 21A in the axial direction, as shown in FIGS. 9 and 10. The through portion 63 is a notch formed at the radially inner end of the constriction top portion 59A. The constriction top portion 59A is recessed radially outward at the through portion 63.

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

[Detailed configuration of the internal intake passage 52B of the 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 passage 52B of the compressor 1 according to the first embodiment. FIG. 13 is a conceptual diagram of the internal intake passage 52B of the compressor 1 according to the first embodiment. FIG. 11 is a perspective view of the second cylinder 21B as viewed from the partition plate 25 side. FIG. 13 is a conceptual diagram of the internal intake passage 52B as viewed from the side where the lower bearing 24B is disposed. Next, the configuration of the internal intake passage 52B of the second cylinder 21B will be described in detail with reference to FIGS. 11 to 13.

The second cylinder 21B has an internal intake passage 52B that connects from the top surface of the second cylinder 21B to the second cylinder chamber 55B. The internal intake passage 52B has a communicating intake hole 62 that extends radially inward from the top surface of the second cylinder 21B through the inside of the second cylinder 21B. The internal intake passage 52B also has a second throttling portion 60 that is formed radially inward of the communicating intake hole 62 and forms a space that connects the communicating intake hole 62 to the second cylinder chamber 55B. That is, the internal intake passage 52B has the communicating intake hole 62 and the second throttling portion 60 that is formed radially inward of the communicating intake hole 62 and connects the communicating intake hole 62 to the second cylinder chamber 55B.

The communicating suction hole 62 is a hole that extends radially inward from the top surface of the second cylinder 21B through the inside of the second cylinder 21B. The communicating suction hole 62 extends axially downward from the top surface of the second cylinder 21B and then extends radially inward from there. The communicating suction hole 62 is a hole that connects the outside of the second cylinder 21B with the second throttling portion 60. The communicating suction hole 62 is a hole that connects the connection path 25A (see Figure 4) of the partition plate 25 with the second throttling portion 60.

The second throttling portion 60 has a pair of second throttling portion side portions 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 also formed of a pair of second throttling portion side portions 60B, has a second shaft side opening 60D that opens at one end in the axial direction of the rotating shaft 40 and is closed by a partition plate 25. The second throttling portion 60 is also formed of a pair of second throttling portion side portions 60B, has a second inner opening 60C that opens to communicate with the second cylinder chamber 55B on the radially inner side of the second cylinder 21B 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.

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

When the second cylinder 21B is viewed in the axial direction, of the pair of second throttle portion side portions 60B, the second throttle portion side portion 60B1 on the side 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 radially outer side to the radially inner side. When the second cylinder 21B is viewed in a plan view, of the pair of second throttle portion side portions 60B, the second throttle portion side portion 60B1 on the side farther from the second vane groove 56B is inclined with respect to the plane J2 along which the axis of the communicating suction hole 62 extends, more so than the second throttle portion side portion 60B2 on the side closer to the second vane groove 56B.

The second throttling portion 60 has a second inner opening 60C and a second shaft side opening 60D. A pair of second throttling portion side portions 60B constitute 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 is an opening that connects the internal space of the second throttling portion 60 to the second cylinder chamber 55B. As shown in FIG. 13, the second cylinder 21B is formed so that the second inner opening 60C is biased toward the second vane groove 56B with respect to the plane J2 along which the axis of the communicating suction hole 62 extends.

The second shaft side opening 60D is an opening formed on the outer surface of the second cylinder 21B on the partition plate 25 side. 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 throttling portion 60 is formed so that the second shaft side opening 60D and the second inner opening 60C are connected in the axial and radial directions of the rotating shaft 40. In other words, the second throttling portion 60 is formed so that the second shaft side opening 60D and the second inner opening 60C are connected at the radial inner end of the second cylinder 21B and the end on the partition plate 25 side.

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

The constriction bottom 60A contributes to improving the rigidity of the second cylinder 21B regardless of which side of the axial end face of the second cylinder 21B it is located on. However, from the standpoint of workability and improved rigidity, it is preferable to locate it on the side opposite the side on which the communicating suction hole 62 is formed.

The second throttling portion 60 has one end that opens into the second shaft side opening 60D in the axial direction of the rotating shaft 40, and the other end that is closed by the throttling portion bottom portion 60A. In the radial direction of the rotating shaft 40, the second throttling portion 60 has one end that communicates with the communicating suction hole 62, and the other end that communicates with the second cylinder chamber 55B.

In the inner peripheral 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.

The second cylinder 21B is formed so that the circumferential length A2, which is the distance between the second vane groove 56B and the second inner opening 60C in the circumferential direction of the second cylinder 21B, is greater than the thickness B2, which is the plate thickness of the constricted 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 constricted 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.

The intermediate wall portion 155B between the second vane groove 56B and the second inner opening 60C is the wall of the portion that constitutes the circumferential length A2, as described above. 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. The constricted portion bottom portion 60A receives a pressing force from the second vane 50B, but receives less pressing force from the second vane 50B than the wall of the portion that constitutes the intermediate wall portion 155B.

Therefore, the constricted portion bottom portion 60A does not need to be thicker than the walls of the portion that defines the circumferential length A2. By making the constricted portion bottom portion 60A thinner than the walls of the portion that defines the intermediate wall portion 155B, the compressor 1 can reduce the weight of the second cylinder 21B. Also, the constricted portion bottom portion 60A does not need to be thicker than the walls of the portion that defines the circumferential length A2.

The refrigerant flowing in from the suction pipe 2 connected to the first cylinder 21A flows into the second high-pressure chamber 58B through the connection path 25A of the partition plate 25 and the internal suction passage 52B of the second cylinder 21B. The refrigerant that flows 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 passage 53B.

In addition, the second high-pressure chamber 58B repeatedly draws in, compresses, and exhausts the refrigerant, and when the refrigerant is exhausted, the high-pressure refrigerant inside 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 intake passage 52B, reducing the amount of refrigerant sucked in from the intake pipe 2 and decreasing the compressor efficiency. Therefore, in order to prevent the refrigerant from flowing back into the second high-pressure chamber 58B when the refrigerant is exhausted, it is preferable that the second inner opening 60C, which is the connection between the internal intake passage 52B and the second cylinder chamber 55B, is close to the second vane groove 56B.

In view of the above, it is desirable for the compressor 1 to expand the internal intake passage 52B in the axial direction of the second cylinder 21B in order to improve the compressor efficiency. Also, in order to improve the compressor efficiency, it is effective for the compressor 1 to have a second throttling portion 60 at the inner end of the internal intake passage 52B and to connect the internal intake passage 52B to the second cylinder chamber 55B at a position close to the second vane 50B.

On the other hand, when the communicating suction hole 62 is enlarged and when the communicating suction hole 62 is brought closer to the second vane groove 56B, the thickness of the wall between the communicating suction hole 62 of the second cylinder 21B and the second vane groove 56B of the compressor 1 becomes thinner. In such a case, the compressor 1 may increase the risk of distortion of the second cylinder 21B due to external forces such as the pressing force of the second vane 50B against the second cylinder 21B caused by the pressure difference between the second low pressure chamber 57B and the second high pressure chamber 58B.

The compressor 1 according to the first embodiment has a second throttling section 60 in the internal intake passage 52B. The internal intake passage 52B is formed in a shape in which the second throttling section 60 penetrates only one axial side of the second cylinder 21B, and the other side is walled by the throttling section bottom 60A. The compressor 1 ensures the rigidity of the second cylinder 21B by the throttling section bottom 60A, and the second throttling section 60 can expand the internal intake passage 52B in the axial direction while bringing the second inner opening 60C, which is the connection part with the second cylinder chamber 55B, closer to the second vane groove 56B.

FIG. 14 is a perspective view of the second cylinder 21B of the modified compressor 1 according to the first embodiment. FIG. 15 is a partial enlarged view of the internal intake passage 52B of the modified compressor 1 according to the first embodiment. The constriction bottom 60A may have a second through-hole 63B at its radially inner end that penetrates the second cylinder 21B in the axial direction as shown in FIGS. 14 and 15. The second through-hole 63B is a notch formed at the radially inner end of the constriction bottom 60A. The constriction bottom 60A is recessed radially outward at the second through-hole 63B. That is, the constriction bottom 60A, which is the second blocking wall 151, has a radially inner end that has a second through-hole 63B that penetrates the second cylinder 21B in the axial direction.

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

[Configuration of refrigeration cycle device 200]
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.

The refrigeration cycle device 200 is used for various purposes, such as a refrigerator or freezer, a vending machine, an air conditioner, a freezing device, a hot water supply device, etc. FIG. 16 shows an example in which the refrigeration cycle device 200 is used as an air conditioner. For this reason, the refrigeration cycle device 200 shown in FIG. 16 is equipped with an indoor heat exchanger 204 that functions as a radiator during heating operation, and an outdoor heat exchanger 202 that functions as an evaporator during heating operation.

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

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.

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.

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

When the refrigeration cycle device 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 device 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.

In this state, when the high-temperature, high-pressure gaseous refrigerant compressed by compressor 1 is discharged from compressor 1, the refrigeration cycle device 200 flows into the indoor heat exchanger 204. The high-temperature, high-pressure gaseous refrigerant that flows into the indoor heat exchanger 204 condenses while releasing heat to the indoor air, and flows out of the indoor heat exchanger 204 as a high-pressure liquid refrigerant. At this time, the air in the room is warmed by the heat released by the refrigerant. Note that, depending on the type of refrigerant, such as carbon dioxide refrigerant, there are refrigerants that do not condense when releasing heat. When a refrigerant that condenses when releasing heat is used, the radiator may also be called a condenser.

The high-pressure liquid refrigerant flowing out from the indoor heat exchanger 204 flows into the pressure reducer 203. The high-pressure liquid refrigerant that flowed into the pressure reducer 203 is then depressurized by the pressure reducer 203 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant, which flows out from the pressure reducer 203. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows out from 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.

The low-pressure gaseous refrigerant or gas-liquid two-phase refrigerant flowing out of the outdoor heat exchanger 202 is sucked into the suction muffler 3 of the compressor 1. The low-pressure gaseous refrigerant among the refrigerants sucked 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 device 200 is performing heating operation, the refrigerant circulates as shown by the solid arrows in FIG. 16.

When the refrigeration cycle device 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 device 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.

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

The high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 202 flows into the pressure reducer 203. The high-pressure liquid refrigerant that flowed into the pressure reducer 203 is then depressurized 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 two-phase gas-liquid refrigerant. At this time, the indoor air is cooled by the heat absorbed by the refrigerant.

The low-pressure gaseous refrigerant or gas-liquid two-phase refrigerant flowing out of the indoor heat exchanger 204 is sucked into the suction muffler 3 of the compressor 1. The low-pressure gaseous refrigerant among the refrigerants sucked 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. In other words, when the refrigeration cycle device 200 performs cooling operation, the refrigerant circulates as shown by the dashed arrows in FIG. 16.

[Function and effect of compressor 1]
The compressor 1 has a throttling portion 59 in the refrigerant intake passage 52A formed in the first cylinder 21A. The throttling portion 59 has a pair of throttling portion side portions 59B that form both inner surfaces of the throttling portion 59 and are formed so as to approach each other as they move radially inward of the first cylinder 21A. The throttling portion 59 is also formed of the pair of throttling portion side portions 59B and has a shaft side opening 59D that opens at one end in the axial direction of the rotating shaft 40. The throttling portion 59 is also formed of the pair of throttling portion side portions 59B and has an inner opening 59C that opens to 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 throttling portion 59 also has a throttling portion top portion 59A that 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 block the throttling 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 the shaft side opening 59D and the inner opening 59C, while ensuring the rigidity of the first cylinder 21A by the blocking wall portion 150, thereby increasing the strength of the first cylinder 21A.

The compressor 1 ensures the rigidity of the first cylinder 21A by the blocking wall portion 150 of the constriction portion 59, and can increase 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, and can increase the strength of the first cylinder 21A.

The compressor 1 ensures the rigidity of the first cylinder 21A by the blocking wall portion 150 of the narrowing portion 59, and can increase the strength of the first cylinder 21A. Therefore, the compressor 1 can suppress deformation of the first cylinder 21A even when the intake pipe 2 is inserted into the intake passage 52A of the first cylinder 21A while shaking it.

If blocking walls 150 are provided at both ends of the throttling portion 59 in the axial direction of the rotating shaft 40, the opening area and volume of the throttling portion 59 become smaller, so the compressor 1 experiences greater pressure loss and the refrigerant is less likely to enter the first cylinder chamber 55A. The compressor 1 has a shaft side opening 59D at one end of the throttling portion 59 in the axial direction of the rotating shaft 40, and a blocking wall 150 at the other end. Therefore, the compressor 1 can expand 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, while ensuring the rigidity of the first cylinder 21A by using the blocking wall 150, thereby increasing the strength of the first cylinder 21A.

The first cylinder 21A is formed with an intake passage 52A and a branch passage 52AA branching off from the intake passage 52A. The second cylinder 21B is formed with an internal intake passage 52B that leads from the top surface of the second cylinder 21B to the 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 if a two-cylinder rotary compressor is used for the compressor 1, the compressor 1 can increase the opening area of the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 while ensuring the rigidity of the first cylinder 21A with the blocking wall portion 150, thereby increasing the strength of the first cylinder 21A.

The compressor 1 also has a second throttling portion 60 in the internal suction passage 52B of the refrigerant formed in the second cylinder 21B. The second throttling portion 60 has a pair of second throttling portion side portions 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 also formed by a pair of second throttling portion side portions 60B, 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 a pair of second throttling portion side portions 60B, has a second inner opening 60C that opens to the radially inner 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. In addition, the second narrowing portion 60 has a narrowing bottom portion 60A, which is a plate-shaped second closing wall portion 151 provided to close the second narrowing portion 60, at the other end in the axial direction of the rotating shaft 40.

The second throttling portion 60 increases 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 second cylinder 21B by using the second blocking wall portion 151, thereby increasing the strength of the second cylinder 21B.

The compressor 1 ensures the rigidity of the second cylinder 21B by the second blocking wall portion 151 of the second throttling portion 60, and can increase 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, and can increase the strength of the second cylinder 21B.

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 top portion 59A, which is the blocking wall portion 150.

The radially inner end of the constriction top portion 59A, which is the blocking wall portion 150, has a through portion 63 that penetrates the first cylinder 21A in the axial direction. In the first cylinder 21A, the refrigerant that reaches the through portion 63 tends 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 portion 63, the amount of refrigerant sucked in increases due to the refrigerant passing through the through portion 63, so the refrigeration capacity of the compressor 1 is increased and the compression efficiency is improved.

In addition, when high-pressure refrigerant flows back from the outside of the first discharge passage toward the first cylinder chamber, which is now at low pressure, after the refrigerant compressed in the first cylinder chamber is discharged, if the suction passage is wide in the circumferential direction, the time that the piston blocks the suction passage will be short. In that case, the compressor is more likely to allow the backflowing high-pressure refrigerant to enter the suction passage, reducing the amount of low-pressure refrigerant suctioned into the compression mechanism from the suction pipe, which could result in reduced compression efficiency.

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 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 the time that the piston 22 blocks the intake passage 52A, thereby suppressing the backflow of refrigerant into the intake passage 52A and suppressing a decrease in compression efficiency.

The constriction bottom 60A, which is the second blocking wall 151, has a second through-hole 63B at its radially inner end that penetrates the second cylinder 21B in the axial direction. In the second cylinder 21B, the refrigerant that reaches the second through-hole 63B tends 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 when the compressor 1 does not have the second through-hole 63B, the amount of refrigerant sucked in increases due to the refrigerant passing through the second through-hole 63B, so the refrigeration capacity of the compressor 1 increases and the compression efficiency increases.

Furthermore, the second through-hole 63B of the compressor 1 does not widen the opening of the intake passage 52A in the circumferential direction, but widens 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 the time that the piston 22 blocks the intake passage 52A, thereby suppressing the backflow of refrigerant into the intake passage 52A and suppressing a decrease in compression efficiency.

The refrigeration cycle device 200 according to the first embodiment is equipped with the compressor 1 according to the first embodiment. Therefore, the refrigeration cycle device 200 can obtain the same effects as the compressor 1 according to the first embodiment.

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

The compression mechanism 20 of the second embodiment will be described using Figures 17 to 20. Note that parts having the same configuration as the compression mechanism 20 of Figures 1 to 16 are given the same reference numerals and their description will be omitted. Below, the configuration of the second embodiment that differs from the first embodiment will be mainly described, and the configuration not described in the second embodiment is the same as the first embodiment. Note that the compressor 1 has the first cylinder 21A fixed to the sealed container 10 and the second cylinder 21B not fixed to the sealed container 10.

In the compressor 1 according to the first embodiment, the intake pipe 2 is connected to the first cylinder 21A, whereas in the compressor 1 according to the second embodiment, the intake pipe 2 is connected to the second cylinder 21B. Therefore, in the compressor 1 according to the second embodiment, the structure of the first cylinder 21A and the structure of the second cylinder 21B are reversed from those of the compressor 1 according to the first embodiment. Also, in the second cylinder 21B of the compressor 1 according to the second embodiment, a branch flow path 52AA is formed which branches off from the intake flow path 52A.

The first cylinder 21A has an internal intake passage 52B that connects the lower surface of the first cylinder 21A to the first cylinder chamber 55A. The internal intake passage 52B has a communicating intake hole 62 that extends radially inward from the lower surface of the first cylinder 21A through the inside of the first cylinder 21A. The internal intake passage 52B also has a second throttling portion 60 that is formed radially inward of the communicating intake hole 62 and forms a space that connects the communicating intake hole 62 to the first cylinder chamber 55A. That is, the internal intake passage 52B has the communicating intake hole 62 and the second throttling portion 60 that is formed radially inward of the communicating intake hole 62 and connects the communicating intake hole 62 to the first cylinder chamber 55A.

The communicating suction hole 62 is a hole that extends radially inward from the underside of the first cylinder 21A through the inside of the first cylinder 21A. The communicating suction hole 62 extends axially downward from the underside of the first cylinder 21A and then extends radially inward from there. The communicating suction hole 62 is a hole that connects the outside of the first cylinder 21A with the second throttling section 60. The communicating suction hole 62 is a hole that connects the connection path 25A (see Figure 4) of the partition plate 25 with the second throttling section 60.

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

The second throttling portion 60 has a pair of second throttling portion side portions 60B that form both inner surfaces of the second throttling portion 60 and are formed to approach each other as they move radially inward of the first cylinder 21A. The second throttling portion 60 is also formed of a pair of second throttling portion side portions 60B, has a second shaft side opening 60D that opens at one end in the axial direction of the rotating shaft 40 and is blocked by a partition plate 25. The second throttling portion 60 is also formed of a pair of second throttling portion side portions 60B, has a second inner opening 60C that opens to communicate with the first cylinder chamber 55A on the radially inner side of the first cylinder 21A and is formed to communicate with the second shaft side opening 60D. The second throttling portion 60 also has a plate-shaped second blocking wall portion 151 that is provided at the other end in the axial direction of the rotating shaft 40 to block the second throttling portion 60.

The second throttling portion 60 has one end that opens into the second shaft side opening 60D in the axial direction of the rotating shaft 40, and the other end that is closed by the throttling portion top portion 160A. In the radial direction of the rotating shaft 40, the second throttling portion 60 has one end that communicates with the communicating suction hole 62, and the other end that communicates with the first cylinder chamber 55A.

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

The intake passage 52A includes an intake hole 61 extending radially inward from the outer peripheral surface 156 of the second cylinder 21B, and a throttling portion 59 formed radially inward of the intake hole 61 and connecting the intake hole 61 to the second low pressure chamber 57B. That is, the intake passage 52A includes an intake hole 61 and a throttling portion 59 formed radially inward of the intake hole 61 and connecting the intake hole 61 to the second cylinder chamber 55B.

The suction hole 61 is a hole that extends radially inward from the outer circumferential 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 throttling 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 throttling portion 59. The opening shape of the suction hole 61, which is the entrance to the suction flow passage 52A, may be any shape that matches the shape of the suction pipe 2.

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

The constriction portion 59 has one end opened by the shaft side opening 59D in the axial direction of the rotating shaft 40, and the other end closed by the constriction portion bottom 159A. The constriction portion bottom 159A contributes to improving the rigidity of the second cylinder 21B regardless of which side of the axial end face it is provided on, but from the standpoint of workability and rigidity improvement, it is preferable to provide it on the side opposite the side on which the branch flow path 52AA is formed.

The throttling portion 59 has one end communicating with the suction hole 61 in the radial direction of the rotating shaft 40, and the other end communicating with the second cylinder chamber 55B. In the compressor 1 of embodiment 2, the throttling portion bottom 159A forms the blocking wall portion 150 of the throttling portion 59.

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

The partition plate 25 is formed with a connection path 25A that communicates with a branch flow path 52AA branching off from the intake flow path 52A of the second cylinder 21B. The connection path 25A also communicates with an internal intake flow path 52B formed in the first cylinder 21A. The connection path 25A connects the branch flow path 52AA of the second cylinder 21B to the internal intake flow path 52B of the first cylinder 21A. The connection path 25A connects the internal intake flow path 52B of the first cylinder 21A to the intake flow path 52A of the second cylinder 21B.

FIG. 21 is a partial enlarged view of the internal intake passage 52B of a modified example of the compressor 1 according to embodiment 2. FIG. 22 is a partial enlarged view of the 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 the first cylinder 21A in the axial direction. Also, as shown in FIG. 22, the radially inner end of the constriction bottom portion 159A may form a through portion 63 that penetrates the second cylinder 21B in the axial direction.

The constriction top portion 160A, which is the second blocking wall portion 151, has a second through portion 63B at its radially inner end 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. The second through portion 63B is covered and blocked by the plate surface of the upper bearing 24A in the compression mechanism 20.

The constriction bottom 159A, which is the blocking wall 150, has a through-hole 63 at its radially inward end 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. The through-hole 63 is covered and blocked by the plate surface of the lower bearing 24B in the compression mechanism 20.

The refrigerant flowing in from the suction pipe 2 connected to the second cylinder 21B flows through the suction passage 52A 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 passage 53B.

Similarly, the refrigerant flowing in from the suction pipe 2 connected to the second cylinder 21B flows into the first high-pressure chamber 58A through the connection path 25A of the partition plate 25 and the internal suction passage 52B of the first cylinder 21A. The refrigerant that flows 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.

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

In addition, the second high-pressure chamber 58B repeatedly draws in, compresses, and exhausts the refrigerant, and when the refrigerant is exhausted, the high-pressure refrigerant inside 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 intake passage 52A, reducing the amount of refrigerant sucked in from the intake pipe 2 and decreasing the compressor efficiency. Therefore, in order to prevent the refrigerant from flowing back into the second high-pressure chamber 58B when the refrigerant is exhausted, it is preferable that the inner opening 59C, which is the connection between the intake passage 52A and the second cylinder chamber 55B, is close to the second vane groove 56B.

In view of the above, it is desirable for the compressor 1 to expand the intake passage 52A in the axial direction of the second cylinder 21B in order to improve the compressor efficiency. Also, in order to improve the compressor efficiency of the compressor 1, it is effective to provide a constriction 59 at the end of the inner circumference side of the intake passage 52A and connect the intake passage 52A to the second cylinder chamber 55B at a position close to the second vane 50B.

On the other hand, when the suction hole 61 is enlarged and when the suction hole 61 is brought closer to the second vane groove 56B, the thickness of the wall between the suction hole 61 of the second cylinder 21B and the second vane groove 56B of the compressor 1 becomes thinner. In such a case, the compressor 1 may increase the risk of distortion of the second cylinder 21B due to external forces such as the pressure of the suction pipe 2 being pressed into the second cylinder 21B. In addition, the compressor 1 may increase the risk of distortion of the second cylinder 21B due to external forces such as the pressing force of the second vane 50B against the second cylinder 21B caused by the pressure difference between the second low pressure chamber 57B and the second high pressure chamber 58B.

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

Similar to the intake passage 52A, the internal intake passage 52B is formed in a shape in which the second throttling portion 60 penetrates only one axial side of the first cylinder 21A, and the other side is walled by the throttling top portion 160A. The compressor 1 ensures the rigidity of the first cylinder 21A by the throttling top portion 160A, and the second throttling portion 60 can expand the internal intake passage 52B in the axial direction while bringing the second inner opening 60C, which is the connection part with the first cylinder chamber 55A, closer to the first vane groove 56A.

[Function and effect of compressor 1]
The compressor 1 has a throttling portion 59 in the refrigerant intake passage 52A formed in the second cylinder 21B. The throttling portion 59 has a pair of throttling portion side portions 59B that form both inner surfaces of the throttling portion 59 and are formed so as to approach each other as they move radially inward of the second cylinder 21B. The throttling portion 59 is also formed of the pair of throttling portion side portions 59B and has a shaft side opening 59D that opens at one end in the axial direction of the rotating shaft 40. The throttling portion 59 is also formed of the pair of throttling portion side portions 59B and has an inner opening 59C 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 shaft side opening 59D. The throttling portion 59 also has a throttling portion bottom portion 159A that 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 block the throttling 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 the shaft side opening 59D and the inner opening 59C, while ensuring the rigidity of the second cylinder 21B by the blocking wall portion 150, thereby increasing the strength of the second cylinder 21B.

The compressor 1 ensures the rigidity of the second cylinder 21B by the blocking wall portion 150 of the constriction portion 59, and can increase 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, and can increase the strength of the second cylinder 21B.

The compressor 1 ensures the rigidity of the second cylinder 21B by the blocking wall portion 150 of the narrowing portion 59, and can increase the strength of the second cylinder 21B. Therefore, the compressor 1 can suppress deformation of the second cylinder 21B even when the intake pipe 2 is inserted into the intake passage 52A of the second cylinder 21B while shaking it.

If blocking walls 150 are provided at both ends of the throttling portion 59 in the axial direction of the rotating shaft 40, the opening area and volume of the throttling portion 59 become smaller, so the compressor 1 experiences greater pressure loss and the refrigerant is less likely to enter the first cylinder chamber 55A. The compressor 1 has a shaft side opening 59D at one end of the throttling portion 59 in the axial direction of the rotating shaft 40, and a blocking wall 150 at the other end. Therefore, the compressor 1 can expand 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, while ensuring the rigidity of the second cylinder 21B by using the blocking wall 150, thereby increasing the strength of the second cylinder 21B.

The second cylinder 21B is formed with an intake passage 52A and a branch passage 52AA branching off from the intake passage 52A. The first cylinder 21A is formed with an internal intake passage 52B that connects the underside of the first cylinder 21A to the first cylinder chamber 55A, 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 if a two-cylinder rotary compressor is used for the compressor 1, the compressor 1 can increase the opening area of the passage through which the refrigerant passes in the axial direction of the rotating shaft 40 while ensuring the rigidity of the second cylinder 21B with the blocking wall portion 150, thereby increasing the strength of the second cylinder 21B.

The compressor 1 also has a second throttling portion 60 in the internal suction passage 52B of the refrigerant formed in the first cylinder 21A. The second throttling portion 60 has a pair of second throttling portion side portions 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 also formed by a pair of second throttling portion side portions 60B, 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 a pair of second throttling portion side portions 60B, has a second inner opening 60C that opens to the radially inner 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. In addition, the second narrowing portion 60 has a narrowing portion top portion 160A, which is a plate-shaped second closing wall portion 151 provided to close the second narrowing portion 60, at the other end in the axial direction of the rotating shaft 40.

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 means of the second shaft side opening 60D and the second inner opening 60C, while ensuring the rigidity of the first cylinder 21A by means of the second blocking wall portion 151, thereby increasing the strength of the first cylinder 21A.

The compressor 1 ensures the rigidity of the first cylinder 21A by the second blocking wall portion 151 of the second throttling portion 60, and can increase 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, and can increase the strength of the first cylinder 21A.

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 has the restrictor bottom 60A, which is the blocking wall 150, in the restrictor 59, so deformation of the second cylinder 21B can be suppressed.

The diametrically 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 tends 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 amount of refrigerant sucked in increases due to the refrigerant passing through the through-hole 63, so the refrigeration capacity of the compressor 1 is increased and the compression efficiency is improved.

In addition, when high-pressure refrigerant flows into the low-pressure second cylinder chamber from the outside of the second discharge passage after the refrigerant compressed in the second cylinder chamber is discharged, if the suction passage is wide in the circumferential direction, the time that the piston blocks the suction passage will be short. In that case, the compressor is more likely to allow high-pressure refrigerant that has flowed back into the suction passage to flow in, reducing the amount of low-pressure refrigerant suctioned into the compression mechanism from the suction pipe, which may result in reduced compression efficiency.

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 first cylinder 21A, the refrigerant that reaches the second through portion 63B tends 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 when the compressor 1 does not have the second through portion 63B, the amount of refrigerant sucked in increases due to the refrigerant passing through the second through portion 63B, so the refrigeration capacity of the compressor 1 is increased and the compression efficiency is improved.

Furthermore, the first cylinder 21A of the compressor 1 is fixed to the sealed container 10. For example, as described above, the first cylinder 21A of the compressor 1 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.

The compressor 1 has the intake pipe 2 connected to the second cylinder 21B, which is not connected to the sealed container 10. When the intake pipe 2 of the compressor 1 is connected to the sealed container 10, distortion may occur in the second cylinder 21B.

The compressor 1 joins the suction pipe 2 to the second cylinder 21B and fixes the first cylinder 21A to the sealed container 10. By having this configuration, the compressor 1 reduces the amount of distortion of the first cylinder 21A and increases the amount of distortion of the second cylinder 21B 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.

Compared to fixing the first cylinder 21A to the sealed container 10 and joining the suction pipe 2 to the first cylinder 21A, the compressor 1 can eliminate the imbalance in distortion between the first cylinder 21A and the second cylinder 21B that occurs when distortion due to assembly is biased toward the first cylinder 21A. Therefore, the compressor 1 can unify the target values of the machining dimensions of the first cylinder 21A and the second cylinder 21B, taking into account the distortion due to assembly.

At the same time, by changing 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 due to welding or the like when it is fixed to the sealed container 10. By reducing the number of assembly steps that were biased toward the first cylinder 21A, the compressor 1 can reduce the variation in distortion during assembly of the first cylinder 21A and reduce the clearance for the engagement between 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 and improve compressor efficiency.

The refrigeration cycle device 200 according to the second embodiment is equipped with the compressor 1 according to the second embodiment. Therefore, the refrigeration cycle device 200 can obtain the same effects as the compressor 1 according to the second embodiment.

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

The compression mechanism 20 of embodiment 3 will be described using Figures 23 to 26. Note that parts having the same configuration as the compression mechanism 20 of Figures 1 to 22 are given the same reference numerals and their description will be omitted. The following description will focus on the configuration of embodiment 3 that differs from embodiments 1 and 2, and the configuration not described in embodiment 3 is the same as embodiment 1 or 2.

The compressor 1 in the first and second embodiments is a two-cylinder rotary compressor, whereas the compressor 1 in the third embodiment is a one-cylinder rotary compressor. The compressor 1 in the third embodiment has a first cylinder 21A in the compression mechanism 20.

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.

The upper bearing 24A is positioned so that it abuts against the upper end surface of the first cylinder 21A, and closes the first cylinder chamber 55A. The lower bearing 24B is positioned so that it abuts against the lower end surface of the first cylinder 21A, and closes the first cylinder chamber 55A.

The first cylinder 21A is formed with an intake passage 52A that connects the outside of the first cylinder 21A to the first cylinder chamber 55A. The intake passage 52A extends radially inward from the outer 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 constriction 59 formed radially inward of the intake hole 61 and forming a space that connects the intake hole 61 to the first cylinder chamber 55A.

The compressor 1 has an intake passage 52A that connects 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 throttling portion 59 that is formed radially inward of the intake hole 61 and connects the intake hole 61 to the first low pressure chamber 57A. That is, the intake passage 52A includes an intake hole 61 and a throttling portion 59 that is formed radially inward of the intake hole 61 and connects the intake hole 61 to the first cylinder chamber 55A.

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

The throttling portion 59 opens to the outer surface of the first cylinder 21A on the lower side and radially inward side, has a throttling portion top portion 59A on the upper side, and has throttling portion side portions 59B that approach each other as the inner surfaces move radially inward. That is, the throttling 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 throttling portion top portion 59A on the upper bearing 24A side. The throttling portion 59 has throttling portion side portions 59B that face each other in the circumferential direction. The throttling portion side portions 59B are formed so as to approach each other as they move from the radially outward to the radially inward. In the compressor 1 of embodiment 3, the throttling portion top portion 59A forms the blocking wall portion 150 of the throttling portion 59.

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

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

FIG. 27 is a perspective view of the first cylinder 21A of a modified example of the compressor 1 according to the third embodiment. FIG. 28 is a partially enlarged view of the intake passage 52A of a modified example of the compressor 1 according to the third embodiment. 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.

[Function and effect of compressor 1]
The compressor 1 has a throttling portion 59 in the refrigerant intake passage 52A formed in the first cylinder 21A. The throttling portion 59 has a pair of throttling portion side portions 59B that form both inner surfaces of the throttling portion 59 and are formed so as to approach each other as they move radially inward of the first cylinder 21A. The throttling portion 59 is also formed of the pair of throttling portion side portions 59B and has a shaft side opening 59D that opens at one end in the axial direction of the rotating shaft 40. The throttling portion 59 is also formed of the pair of throttling portion side portions 59B and has an inner opening 59C that opens to 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 throttling portion 59 also has a throttling portion top portion 59A that is a plate-shaped blocking wall portion 150 provided to block the throttling portion 59 at the other end in the axial direction of the rotating shaft 40. 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 the shaft side opening 59D and the inner opening 59C, while ensuring the rigidity of the first cylinder 21A by the blocking wall portion 150, thereby increasing the strength of the first cylinder 21A.

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 portion 150 is provided to abut against the upper bearing 24A. In the compressor 1, the shaft side opening 59D expands 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.

In addition, when high-pressure refrigerant flows into the low-pressure first cylinder chamber from the outside of the first discharge passage after the refrigerant compressed in the first cylinder chamber is discharged, if the suction passage is wide in the circumferential direction, the time that the piston blocks the suction passage will be short. In that case, the compressor is more likely to allow high-pressure refrigerant that has flowed back into the suction passage to flow in, reducing the amount of low-pressure refrigerant suctioned into the compression mechanism from the suction pipe, which may result in reduced compression efficiency.

The refrigeration cycle device 200 according to the third embodiment is equipped with the compressor 1 according to the third embodiment. Therefore, the refrigeration cycle device 200 can obtain the same effects as the compressor 1 according to the third embodiment.

Embodiment 4.
Fig. 29 is a schematic vertical cross-sectional view showing the overall configuration of a compressor 1 according to embodiment 4. Fig. 30 is a schematic partial vertical cross-sectional view of a compression mechanism 20 according to embodiment 4. The compression mechanism 20 according to embodiment 4 will be described with reference to 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 embodiment 4 that differs from embodiment 3, and the configuration not described in embodiment 4 is the same as embodiments 1 to 3.

The compressor 1 of embodiment 4 differs from the compressor 1 of embodiment 3 in the structure of the throttling portion 59. The throttling portion 59 in the compressor 1 of embodiment 3 has a throttling portion top portion 59A, whereas the throttling portion 59 in the compressor 1 of embodiment 4 has a throttling portion bottom portion 59A1.

The throttling portion 59 in the fourth embodiment opens to the outer surface of the first cylinder 21A on the upper side and radially inner side, has a throttling portion bottom 59A1 on the lower side, and has throttling portion side portions 59B that approach each other as both inner surfaces move radially inward. That is, the throttling 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 throttling portion bottom 59A1 on the lower bearing 24B side. In the compressor 1 in the third embodiment, the throttling portion bottom 59A1 forms the blocking wall portion 150 of the throttling portion 59.

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

In the compressor 1 of the fourth embodiment, the upper bearing 24A closes the upper end surface of the first cylinder 21A, and the lower bearing 24B closes the lower end surface of the first cylinder 21A. In the compressor 1 of the fourth embodiment, the shaft side opening 59D is closed by the upper bearing 24A, and the narrowing portion bottom 59A1, which is the closing wall portion 150, is arranged to abut against the lower bearing 24B.

In the axial direction of the rotating shaft 40, the constricted portion 59 has one end that opens into the shaft side opening 59D and the other end that is closed by the constricted portion bottom 59A1. In the radial direction of the rotating shaft 40, the constricted portion 59 has one end that communicates with the suction hole 61 and the other end that communicates with the first cylinder chamber 55A. The constricted portion bottom 59A1 may have a radially inner end that forms a through portion 63 that penetrates the first cylinder 21A in the axial direction.

[Function and effect of compressor 1]
The compressor 1 has a throttling portion 59 in the refrigerant intake passage 52A formed in the first cylinder 21A. The throttling portion 59 has a pair of throttling portion side portions 59B that form both inner surfaces of the throttling portion 59 and are formed so as to approach each other as they move radially inward of the first cylinder 21A. The throttling portion 59 is also formed of the pair of throttling portion side portions 59B and has a shaft side opening 59D that opens at one end in the axial direction of the rotating shaft 40. The throttling portion 59 is also formed of the pair of throttling portion side portions 59B and has an inner opening 59C that opens to 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 throttling portion 59 also has a throttling portion bottom portion 59A1 that 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 block the throttling 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 the shaft side opening 59D and the inner opening 59C, while ensuring the rigidity of the first cylinder 21A by the blocking wall portion 150, thereby increasing the strength of the first cylinder 21A.

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 portion 150 is provided to abut against the lower bearing 24B. In the compressor 1, the shaft side opening 59D expands 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.

The refrigeration cycle device 200 according to the fourth embodiment is equipped with the compressor 1 according to the fourth embodiment. Therefore, the refrigeration cycle device 200 can obtain the same effects as the compressor 1 according to the fourth embodiment.

The configurations shown in the above embodiments are merely examples, and may be combined with other known technologies, and parts of the configurations 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. Also, while the number of cylinders 21 is one or two in the embodiments, it may be three or more.

1 compressor, 2 suction pipe, 3 suction muffler, 4 discharge pipe, 6 refrigeration 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, 4 0 Rotating shaft, 40A First eccentric shaft portion, 40B Second eccentric shaft portion, 41 End portion, 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, 55 B 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 constricted portion, 59A top of constricted portion, 59A1 bottom of constricted portion, 59B side portion of constricted portion, 59B1 side portion of constricted portion, 59B2 side portion of constricted portion, 59C inner opening, 59D shaft side opening, 60 second constricted portion, 60A bottom of constricted portion, 60B side portion of second constricted portion, 60B1 side portion of second constricted portion, 60B2 side of second constricted portion Surface portion, 60C second inner opening, 60D second shaft side opening, 61 suction hole, 62 connecting suction hole, 63 penetration portion, 63B second penetration portion, 122 outer peripheral wall, 150 blocking wall portion, 151 second blocking wall portion, 155 inner peripheral wall, 155A intermediate wall portion, 155B intermediate wall portion, 156 outer peripheral surface, 159A bottom of constriction portion, 160A top of constriction 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

A sealed container;
a rotating electric machine disposed in the sealed container;
a rotating shaft that is disposed in the sealed container and is rotated by the rotating electric machine;
a compression mechanism that is disposed in the sealed container and compresses a refrigerant by a driving force transmitted from the rotating electric machine via the rotating shaft;
a suction pipe that penetrates the sealed container and is connected to the compression mechanism and 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 that is fitted to the rotary shaft and accommodated in the cylinder chamber and rotates eccentrically in association 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 dividing 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;
having
The cylinder includes:
An intake passage is formed to communicate the outside of the cylinder with the cylinder chamber,
The intake passage is
a suction hole extending radially inward from an outer circumferential surface of the cylinder, the suction pipe being connected to the outer circumferential surface;
a throttle portion formed radially inward of the suction hole and defining a space that communicates between the suction hole and the cylinder chamber;
having
The narrowed portion is
a pair of narrowed portion side portions that constitute both inner surfaces of the narrowed portion and are formed so as to approach each other as they move radially inward of the cylinder;
a shaft side opening portion formed by the pair of tapered portion side portions and opening at one end portion in the axial direction of the rotating shaft;
an inner opening formed by the pair of tapered portion side surfaces, the inner opening being open radially inwardly to communicate with the cylinder chamber and connected to the shaft side opening;
a plate-shaped blocking wall portion provided at the other end of the rotating shaft in the axial direction so as to block the tapered portion;
A compressor having
The at least one cylinder comprises:
a 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 is closed by a first recess,
The lower bearing is
a second cylinder chamber is closed by the second piston.
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 includes:
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 connection path that connects the branch passage and the internal suction passage.
The internal intake passage is
a communicating suction hole extending radially inward from an upper surface of the second cylinder through an interior of the second cylinder;
a second throttle portion that is formed radially inward of the communicating suction hole and defines a space that communicates between the communicating suction hole and the second cylinder chamber;
Equipped with
The second narrowing portion is
a pair of second reduced portion side portions that constitute both inner surfaces of the second reduced portion and are formed so as to approach each other toward the inside in the radial direction of the second cylinder;
a second shaft side opening portion formed by the pair of second tapered portion side portions, opening at one end portion in the axial direction of the rotating shaft, and closed by the partition plate;
a second inner opening formed by the pair of second tapered portion side surfaces, opening toward a radially inner side 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 portion in the axial direction of the rotating shaft so as to close the second narrowed portion;
3. The compressor of claim 2, further comprising:
The at least one cylinder comprises:
A cylindrical first cylinder that is fixed to the sealed container and forms 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 is closed by a first recess,
The lower bearing is
a second cylinder chamber is closed by the second piston.
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 includes:
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 connection path that connects the branch passage and the internal suction passage.
The internal intake passage is
a communicating suction hole extending radially inward from a lower surface of the first cylinder through an interior of the first cylinder;
a second throttle portion that is formed radially inward of the communicating suction hole and defines a space that communicates between the communicating suction hole and the first cylinder chamber;
Equipped with
The second narrowing portion is
a pair of second reduced portion side portions that constitute both inner surfaces of the second reduced portion and are formed so as to approach each other as they proceed radially inward of the first cylinder;
a second shaft side opening portion formed by the pair of second tapered portion side portions, opening at one end portion in the axial direction of the rotating shaft, and closed by the partition plate;
a second inner opening formed by the pair of second throttle portion side surfaces, opening toward a radially inner side 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 portion in the axial direction of the rotating shaft so as to close the second narrowed portion;
5. The compressor according to claim 4, further comprising:
The upper bearing closes the upper end surface of the cylinder,
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.
The upper bearing closes the upper end surface of the cylinder,
The lower bearing is
The lower end surface of the cylinder is closed,
The shaft side opening is
The upper bearing is closed,
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.
The compressor according to any one of claims 1 to 7, in which the suction pipe is press-fitted into the suction passage.
The compressor according to any one of claims 1 to 8, wherein the blocking wall has a through-hole at its radially inner end that penetrates the cylinder in the axial direction.
The compressor according to claim 3 or 5, wherein the second blocking wall portion has a second through-portion at its radially inner end that penetrates the cylinder in the axial direction.
A compressor according to any one of claims 1 to 10;
an outdoor heat exchanger for exchanging 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 for exchanging heat between indoor air and the refrigerant flowing therein;
A refrigeration cycle device comprising: