Compressor and refrigeration cycle device

Abstract

This compressor comprises, inside a sealed container, an electric motor unit, a rotation shaft, and a compression mechanism unit for compressing refrigerant. The compression mechanism unit includes a cylindrical cylinder forming a cylinder chamber, a rolling piston, a vane, and a bearing closing the cylinder chamber. In the cylinder, a suction hole is formed extending in a radial direction of the cylinder, through which the refrigerant to be suctioned into the cylinder chamber passes. The suction hole has a suction-hole outer-diameter connection part forming a space positioned on the radially outer peripheral side of the cylinder, and a suction-hole inner-diameter connection part forming a space positioned on the radially inner peripheral side of the cylinder. The cross-sectional area of the suction-hole outer-diameter connection part in a cross section orthogonal to the radial direction of the cylinder is made larger than the cross-sectional area of the suction-hole inner-diameter connection part in the cross section orthogonal to the radial direction of the cylinder. The cross-sectional shape of the suction-hole inner-diameter connection part in the cross section orthogonal to the radial direction of the cylinder is a shape with an opening width in a circumferential direction of the cylinder smaller than an opening width thereof in a thickness direction of the cylinder.

Description

[Technical field]

[0001] The present disclosure relates to a compressor that compresses and discharges a refrigerant and a refrigeration cycle device including the compressor, and in particular to a suction mechanism that forms a refrigerant path to a compression chamber. [Background technology]

[0002] A conventional rotary compressor includes a compression mechanism having a rotating shaft with an eccentric portion, a cylindrical cylinder provided on the outer periphery of the eccentric portion, a piston that rotates following the eccentric portion and forms a compression chamber between the piston and the cylinder, and upper and lower bearings that support both ends of the cylinder (see, for example, Patent Document 1). In recent years, low GWP (Global Warming Potential) refrigerants have been used as refrigerants for refrigeration cycle devices equipped with compressors such as rotary compressors as one of the measures against global warming. However, low GWP refrigerants such as R32, R1234yf, or R290 have a smaller refrigeration capacity per volume than conventionally used refrigerants such as R410A, and the flow rate of the refrigerant flowing in the refrigeration cycle device is increased to achieve the desired refrigeration capacity. Therefore, in order to improve the efficiency of the compressor, it is particularly effective to increase the flow path area of ​​the suction hole of the cylinder, which is the refrigerant suction path to the compression mechanism, and reduce the pressure loss in the suction path. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2013-139726 A Summary of the Invention [Problem to be solved by the invention]

[0004] In a rotary compressor, the pressure loss of the suction refrigerant is reduced by expanding the diameter of the suction hole of the cylinder. However, a screw hole and a spring hole are generally formed around the suction hole of the cylinder of a rotary compressor. The screw hole is a hole for arranging a screw for fastening the components constituting the compression mechanism, and the spring hole is a hole for arranging a spring for operating a vane separating a high pressure chamber and a low pressure chamber in the compression mechanism. Interference between the suction hole and the screw hole or between the suction hole and the spring hole restricts the expansion of the suction hole, making it difficult to secure a sufficient flow passage area of ​​the suction hole, which may reduce the efficiency of the compressor under operating conditions using a high flow rate refrigerant.

[0005] The present disclosure is devised to solve the above-mentioned problems, and provides a compressor and a refrigeration cycle device that prevent a decrease in compressor efficiency even under operating conditions using a high flow rate refrigerant. [Means for solving the problem]

[0006] The compressor according to the present disclosure includes, inside a sealed container, an electric motor unit, a rotating shaft having an eccentric shaft unit and driven to rotate by the electric motor unit, and a compression mechanism unit that compresses a refrigerant by driving force transmitted from the electric motor unit via the rotating shaft. The compression mechanism unit includes a cylindrical cylinder that is fixed to the sealed container and forms a cylinder chamber in a hollow portion, a rolling piston that is fitted to the eccentric shaft unit and stored in the cylinder chamber and rotates eccentrically together with the eccentric shaft unit to compress the refrigerant, a vane that is provided in a vane groove formed to extend radially of the cylinder and separates the cylinder chamber into a suction chamber and a compression chamber, and a piston that is provided on an end surface of the cylinder and closes the cylinder chamber. and a bearing for supporting the refrigerant in the cylinder chamber, the cylinder having a suction hole extending in the radial direction of the cylinder through which the refrigerant to be suctioned into the cylinder chamber passes, the suction hole having a suction hole outer diameter connection portion forming a space located on the radial outer periphery side of the cylinder and a suction hole inner diameter connection portion forming a space located on the radial inner periphery side of the cylinder, the cross-sectional area of ​​the suction hole outer diameter connection portion in a cross section perpendicular to the radial direction of the cylinder is larger than the cross-sectional area of ​​the suction hole inner diameter connection portion in a cross section perpendicular to the radial direction of the cylinder, and the cross-sectional shape of the suction hole inner diameter connection portion in the cross section perpendicular to the radial direction of the cylinder is such that an opening width in the circumferential direction of the cylinder is S The cylinder has a shape smaller than the opening width in the thickness direction of the cylinder, and the cylinder has an intake groove formed therein that penetrates the wall of the cylinder between the intake hole inner diameter connection part and at least one of the end faces of the cylinder in the thickness direction of the cylinder, and the intake groove is formed so as to open to the radially inner side of the cylinder from the intake hole inner diameter connection part in the thickness direction of the cylinder to the end face of the cylinder. The cylinder further has a plurality of screws fastening the bearing and the cylinder, the cylinder has a plurality of screw holes penetrating the cylinder in a thickness direction thereof and in which the plurality of screws are respectively arranged, the cylinder has a first thin-walled portion constituting a part of the wall of the cylinder between the suction hole outer diameter connection portion and an end face of the cylinder in the thickness direction thereof, and a second thin-walled portion which is a part of the wall constituting the cylinder and is a portion where the distance between the suction hole inner diameter connection portion and the screw hole among the plurality of screw holes that is located closest to the suction hole inner diameter connection portion in the circumferential direction of the cylinder is smallest, and the thickness t1 of the first thin-walled portion in the thickness direction of the cylinder is The vane further includes a spring that biases the vane so as to press the tip of the vane against the outer circumferential wall of the rolling piston, and the cylinder is formed with a spring hole for arranging the spring so as to extend in the radial direction of the cylinder. The cylinder further includes a third thin-walled portion that is a part of the wall constituting the cylinder and is a portion where the distance between the suction hole inner diameter connection portion and the spring hole is smallest in the circumferential direction of the cylinder, and the thickness t1 of the first thin-walled portion is formed to be larger than the thickness t3 of the third thin-walled portion in the circumferential direction of the cylinder. It is something.

[0007] The refrigeration cycle device according to the present disclosure includes a compressor according to the present disclosure, an outdoor heat exchanger that performs heat exchange between outdoor air and the refrigerant flowing inside, an indoor heat exchanger that performs heat exchange between indoor air and the refrigerant flowing inside, and a pressure reducing device that reduces the pressure of the refrigerant flowing into the outdoor heat exchanger or the indoor heat exchanger. Effect of the Invention

[0008] According to the compressor and refrigeration cycle device of the present disclosure, the cross-sectional area of ​​the suction hole outer diameter connection part is formed larger than the cross-sectional area of ​​the suction hole inner diameter connection part. Therefore, the compressor can increase the flow path area of ​​the refrigerant in the suction hole as a whole without expanding the radial inner circumferential side of the suction hole in the circumferential direction of the cylinder, and reduce the pressure loss of the refrigerant flow. In addition, the cross-sectional shape of the suction hole inner diameter connection part is a shape in which the opening width in the circumferential direction of the cylinder is smaller than the opening width in the thickness direction of the cylinder. Therefore, the compressor can set the angle at which the rolling piston completes blocking of the suction hole earlier from the start of rotation compared to a compressor that does not have the suction hole, and can improve the volumetric efficiency of the compressor compared to a compressor that does not have the suction hole. By having a suction hole with such a structure, the compressor can prevent a decrease in the efficiency of the compressor even under operating conditions using a high flow rate refrigerant. [Brief description of the drawings]

[0009] [Figure 1] 1 is a vertical sectional view of a compressor according to a first embodiment. [Diagram 2] 1 is a cross-sectional view that shows a schematic cross section of a compression mechanism of a compressor according to a first embodiment. [Diagram 3] 2 is a configuration diagram showing a schematic structure of a cylinder in a compression mechanism of the compressor according to the first embodiment. FIG. [Figure 4] 3 is a conceptual diagram of a vane groove and a spring hole as viewed in a circumferential direction of a cylinder of the compression mechanism part according to the first embodiment. FIG. [Diagram 5] 3 is a conceptual diagram of a vane groove and a spring hole as viewed in a radial direction of a cylinder of the compression mechanism part according to the first embodiment. FIG. [Figure 6] 2 is a side view showing a schematic structure of a suction hole in the compression mechanism of the compressor according to the first embodiment. FIG. [Figure 7] 2 is a vertical cross-sectional view that shows a schematic structure of a suction hole portion in a compression mechanism of the compressor according to the first embodiment. FIG. [Figure 8] 2 is a partial cross-sectional view showing, in outline, the structures of a suction hole, a threaded hole, and a spring hole in a cylinder of the compressor according to the first embodiment. FIG. [Figure 9] 1 is a configuration diagram of a refrigeration cycle device including a compressor according to a first embodiment. [Figure 10] 10 is a configuration diagram showing a schematic structure of a cylinder in a compression mechanism of a compressor according to a second embodiment. FIG. [Figure 11] 10 is a partial cross-sectional view showing, in outline, the structures of a suction hole, a threaded hole, and a spring hole in a cylinder of a compressor according to a second embodiment. FIG. [Figure 12] 11 is a vertical cross-sectional view that shows a schematic structure of a suction hole portion in a compression mechanism of a compressor according to embodiment 3. FIG. [Figure 13] 13 is a vertical cross-sectional view that shows a schematic structure of a suction hole portion in a compression mechanism of a compressor according to embodiment 4. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0010] Hereinafter, a compressor and a refrigeration cycle device according to an embodiment will be described with reference to the drawings. In the following drawings including FIG. 1, the relative dimensional relationship and shape of each component may differ from the actual ones. In the following drawings, the same reference numerals are used to denote the same or equivalent parts, and this is common throughout the entire specification. In addition, to facilitate understanding, terms indicating directions (e.g., "upper", "lower", "right", "left", "front", "rear", etc.) are used as appropriate, but these notations are written in this way only for the convenience of explanation and do not limit the arrangement and orientation of the device or parts.

[0011] Embodiment 1 [Configuration of Compressor 100] Fig. 1 is a vertical cross-sectional view of a compressor 100 according to the first embodiment. The overall configuration of the compressor 100 will be described with reference to Fig. 1. The compressor 100 is a fluid machine that draws a low-temperature, low-pressure refrigerant into the compressor 100, compresses the drawn refrigerant inside the compressor 100, and discharges a high-temperature, high-pressure refrigerant to the outside of the compressor 100.

[0012] The compressor 100 may be, for example, a one-cylinder type rotary compressor having one cylinder 23 as shown in FIG. 1, that is, a single rotary compressor. The compressor 100 is not limited to a single rotary compressor, and may be a rotary compressor having a plurality of cylinders 23. The compressor 100 may be, for example, a twin rotary compressor having two cylinders 23 or other configurations. In particular, in a compressor that flows a refrigerant at a high flow rate, it is necessary to effectively reduce the pressure loss in the suction path of the refrigerant. Therefore, the compressor 100 may be a twin rotary compressor or the like that is required to have a high flow rate and high capacity.

[0013] (Sealed container 10) The compressor 100 is a hermetic compressor that forms a hermetic space inside a hermetic container 10. The hermetic container 10 is composed of an upper container 11 and a lower container 12, and constitutes the outer shell of the compressor 100. Note that the hermetic container 10 is not limited to being formed from two components, the upper container 11 and the lower container 12, and may be formed from three or more components.

[0014] A suction muffler 101 is provided on the outside of the sealed container 10 to prevent the liquid refrigerant from being directly sucked into the cylinder chamber 23a of the cylinder 23. The suction muffler 101 is connected to the cylinder 23 of the compression mechanism 20 by a refrigerant suction pipe 107. The sealed container 10 is connected to the suction muffler 101 via the refrigerant suction pipe 107, and refrigerant gas is taken in from the suction muffler 101. The suction muffler 101 serves as an accumulator that stores the liquid refrigerant. In general, a compressor may receive a mixture of low-pressure refrigerant gas and liquid refrigerant from an external refrigerant circuit to which the compressor is connected. If the liquid refrigerant flows into the cylinder of the compression mechanism and is compressed by the compression mechanism, it may cause the compression mechanism to break down.

[0015] A suction muffler 101 is provided next to the sealed container 10 to separate the refrigerant into liquid refrigerant and gas refrigerant and to prevent the liquid refrigerant from being drawn into the compression mechanism 20 as much as possible, i.e., to send only refrigerant gas to the cylinder chamber 23a. The suction muffler 101 is connected via a refrigerant suction pipe 107 and the suction hole 40 of the cylinder 23 (see FIG. 3), and low-pressure refrigerant gas sent from the suction muffler 101 is drawn into the cylinder chamber 23a via the refrigerant suction pipe 107. The suction muffler 101 also functions as a silencer to reduce or eliminate noise generated by the inflowing refrigerant.

[0016] A discharge pipe 102 through which compressed refrigerant is discharged is connected to the top of the sealed container 10. The discharge pipe 102 is a refrigerant piping that discharges high-pressure gas refrigerant to the outside of the sealed container 10. The discharge pipe 102 is fixed to the upper container 11 in a state where it penetrates the upper container 11 that constitutes the sealed container 10. The fixed portion between the discharge pipe 102 and the upper container 11 is joined by, for example, brazing or resistance welding.

[0017] The compressor 100 includes, inside the sealed container 10, an electric motor unit 30, a rotating shaft 21 having an eccentric shaft unit 21b and driven to rotate by the electric motor unit 30, and a compression mechanism unit 20 that compresses the refrigerant by eccentric rotational motion at the eccentric shaft unit by driving force transmitted from the electric motor unit 30 via the rotating shaft 21. Within the sealed container 10, the electric motor unit 30 is housed above the sealed container 10, and the compression mechanism unit 20 is housed below the sealed container 10.

[0018] The electric motor unit 30 and the compression mechanism unit 20 are connected by a rotating shaft 21. The rotating shaft 21 transmits the rotational motion of the electric motor unit 30 to the compression mechanism unit 20. In the compression mechanism unit 20, the refrigerant gas is compressed by the transmitted rotational force, and the compressed refrigerant gas is discharged into the sealed container 10.

[0019] The inside of the sealed container 10 is filled with high-temperature, high-pressure refrigerant gas compressed by the compression mechanism section 20, and refrigeration oil used to lubricate the compression mechanism section 20 is stored below, i.e., at the bottom of the sealed container 10. The refrigeration oil is mainly used to lubricate the sliding parts of the compression mechanism section 20. An oil pump (not shown) is provided below the rotating shaft 21. As the rotating shaft 21 rotates, the oil pump pumps up the refrigeration oil stored at the bottom of the sealed container 10 and supplies it to each sliding part of the compression mechanism section 20. The compression mechanism section 20 ensures mechanical lubrication by supplying oil to each sliding part.

[0020] (Electric motor part 30) The electric motor unit 30 is an electric motor disposed inside the sealed container 10, and is used to drive the compression mechanism unit 20. The electric motor unit 30 is a motor that generates a rotational driving force in the rotating shaft 21 by using power supplied from an external power source, and transmits the rotational driving force to the compression mechanism unit 20 via the rotating shaft 21. For example, a brushless DC motor is used as the electric motor unit 30.

[0021] The electric motor section 30 includes a stator 31 having a hollow cylindrical appearance when viewed from above, and a cylindrical rotor 32 that is rotatably disposed inside the inner surface of the stator 31 and rotates by magnetic action. In the electric motor section 30, electric power is supplied from an external power source to a wound coil that constitutes the stator 31 via lead wires 33, causing the rotor 32 to rotate inside the stator 31.

[0022] The refrigerant flow path 34 formed in the iron core of the rotor 32 is used to guide the refrigerant gas discharged from the compression mechanism 20 to the top of the sealed container 10, and to drop the refrigeration oil that has been guided to the top of the sealed container 10 together with the refrigerant gas to the bottom of the sealed container 10.

[0023] At the center of rotor 32, rotating shaft 21 penetrates rotor 32 in the axial direction and is fixed to rotor 32. Rotating shaft 21 transmits the rotational driving force of rotor 32 to compression mechanism section 20. The inner diameter of the iron core constituting rotor 32 is formed to be smaller than the outer diameter of rotating shaft 21, and the iron core of rotor 32 is fixed to main shaft section 21a of rotating shaft 21.

[0024] (Rotation axis 21) The rotating shaft 21 has a main shaft portion 21a fixed to a rotor 32 of the electric motor unit 30, a counter shaft portion 21c provided on the opposite side of the main shaft portion 21a with the cylinder 23 in between, and an eccentric shaft portion 21b provided between the main shaft portion 21a and the counter shaft portion 21c. The rotating shaft 21 is formed in the axial direction with the main shaft portion 21a, the eccentric shaft portion 21b, and the counter shaft portion 21c formed in this order from above to below the sealed container 10. The rotor 32 of the electric motor unit 30 is fixed to the main shaft portion 21a by shrink fitting or press fitting, and a cylindrical rolling piston 22 is slidably fitted to the eccentric shaft portion 21b.

[0025] The rotating shaft 21 has an eccentric shaft portion 21b disposed at a position corresponding to the cylinder 23 inside the compression mechanism portion 20. A substantially cylindrical rolling piston 22 rotatably attached along the outer surface of the eccentric shaft portion 21b is disposed on the outer periphery of the eccentric shaft portion 21b. When the rotating shaft 21 is rotated by the electric motor portion 30, the rolling piston 22 rotates inside the cylinder 23 along its inner circumferential wall 23e (see FIG. 2).

[0026] (Compression mechanism 20) Fig. 2 is a cross-sectional view that shows a schematic view of the compression mechanism 20 of the compressor 100 according to the first embodiment. Fig. 2 is a cross-sectional view of the compression mechanism 20 cut along the line AA in Fig. 1 and viewed from the top. In Fig. 2, in order to explain the basic structure of the compression mechanism 20, suction holes 40, screw holes 50, spring holes 60, etc., which will be described later, are omitted. The basic structure of the compression mechanism 20 will be explained with reference to Fig. 2.

[0027] The compression mechanism unit 20 is driven by the electric motor unit 30 and compresses the refrigerant gas sucked from the outside. The compression mechanism unit 20 compresses the low-pressure gas refrigerant sucked into the low-pressure space of the sealed container 10 from the refrigerant suction pipe 107 into a high-pressure gas refrigerant by the rotational driving force supplied from the electric motor unit 30, and discharges the compressed high-pressure gas refrigerant above the compression mechanism unit 20.

[0028] As shown in FIGS. 1 and 2, the compression mechanism 20 has a cylinder 23, a rolling piston 22, a vane 26, an upper bearing 24, and a lower bearing 25.

[0029] The cylinder 23 is fixed inside the sealed container 10, and the outer periphery is fixed to the sealed container 10 by bolts or the like. The cylinder 23 is formed in a hollow cylindrical shape. The cylinder 23 has both ends in the axial direction of the rotating shaft 21 open, and a cylinder chamber 23a is provided in the hollow portion. The openings formed at both ends in the axial direction of the rotating shaft 21 of the cylinder 23 are closed by the upper bearing 24 and the lower bearing 25. The upper bearing 24 is provided on the upper surface side of the cylinder 23, and the lower bearing 25 is provided on the lower surface side of the cylinder 23. The cylinder chamber 23a is a space formed in a cylindrical shape, and is a space surrounded by the inner periphery surface of the cylinder 23, the inner wall surface of the upper bearing 24, and the inner wall surface of the lower bearing 25.

[0030] The cylinder chamber 23a accommodates an eccentric shaft portion 21b of the rotary shaft 21 that performs eccentric motion within the cylinder chamber 23a, and a rolling piston 22 that fits onto the eccentric shaft portion 21b. Also, a vane 26 that partitions a space formed by an inner peripheral wall 23e that forms the cylinder chamber 23a and an outer peripheral wall 22a of the rolling piston 22 is accommodated within the cylinder chamber 23a.

[0031] In the compression mechanism 20, the vane 26 moves back and forth radially in a groove provided in the cylinder 23, with one end of the vane 26 abutting against the outer circumferential wall 22a of the rolling piston 22, and divides the inside of the cylinder chamber 23a into a high pressure space and a low pressure space. In the compression mechanism 20, the space surrounded by the rolling piston 22, the cylinder 23, the vane 26, the upper bearing 24, and the lower bearing 25 forms a compression chamber that compresses the low pressure gas refrigerant sucked from the refrigerant suction pipe 107.

[0032] The cylinder 23 is formed with a suction hole 40 (see FIG. 3) through which the refrigerant gas that is sucked into the cylinder chamber 23a from the outside of the sealed container 10 passes. The suction hole 40 through which the refrigerant gas supplied from the refrigerant suction pipe 107 passes is formed penetrating the cylinder 23 from its outer peripheral surface to its inner peripheral surface, and is provided so that the pipe of the refrigerant suction pipe 107 communicates with the cylinder chamber 23a. The cylinder 23 also has a back pressure chamber 23b and an opening 23d, and the detailed structure of the cylinder 23 including these will be described later.

[0033] The rolling piston 22 is housed in the cylinder chamber 23a together with the eccentric shaft portion 21b, and rotates eccentrically in the cylinder chamber 23a by the eccentric shaft portion 21b to compress the refrigerant gas. The rolling piston 22 is formed in a hollow cylindrical shape, and the eccentric shaft portion 21b of the rotating shaft 21 is housed inside the rolling piston 22. The inside of the rolling piston 22 is slidably fitted with the eccentric shaft portion 21b of the rotating shaft 21.

[0034] The vane 26 is provided in a vane groove 23c formed to extend in the radial direction of the cylinder 23, and separates the cylinder chamber 23a into a suction chamber and a compression chamber. The vane 26 is formed in a substantially rectangular parallelepiped shape. When the vane 26 is attached to the vane groove 23c, the thickness of the vane 26 in the circumferential direction of the cylinder 23 is smaller than the length of the vane 26 in the radial direction of the cylinder 23 and the length of the vane 26 in the axial direction of the cylinder 23.

[0035] The upper bearing 24 is fitted to the main shaft portion 21a of the rotating shaft 21 and rotatably supports the main shaft portion 21a. The upper bearing 24 is provided on the end face of the cylinder 23 on the side where the electric motor portion 30 is arranged, and closes one axial opening 23m (see FIG. 7) of the cylinder chamber 23a. Similarly, the lower bearing 25 is fitted to the counter shaft portion 21c of the rotating shaft 21 and rotatably supports the counter shaft portion 21c. The lower bearing 25 is provided on the end face of the cylinder 23 opposite to the side where the electric motor portion 30 is arranged, and closes the other axial opening 23n (see FIG. 7) of the cylinder chamber 23a.

[0036] The upper bearing 24 is formed in a generally inverted T-shape in side view, and the lower bearing 25 is formed in a generally T-shape in side view. The upper bearing 24 is provided with a discharge port (not shown) that discharges the refrigerant gas compressed in the compression chamber to the outside of the cylinder chamber 23a.

[0037] A discharge valve (not shown) is provided in the discharge port of the upper bearing 24, and the discharge valve controls the timing of discharging the high-temperature, high-pressure refrigerant gas discharged through the discharge port from the cylinder 23. The discharge valve closes until the refrigerant gas compressed in the cylinder chamber 23a of the cylinder 23 reaches a predetermined pressure, and opens the valve when the refrigerant gas reaches or exceeds the predetermined pressure, discharging the high-temperature, high-pressure refrigerant gas outside the cylinder chamber 23a.

[0038] In the cylinder chamber 23a, the operations of sucking in the refrigerant, compressing it, and discharging the refrigerant are repeated, and the refrigerant gas is intermittently discharged from the discharge port, which may cause noise such as pulsating noise to be generated from the cylinder 23. In order to reduce such generated noise, a discharge muffler 27 is attached to the outer side of the upper bearing 24, which is the side on which the electric motor unit 30 is located, so as to cover the upper bearing 24.

[0039] Discharge muffler 27 is provided with a discharge hole (not shown) that connects the space formed by discharge muffler 27 and upper bearing 24 with the inside of sealed container 10. Refrigerant gas discharged from cylinder 23 through the discharge port is first discharged into the space formed by discharge muffler 27 and upper bearing 24, and then discharged from the discharge hole into sealed container 10.

[0040] (Detailed structure of cylinder 23) FIG. 3 is a schematic diagram showing the structure of the cylinder 23 in the compression mechanism section 20 of the compressor 100 according to the first embodiment. FIG. 3 conceptually shows the internal structure of the cylinder 23. FIG. 4 is a conceptual diagram of the vane groove 23c and the spring hole 60 of the cylinder 23 of the compression mechanism section 20 according to the first embodiment, as viewed from the circumferential direction. FIG. 4 is a schematic cross-sectional view of the compression mechanism section 20 cut along the line HH in FIG. 5, as viewed from the circumferential direction, as viewed from the cylinder 23. FIG. 5 is a conceptual diagram of the vane groove 23c and the spring hole 60 of the compression mechanism section 20 according to the first embodiment, as viewed from the radial direction, as viewed from the cylinder 23. FIG. 5 is a schematic cross-sectional view of the compression mechanism section 20 cut along the line GG in FIG. 4, as viewed from the radial direction, as viewed from the cylinder 23. In addition, in FIG. 3 to FIG. 5, in order to explain the structure of the vane groove 23c and the spring hole 60, the vane 26 is omitted. The structure of the cylinder 23 will be explained in more detail with reference to FIG. 2 to FIG. 4.

[0041] A vane groove 23c is formed in the cylinder 23, which communicates with the cylinder chamber 23a and extends in the radial direction of the cylinder 23 centered on the rotary shaft 21. An opening 23d is formed in the vane groove 23c at one end located on the inner periphery side of the cylinder 23, and a back pressure chamber 23b is formed at the other end located on the outer periphery side of the cylinder 23. The opening 23d is provided in an inner periphery wall 23e of the cylinder 23 and opens to the cylinder chamber 23a.

[0042] The vane groove 23c is a groove that penetrates the cylinder 23 on the inner diameter side and communicates with the cylinder chamber 23a, but does not penetrate the cylinder 23 on the outer diameter side. The vane groove 23c penetrates the cylinder 23 from the front side to the back side when the cylinder 23 is viewed from the front, that is, when viewed from a direction in which the outer shape of the cylinder 23 appears circular. In other words, the vane groove 23c is a groove that penetrates the cylinder 23 in the axial direction of the cylinder 23.

[0043] The vane groove 23c is a space in which the vane 26 reciprocates, and the vane 26 that separates the cylinder chamber 23a into a suction chamber and a compression chamber is fitted into the vane groove 23c. The vane 26 is slidably housed in the vane groove 23c. During the compression stroke, the vane 26 reciprocates in the radial direction of the cylinder 23 within the vane groove 23c following the eccentric rotation of the rolling piston 22 while keeping the tip of the vane 26 in contact with the outer peripheral wall 22a of the rolling piston 22. The cylinder chamber 23a is separated into a suction chamber and a compression chamber by the tip of the vane 26 abutting against the outer peripheral wall 22a of the rolling piston 22.

[0044] The back pressure chamber 23b of the vane groove 23c is also called a blind hole. The back pressure chamber 23b is a portion that stops the movement of the vane 26 toward the outer diameter side of the cylinder 23 and limits the movement of the vane 26 so that the vane 26 does not jump out toward the outer diameter side of the cylinder 23. The back pressure chamber 23b also serves as a back pressure chamber to introduce high pressure refrigerant.

[0045] A vane spring 62 is provided in the back pressure chamber 23b of the vane groove 23c. The vane spring 62 is fixed inside the spring hole 60. The vane spring 62 and the cylinder 23 are fixed by a spring fixing portion 63. At the spring fixing portion 63, a seat coil portion 62a of the vane spring 62 is press-fitted into the spring hole 60 and abuts against the inner wall of the cylinder 23, thereby fixing the vane spring 62 to the cylinder 23. Note that fixing the vane spring 62 to the cylinder 23 by pressing the seat coil portion 62a is one example of a method of fixing the vane spring 62 to the cylinder 23, and the method of fixing the vane spring 62 to the cylinder 23 is not limited.

[0046] The vane spring 62 abuts against the back (outer diameter side) of the vane 26, and presses the vane 26 toward the center of the cylinder 23. In the compression mechanism 20, high-pressure refrigerant gas in the sealed container 10 flows into the back pressure chamber 23b, and a force that moves the vane 26 radially toward the center of the cylinder chamber 23a is generated by the pressure difference between the pressure of the refrigerant gas in the back pressure chamber 23b and the pressure of the refrigerant gas in the cylinder chamber 23a. The vane 26 is moved radially toward the center of the cylinder chamber 23a by the force due to the pressure difference between the back pressure chamber 23b and the cylinder chamber 23a and the force of the vane spring 62 pressing the vane 26 radially.

[0047] The force moving the vane 26 in the radial direction causes one end of the vane 26, i.e., the end on the cylinder chamber 23a side, to abut against the outer circumferential wall 22a of the cylindrically formed rolling piston 22. As a result, the vane 26 can separate the space formed by the inner circumferential wall 23e of the cylinder 23 and the outer circumferential wall 22a of the rolling piston 22, as described above.

[0048] There are cases where the pressure difference between the refrigerant gas in the sealed container 10, i.e., the pressure of the refrigerant gas in the back pressure chamber 23b, and the pressure of the refrigerant gas in the cylinder chamber 23a is not sufficient to press the vane 26 against the outer peripheral wall 22a of the rolling piston 22. Even in such cases, the compression mechanism 20 can press one end of the vane 26 against the outer peripheral wall 22a of the rolling piston 22 with the force of the vane spring 62, so that one end of the vane 26 can always abut against the outer peripheral wall 22a of the rolling piston 22.

[0049] (Suction hole 40) FIG. 6 is a side view that shows a schematic structure of the suction hole 40 in the compression mechanism 20 of the compressor 100 according to the first embodiment. FIG. 7 is a vertical cross-sectional view that shows a schematic structure of the suction hole 40 in the compression mechanism 20 of the compressor 100 according to the first embodiment. FIG. 8 is a partial cross-sectional view that shows a schematic structure of the suction hole 40, the screw hole 50, and the spring hole 60 in the cylinder 23 of the compressor 100 according to the first embodiment. Note that FIG. 6 shows the suction hole 40 from the side of the cylinder 23, and is a view of the cylinder 23 in the direction C shown in FIG. 3. Also, FIG. 8 is a cross-sectional view of the position of the line DD in FIG. 3. Note that FIG. 7 omits the illustration of the structure inside the cylinder chamber 23a in order to explain the structures of the cylinder 23, the upper bearing 24, and the lower bearing 25. Next, the shape of the suction path of the refrigerant in the compression mechanism 20 will be explained with reference to FIGS. 3 to 8.

[0050] As shown in Fig. 3 and Fig. 6, the cylinder 23 is formed with a suction hole 40 through which the refrigerant drawn into the cylinder chamber 23a passes, the suction hole 40 extending in the radial direction of the cylinder 23. The suction hole 40 penetrates the walls constituting the cylinder 23 in the radial direction. That is, the suction hole 40 penetrates between the outer peripheral wall 23f and the inner peripheral wall 23e. The suction hole 40 penetrates the cylinder 23 in the radial direction, but does not penetrate the cylinder 23 in the thickness direction. The thickness direction of the cylinder 23 referred to here is the axial direction of the rotating shaft 21, which is the up-down direction on the paper surface of Fig. 6.

[0051] The suction hole 40 has a suction hole outer diameter connection part 40a formed on the radial outer periphery side of the cylinder 23, and a suction hole inner diameter connection part 40b formed on the radial inner periphery side of the cylinder 23. The suction hole outer diameter connection part 40a forms a space S1 located on the radial outer periphery side of the cylinder 23, in the cylinder 23. The suction hole inner diameter connection part 40b forms a space S2 located on the radial inner periphery side of the cylinder 23, in the cylinder 23.

[0052] As shown in Figure 7, the cross-sectional area SA1 of the hole of suction hole outer diameter connection portion 40a in a cross section perpendicular to the radial direction of cylinder 23 is formed to be larger than the cross-sectional area SA2 of the hole of suction hole inner diameter connection portion 40b in a cross section perpendicular to the radial direction of cylinder 23.

[0053] The suction hole outer diameter connection part 40a forms an opening in the outer peripheral wall 23f of the cylinder 23, and the refrigerant suction pipe 107 is inserted into and connected to the suction hole outer diameter connection part 40a. The suction hole inner diameter connection part 40b forms an opening in the inner peripheral wall 23e of the cylinder 23 and communicates with the cylinder chamber 23a. In the circumferential direction of the cylinder 23, the suction hole inner diameter connection part 40b is formed next to the threaded hole 50 formed closest to the suction hole 40.

[0054] As shown in Fig. 6, in a cross section perpendicular to the axial direction of the suction hole 40, the cross-sectional shape of the suction hole outer diameter connection part 40a is circular, and the cross-sectional shape of the suction hole inner diameter connection part 40b is elliptical. The axial direction of the suction hole 40 is also the radial direction of the cylinder 23. As shown in Fig. 8, the cross-sectional shape of the suction hole inner diameter connection part 40b in a cross section perpendicular to the radial direction of the cylinder 23 is such that the length of the opening width W2 in the thickness direction of the cylinder 23 is longer than the opening width W1 in the circumferential direction of the cylinder 23. The thickness direction of the cylinder 23 is also the axial direction of the rotating shaft 21.

[0055] In other words, the cross-sectional shape of suction hole inner diameter connection part 40b in a cross section perpendicular to the radial direction of cylinder 23 is an ellipse whose length in the thickness direction of cylinder 23 is longer than in the circumferential direction of cylinder 23. In cylinder 23, the cross-sectional shape of suction hole outer diameter connection part 40a in a cross section perpendicular to the radial direction of cylinder 23 is circular, and the cross-sectional shape of suction hole inner diameter connection part 40b in a cross section perpendicular to the radial direction of cylinder 23 is non-circular.

[0056] The cross-sectional shape of the suction hole inner diameter connecting part 40b is not limited to an elliptical shape. The cross-sectional shape of the suction hole inner diameter connecting part 40b may be, for example, an ellipse or a rectangle, as long as one dimension is longer than the other dimension. Here, the dimension in one direction is the dimension in the axial direction of the cylinder 23 and the dimension in the thickness direction of the cylinder 23. Also, the dimension in the other direction is the dimension in the circumferential direction of the cylinder 23. For example, when the suction hole inner diameter connecting part 40b is an elliptical shape, the major axis direction of the suction hole inner diameter connecting part 40b coincides with the thickness direction of the cylinder 23.

[0057] In addition, the cross-sectional shape of the suction hole outer diameter connection part 40a is not limited to a circular shape. The cross-sectional shape of the suction hole outer diameter connection part 40a may be a shape in which the dimension in one direction is longer than the dimension in the other direction, such as an ellipse or a rectangle, as in the shape of the suction hole outer diameter connection part 40a2 shown in FIG. 6. Here, the dimension in one direction is the dimension in the circumferential direction of the cylinder 23, and the dimension in the other direction is the dimension in the axial direction of the cylinder 23 and the dimension in the thickness direction of the cylinder 23. For example, when the suction hole outer diameter connection part 40a is oval, the major axis direction of the suction hole outer diameter connection part 40a coincides with the circumferential direction of the cylinder 23. That is, the cross-sectional shape of the suction hole outer diameter connection part 40a2 in the cross section perpendicular to the radial direction of the cylinder 23 may be noncircular, and the cross-sectional shape of the suction hole inner diameter connection part 40b in the cross section perpendicular to the radial direction of the cylinder 23 may be noncircular.

[0058] In the compression mechanism 20, the major axis direction of the cross section of the suction hole inner diameter connection part 40b coincides with the thickness direction of the cylinder 23, so that the timing at which the rolling piston 22 completes the closing of the suction hole 40 is earlier than when the cross section of the suction hole inner diameter connection part 40b is a perfect circle. That is, the opening width in the circumferential direction of the cylinder 23 is shorter than the opening width in the thickness direction of the cylinder 23, so that the timing at which the rolling piston 22 completes the closing of the suction hole 40 is earlier than when the cross section of the suction hole inner diameter connection part 40b is a perfect circle. As a result, the compression mechanism 20 can ensure a large volume of the formed compression chamber, and can ensure a large exhaust volume in the compression stroke during one rotation of the rotating shaft 21 and the rolling piston 22. The timing at which the closing of the suction hole 40 is earlier than when the cross section of the suction hole inner diameter connection part 40b is a perfect circle is earlier than when the cross section of the suction hole inner diameter connection part 40b is a perfect circle having the same diameter as the major axis of the suction hole inner diameter connection part 40b.

[0059] Here, an example of the structure of the cylinder 23 according to the first embodiment will be described. The dimensions of the cylinder 23 shown below are examples, and the dimensions of the cylinder 23 are not limited to the dimensions shown below. For example, the thickness of the cylinder 23 is 23 mm. The diameter of the suction hole outer diameter connection part 40a, which is formed in a circular shape in a cross section perpendicular to the radial direction of the cylinder 23, is 19 mm.

[0060] The major axis of the suction hole inner diameter connecting portion 40b formed in an oval shape in a cross section perpendicular to the radial direction of the cylinder 23 is 18 mm, and the minor axis is 15 mm. The thickness t1 of the first thin wall portion 23g of the cylinder 23 formed by this is 2 mm. The first thin wall portion 23g is a wall portion of the cylinder 23 that constitutes a part of the suction hole outer diameter connecting portion 40a, and is a part that constitutes a part of the wall of the cylinder 23 between the suction hole outer diameter connecting portion 40a and the end face 23h in the thickness direction of the cylinder 23. The thickness t1 of the first thin wall portion 23g is the distance between the suction hole outer diameter connecting portion 40a and the end face 23h of the cylinder 23 in the axial direction of the cylinder 23, i.e., in the thickness direction of the cylinder 23.

[0061] First thin portion 23g is a portion where the distance between suction hole 40 and end face 23h of cylinder 23 is smallest in the thickness direction of cylinder 23, and is a part of cylinder 23. End face 23h of cylinder 23 is an end face of cylinder 23 in the axial direction, and is the end face of cylinder 23 on which upper bearing 24 or lower bearing 25 is disposed.

[0062] In the cylinder 23, the diameter of the suction hole outer diameter connection part 40a and the diameter of the suction hole inner diameter connection part 40b are different inside the suction hole 40, so a step part 41 is formed at the boundary between the suction hole outer diameter connection part 40a and the suction hole inner diameter connection part 40b. The step part 41 faces the outer periphery of the cylinder 23 inside the suction hole 40, and constitutes a step part between the inner periphery wall 40a1 of the suction hole outer diameter connection part 40a and the inner periphery wall 40b1 of the suction hole inner diameter connection part 40b.

[0063] In the suction hole 40 of the cylinder 23, the representative dimension of the suction hole outer diameter connection part 40a is larger than the representative dimension of the suction hole inner diameter connection part 40b. Therefore, when forming the suction hole 40 of the cylinder 23, the worker or the processing machine can perform the processing work of the suction hole 40 only from the suction hole outer diameter connection part 40a side in the radial direction of the cylinder 23. In other words, when forming the suction hole 40 of the cylinder 23, the worker or the processing machine does not need to significantly change the processing position of the cylinder 23. Therefore, when manufacturing the cylinder 23 of the compression mechanism part 20, the suction hole 40 can be processed easily, and the manufacturing cost can be suppressed.

[0064] In the cylinder 23 of the first embodiment, the representative dimension of the suction hole outer diameter connection part 40a is larger than the representative dimension of the suction hole inner diameter connection part 40b. However, when a processing tool capable of processing from the inner diameter side of the cylinder 23 can be used, the representative dimension of the suction hole inner diameter connection part 40b of the cylinder 23 may be larger than the representative dimension of the suction hole outer diameter connection part 40a. For example, the diameter of the suction hole outer diameter connection part 40a formed in a circular shape may be 19 [mm], the major axis of the suction hole inner diameter connection part 40b formed in an elliptical shape may be 19.5 [mm], and the minor axis may be 15 [mm]. In other words, the major axis of the suction hole inner diameter connection part 40b formed in an elliptical shape may be larger than the diameter of the suction hole outer diameter connection part 40a formed in a circular shape.

[0065] The diameter of the suction hole outer diameter connecting part 40a is the same from the inner circumference side to the outer circumference side in the radial direction. The diameter of the suction hole inner diameter connecting part 40b is the same from the inner circumference side to the outer circumference side in the radial direction. That is, the diameters of the suction hole outer diameter connecting part 40a and the suction hole inner diameter connecting part 40b are constant from the inner circumference side to the outer circumference side in the radial direction. The suction hole outer diameter connecting part 40a forms a cylindrical space S1, and the suction hole inner diameter connecting part 40b forms a columnar space S2. The space S1 is located on the outer circumference side of the space S2 in the radial direction of the cylinder 23.

[0066] However, the cylinder 23 is not limited to one in which the diameters of the suction hole outer diameter connecting part 40a and the suction hole inner diameter connecting part 40b are formed to be constant from the inner periphery side to the outer periphery side in the radial direction. As long as the cylinder 23 has a step part 41 inside the suction hole 40, the diameter of the suction hole outer diameter connecting part 40a may vary from the inner periphery side to the outer periphery side in the radial direction. As long as the cylinder 23 has a step part 41 inside the suction hole 40, the diameter of the suction hole inner diameter connecting part 40b may vary from the inner periphery side to the outer periphery side in the radial direction.

[0067] In the axial direction of the rotating shaft 21, the center of the suction hole outer diameter connection part 40a coincides with the center in the thickness direction of the cylinder 23. However, the configuration of the cylinder 23 is not limited to this configuration, and depending on the configuration of other compressors 100 such as a twin rotary compressor, the center of the suction hole outer diameter connection part 40a does not have to coincide with the center in the thickness direction of the cylinder 23 in the axial direction of the rotating shaft 21.

[0068] The cylinder 23 is sandwiched between two bearings, an upper bearing 24 and a lower bearing 25, and is fastened together with the upper bearing 24 and the lower bearing 25 by a screw 80 (see FIG. 1). In the compression mechanism 20, the cylinder 23 forms the side surface of the compression chamber, and the two bearings form the end surfaces of the compression chamber, thereby forming a cylindrical cylinder chamber 23a. In addition, the compression mechanism 20 forms a compression chamber surrounded by the rolling piston 22, the cylinder 23, the vane 26, the upper bearing 24, and the lower bearing 25 in the cylinder chamber 23a.

[0069] (Screw hole 50) Next, the screw hole 50 will be described with reference to Figures 3 and 8. The compression mechanism 20 has a plurality of screws 80 (see Figure 1) that fasten the upper bearing 24, the lower bearing 25, and the cylinder 23. The cylinder 23 is formed with a plurality of screw holes 50 that penetrate the cylinder 23 in the thickness direction of the cylinder 23. A plurality of screws 80 are arranged in the plurality of screw holes 50, respectively.

[0070] As described above, the cylinder 23 has threaded holes 50 for arranging the screws 80 for fastening the cylinder 23, the upper bearing 24, and the lower bearing 25, and for inserting the screws 80. As shown in Fig. 8, the threaded holes 50 are formed in the axial direction of the cylinder 23, i.e., parallel to the thickness direction of the cylinder 23. The threaded holes 50 penetrate the cylinder 23 from one end face to the other end face in the axial direction of the cylinder 23, i.e., in the thickness direction of the cylinder 23.

[0071] 3, a plurality of threaded holes 50 are formed along the circumferential direction of the cylinder 23. In the cylinder 23 according to the first embodiment, six threaded holes 50 are formed in the circumferential direction, and the cylinder 23, the upper bearing 24, and the lower bearing 25 are fastened together by six screws 80. The number of threaded holes 50 is not limited to six, and may be five or less, or seven or more, as long as the cylinder 23 and the upper bearing 24, and the cylinder 23 and the lower bearing 25 can be fastened together.

[0072] In many cases, the screws 80 for fastening the cylinder 23, the upper bearing 24, and the lower bearing 25 in the rotary compressor are disposed approximately evenly in the circumferential direction of the cylinder 23. That is, when one circumference of the cylinder 23 in the circumferential direction is taken as 360° around the center AX of the cylinder 23, the screws 80 are disposed at positions that divide the angle of 360° approximately evenly, and the screw holes 50 are formed.

[0073] 3, the positions of the threaded holes 50 when the cylinder 23 is viewed in the axial direction will be described in more detail. When the center axis CS of the vane groove 23c is set as 0° with the center AX of the cylinder 23 as the center, the first threaded hole 50 is formed near the suction hole 40 at a position approximately 30° with respect to the center axis CS in the counterclockwise direction.

[0074] That is, when the central axis CS of vane groove 23c is set to 0° as the reference, the first screw 80 is positioned at approximately 30° from the central axis CS in the counterclockwise direction and is arranged near suction hole 40. The reason why the first screw 80 is positioned at approximately 30° from the central axis CS and is arranged near suction hole 40 is that many operating parts are arranged around vane groove 23c, and therefore screw 80 cannot be arranged around vane groove 23c.

[0075] In the cylinder 23 of the first embodiment, the suction hole 40 is formed such that the central axis CL of the suction hole 40 is located at a position rotated 26° counterclockwise from the central axis CS of the vane groove 23c when the central axis CS of the vane groove 23c is used as a reference. That is, the vane groove 23c and the suction hole 40 are formed in the cylinder 23 such that the angle between the central axis CS of the vane groove 23c and the central axis CL of the suction hole 40 is 26° in the circumferential direction of the cylinder 23.

[0076] In the cylinder 23 of the first embodiment, the interference tolerance distance between the suction hole 40 and the screw hole 50 is 1.3 mm. The nominal diameter of the screw 80 is M6, and the diameter of the screw hole 50 through which the screw 80 passes is Φ7.4, i.e., 7.4 mm. The screw head of the screw 80 is Φ14, i.e., 14 mm. When the cylinder 23 is viewed from the end face direction and the screw hole 50, the screw head of the screw 80, and the suction hole 40 are each projected onto the lower end face of the cylinder 23, the screw hole 50 and the suction hole 40 do not interfere with each other, but the screw head of the screw 80 and the suction hole 40 may interfere with each other.

[0077] 3, among the threaded holes 50, at least the threaded hole 50 formed closest to the suction hole 40 is formed on the inner circumferential side of the suction hole outer diameter connection part 40a in the radial direction of the cylinder 23. Moreover, among the threaded holes 50, the threaded hole 50 formed closest to the suction hole 40 is not formed next to the suction hole outer diameter connection part 40a in the circumferential direction, but is formed next to the suction hole inner diameter connection part 40b.

[0078] 3 and 8, the relationship between the first thin-walled portion 23g and the second thin-walled portion 23j in the cylinder 23 will be described. As described above, the first thin-walled portion 23g is the portion where the distance between the suction hole 40 and the end face 23h of the cylinder 23 is the smallest in the thickness direction of the cylinder 23. The second thin-walled portion 23j is the portion where the distance between the suction hole inner diameter connection portion 40b of the suction hole 40 and the threaded hole 50 is the smallest in the circumferential direction of the cylinder 23, and is a part of the wall constituting the cylinder 23. This threaded hole 50 is the threaded hole 50 that is located closest to the suction hole inner diameter connection portion 40b among the multiple threaded holes 50.

[0079] As described above, the thickness t1 [mm] of the first thin-walled portion 23g is the distance between the suction hole outer diameter connection portion 40a and the end face 23h of the cylinder 23 in the axial direction of the cylinder 23, i.e., the thickness direction of the cylinder 23. The thickness t2 [mm] of the second thin-walled portion 23j is expressed as the distance between the suction hole inner diameter connection portion 40b of the suction hole 40 and the screw hole 50 that is closest to the suction hole inner diameter connection portion 40b among the multiple screw holes 50 in the circumferential direction of the cylinder 23. That is, the thickness t2 [mm] of the second thin-walled portion 23j is the thickness of the cylinder 23 at the part where the distance between the suction hole inner diameter connection portion 40b and the screw hole 50 that is closest to the suction hole inner diameter connection portion 40b among the multiple screw holes 50 is the smallest in the circumferential direction of the cylinder 23.

[0080] The cylinder 23 is formed so that the thickness t1 [mm] of the first thin portion 23g is greater than the thickness t2 [mm] of the second thin portion 23j (thickness t1>thickness t2).

[0081] A refrigerant suction pipe 107 made of copper or iron is driven into the suction hole outer diameter connecting portion 40a of the suction hole 40 to form a refrigerant flow path. Therefore, a large external force is applied to the first thin-walled portion 23g during the process of connecting the refrigerant suction pipe 107.

[0082] In contrast, the suction hole inner diameter connection portion 40b of the suction hole 40 may be affected by screw fastening from the screw hole 50 into which the screw 80 for fastening the cylinder 23 and the like is inserted, but the second thin-walled portion 23j is less likely to be subjected to a large external force than the first thin-walled portion 23g. Therefore, the first thin-walled portion 23g receives a larger force during assembly of the compression mechanism 20 than the second thin-walled portion 23j, and the cylinder 23 is more likely to be distorted. Therefore, by making the thickness t1 of the first thin-walled portion 23g thicker than the thickness t2 of the second thin-walled portion 23j, the compression mechanism 20 can suppress distortion of the cylinder 23 during manufacturing.

[0083] As described above, the cross-sectional shape of the suction hole outer diameter connecting part 40a is circular. By making the suction hole outer diameter connecting part 40a circular, the cross-sectional shape of the copper or iron refrigerant suction pipe 107 can also be made circular. By making the cross-sectional shape of the refrigerant suction pipe 107 circular, the piping can be formed individually at low cost, and the operation of driving the piping into the cylinder 23 can be performed simply and easily.

[0084] However, this does not limit the shape of the suction hole outer diameter connection part 40a to a circular shape. For example, the cross-sectional shape of the suction hole outer diameter connection part 40a may be an oval shape similar to the suction hole inner diameter connection part 40b, or may be an ellipse. Also, for example, the cross-sectional shape of the suction hole inner diameter connection part 40b may be a vertical oval shape long in the axial direction of the cylinder 23, whereas the suction hole outer diameter connection part 40a may be a horizontal oval shape long in the circumferential direction of the cylinder 23.

[0085] In the first embodiment, the portion forming the second thin wall portion 23j of the cylinder 23 is a portion between the threaded hole 50 and the portion of the suction hole 40 that has an elliptical cross section. That is, the threaded hole 50 is formed near the portion of the suction hole 40 where the suction hole inner diameter connection portion 40b, which has an elliptical cross section, is formed. Since the threaded hole 50 is formed near the suction hole inner diameter connection portion 40b having an elliptical cross section, the suction hole outer diameter connection portion 40a can have a large diameter without interfering with the threaded hole 50. Therefore, the compressor 100 can reduce the pressure loss during suction of the refrigerant, compared to a compressor having a cylinder in which the threaded hole 50 is formed near the suction hole outer diameter connection portion 40a and the diameter of the suction hole outer diameter connection portion 40a cannot be increased.

[0086] (Spring hole 60) The cylinder 23 has therein a vane spring 62 for operating the vane 26. The vane spring 62 biases the vane 26 so as to press the tip of the vane 26 against the outer peripheral wall 22a of the rolling piston 22. The vane 26 is a partition plate that separates the cylinder chamber 23a into a high pressure chamber and a low pressure chamber. The cylinder 23 is formed with a spring hole 60 as a space for storing and operating the vane spring 62. The spring hole 60 is a space in which the vane spring 62, which serves as the power for the reciprocating motion of the vane 26, is disposed.

[0087] The cylinder 23 is formed with a spring hole 60 for arranging the vane spring 62 so as to extend in the radial direction of the cylinder 23. As shown in FIG. 4, the spring hole 60 is a hole that does not penetrate the cylinder chamber 23a on the inner diameter side of the cylinder 23 when viewed in the circumferential direction of the cylinder 23, that is, from the direction in which the outer shape of the cylinder 23 appears rectangular. The spring hole 60 is a hole that penetrates the cylinder 23 on the outer diameter side and does not penetrate the cylinder 23 on the inner diameter side. The spring hole 60 is a hole whose cross section is a perfect circle in a cross section perpendicular to the radial direction of the cylinder 23, that is, the direction in which the spring hole 60 extends. In the first embodiment, the diameter of the spring hole 60 is Φ14, that is, 14 [mm]. The depth of the spring hole 60 depends on the shape of the vane spring 62 to be operated or the shape of the cylinder 23, but here, the depth of the spring hole 60 is set to 30 [mm]. The depth of the spring hole 60 is the length of the spring hole 60 from the outer peripheral wall 23f of the cylinder 23 to the inner peripheral wall 23e side in the radial direction of the cylinder 23.

[0088] The outer diameter of the cylinder 23 is 130 mm, and the inner diameter of the cylinder 23 is 60 mm. The radial difference between the inner and outer diameters of the cylinder 23 is 35 mm, and the depth of the spring hole 60 accounts for 85% of this radial difference.

[0089] In a rotary compressor, the depth of the spring hole 60 relative to the radius difference of the cylinder 23 is often about 50% to 99%, and the design tolerance of the vane spring 62 operating inside the spring hole 60 can be increased by deepening the depth of the spring hole 60. A spring hole cone portion 61 is formed at the bottom of the spring hole 60 by a drill tip. The spring hole cone portion 61 is a space portion formed in a cone shape inside the cylinder 23. The spring hole cone portion 61 does not have to be formed in the cylinder 23. The interference tolerance distance between the spring hole 60 and the suction hole 40 is 1.2 [mm]. The above-mentioned dimensions of the cylinder 23 are an example, and are not limited to the above-mentioned dimensions of the cylinder 23.

[0090] If the depth of the spring hole 60 is not deep enough, the force pushing the vane 26 is small, and the force with which the vane 26 follows the rolling piston 22 revolving inside the compression chamber is also weak. This can cause a decrease in the force with which the vane 26 separates from the rolling piston 22, particularly in the low rotation range of the compressor 100, specifically below 20 rps. When the vane 26 separates from the rolling piston 22, the high-pressure refrigerant leaks to the low-pressure refrigerant, deteriorating performance. In addition, when the vane 26 separates from the rolling piston 22, the vane 26 or the rolling piston 22 is scraped or deformed due to the stress generated when the vane 26 collides with the rolling piston 22, deteriorating reliability.

[0091] 6 and 8, the relationship between the first thin-walled portion 23g and the third thin-walled portion 23k in the cylinder 23 will be described. The third thin-walled portion 23k is a portion where the distance between the suction hole 40 and the spring hole 60 is the smallest in the circumferential direction of the cylinder 23. More specifically, the third thin-walled portion 23k is a portion where the distance between the suction hole inner diameter connecting portion 40b of the suction hole 40 and the spring hole 60 is the smallest in the circumferential direction of the cylinder 23, and is a part of the wall that constitutes the cylinder 23.

[0092] The thickness t3 [mm] of the third thin-walled portion 23k is expressed as the distance between the suction hole inner diameter connecting portion 40b and the spring hole 60 in the circumferential direction of the cylinder 23. In other words, the thickness t3 [mm] of the third thin-walled portion 23k is the thickness of the cylinder 23 at the portion where the distance between the suction hole inner diameter connecting portion 40b of the suction hole 40 and the spring hole 60 in the circumferential direction of the cylinder 23 is the smallest.

[0093] The cylinder 23 is formed so that the thickness t1 [mm] of the first thin portion 23g is greater than the thickness t3 [mm] of the third thin portion 23k (thickness t1>thickness t3).

[0094] As described above, the copper or iron refrigerant suction pipe 107 is driven into the suction hole outer diameter connecting portion 40a of the suction hole 40 to form a refrigerant flow path. Therefore, a large external force is applied to the first thin-walled portion 23g during the process of connecting the refrigerant suction pipe 107.

[0095] In contrast, in order to fix the vane spring 62 in the spring hole 60, the vane spring 62 may be lightly press-fitted into the spring hole 60, but a large external force is unlikely to be applied to the third thin-walled portion 23k. Therefore, the first thin-walled portion 23g receives a larger force during assembly of the compression mechanism 20 than the third thin-walled portion 23k, and the cylinder 23 is likely to be distorted. Therefore, by making the thickness t1 of the first thin-walled portion 23g thicker than the thickness t3 of the third thin-walled portion 23k, the compression mechanism 20 can suppress distortion of the cylinder 23 during manufacturing.

[0096] As described above, the cross-sectional shape of the suction hole outer diameter connecting part 40a is circular. By making the suction hole outer diameter connecting part 40a circular, the cross-sectional shape of the copper or iron refrigerant suction pipe 107 can also be made circular. By making the cross-sectional shape of the refrigerant suction pipe 107 circular, the piping can be formed individually at low cost, and the operation of driving the piping into the cylinder 23 can be performed simply and easily.

[0097] In the first embodiment, the portion forming the third thin portion 23k of the cylinder 23 is a portion between the spring hole 60 and the portion of the suction hole 40 that has an elliptical cross section. That is, the portion of the suction hole 40 where the spring hole 60 is closest to the suction hole 40 is close to the portion of the suction hole 40 where the suction hole inner diameter connection portion 40b is formed in an elliptical shape. Therefore, the suction hole outer diameter connection portion 40a can be made larger in diameter without interfering with the spring hole 60. The compressor 100 can reduce pressure loss during suction of a refrigerant, compared to a compressor having a cylinder in which the diameter of the suction hole outer diameter connection portion 40a cannot be made larger because the screw hole 50 is formed near the suction hole outer diameter connection portion 40a.

[0098] [Operation of Compressor 100] In the compressor 100, the rotational motion of the rotary shaft 21 causes the eccentric shaft portion 21b of the rotary shaft 21 to rotate within the cylinder chamber 23a of the cylinder 23. The volume of the suction chamber partitioned by the inner circumferential wall 23e forming the cylinder chamber 23a, the outer circumferential wall 22a of the rolling piston 22 fitted into the eccentric shaft portion 21b, and the vane 26 increases with the rotation of the rotary shaft 21, and the volume of the compression chamber decreases.

[0099] In the compressor 100, first, the suction chamber communicates with the suction hole 40, and low-pressure refrigerant gas is sucked into the cylinder chamber 23a. Next, the rolling piston 22 closes the communication between the compression chamber in which the refrigerant gas is compressed and the suction hole 40, and the volume of the compression chamber decreases and the refrigerant gas in the compression chamber is compressed. Finally, the compression chamber communicates with a discharge port (not shown), and after the refrigerant gas in the compression chamber reaches a predetermined pressure, a discharge valve provided in the discharge port opens, and the compressed, high-pressure, high-temperature refrigerant gas is discharged outside the compression chamber, i.e., outside the cylinder chamber 23a.

[0100] The high-pressure, high-temperature refrigerant gas discharged from the cylinder chamber 23a into the sealed container 10 through the discharge muffler 27 passes through the motor unit 30, rises inside the sealed container 10, and is discharged to the outside of the sealed container 10 from a discharge pipe 102 provided at the top of the sealed container 10. A refrigeration circuit 201 (see FIG. 9) through which the refrigerant flows is configured outside the sealed container 10, and the discharged refrigerant circulates through the refrigeration circuit 201 and returns to the suction muffler 101.

[0101] [Effects of Compressor 100] In the compressor 100, the cross-sectional area SA1 of the suction hole outer diameter connection part 40a is formed larger than the cross-sectional area SA2 of the suction hole inner diameter connection part 40b. Therefore, the compressor 100 can increase the flow passage area of ​​the refrigerant in the suction hole 40 as a whole without expanding the radial inner circumferential side of the suction hole 40 in the circumferential direction of the cylinder 23, and reduce the pressure loss of the refrigerant flow. In addition, the cross-sectional shape of the suction hole inner diameter connection part 40b is a shape in which the opening width W2 in the thickness direction of the cylinder 23 is larger than the opening width W1 in the circumferential direction of the cylinder 23. That is, the cross-sectional shape of the suction hole inner diameter connection part 40b is a shape in which the opening width W1 in the circumferential direction of the cylinder 23 is smaller than the opening width W2 in the thickness direction of the cylinder 23. Therefore, in the compressor 100, the angle at which the rolling piston 22 completes the closing of the suction hole 40 can be set earlier from the start of rotation than a compressor that does not have the suction hole 40. In the compressor 100, the angle at which the rolling piston 22 completes blocking of the suction hole 40 can be set to an earlier timing from the start of rotation, and therefore the volumetric efficiency of the compressor 100 can be improved compared to a compressor that does not have the suction hole 40. By having the suction hole 40 with such a structure, the compressor 100 can ensure a flow path area of ​​the refrigerant suction path while avoiding interference with the screw hole 50 or the spring hole 60. Therefore, the compressor 100 can prevent a decrease in efficiency of the compressor 100 even under operating conditions using a high flow rate refrigerant, and can improve the performance and capacity of the compressor 100.

[0102] Moreover, the cylinder 23 is formed so that the thickness t1 [mm] of the first thin-walled portion 23g is larger than the thickness t2 [mm] of the second thin-walled portion 23j. Since the refrigerant suction pipe 107 is driven into the suction hole outer diameter connecting portion 40a of the cylinder 23, a large force is applied to the first thin-walled portion 23g when the compressor 100 is assembled. By making the thickness t1 of the first thin-walled portion 23g thicker than the thickness t2 of the second thin-walled portion 23j, the compressor 100 can ensure the strain resistance of the first thin-walled portion 23g when the compressor 100 is assembled, and can suppress the distortion of the cylinder 23 when the compressor 100 is manufactured. Since the pipe driving of the refrigerant suction pipe 107 applies a stronger force to the cylinder 23 than the screw fastening by the screw 80, it is desirable to make the thickness t1 of the first thin-walled portion 23g thicker than the thickness t2 of the second thin-walled portion 23j.

[0103] Moreover, the cylinder 23 is formed so that the thickness t1 [mm] of the first thin-walled portion 23g is larger than the thickness t3 [mm] of the third thin-walled portion 23k. As described above, since the refrigerant suction pipe 107 is driven into the suction hole outer diameter connecting portion 40a of the cylinder 23, a large force is applied to the first thin-walled portion 23g when the compressor 100 is assembled. By making the thickness t1 of the first thin-walled portion 23g thicker than the thickness t3 of the third thin-walled portion 23k, the compressor 100 can ensure the strain resistance of the first thin-walled portion 23g when the compressor 100 is assembled, and the distortion of the cylinder 23 can be suppressed when the compressor 100 is manufactured. Since the pipe driving of the refrigerant suction pipe 107 applies a stronger force to the cylinder 23 than the insertion of the vane spring 62 into the spring hole 60, it is desirable to make the thickness t1 of the first thin-walled portion 23g thicker than the thickness t3 of the third thin-walled portion 23k.

[0104] In addition, the cylinder 23 has a circular cross-sectional shape of the suction hole outer diameter connection part 40a in a cross section perpendicular to the radial direction of the cylinder 23, and a non-circular cross-sectional shape of the suction hole inner diameter connection part 40b in a cross section perpendicular to the radial direction of the cylinder 23. Since a suction pipe such as the refrigerant suction pipe 107 is often formed to have a circular cross-sectional shape, it is desirable that the cross-sectional shape of the suction hole outer diameter connection part 40a into which the refrigerant suction pipe 107 is driven is circular. In addition, due to the structure of the compressor 100, there is a relatively large amount of space on the outer diameter side of the cylinder 23, and there is no need to take interference with the screw hole 50, etc. into consideration, so there is no need to make the cross-sectional shape of the suction hole outer diameter connection part 40a non-circular.

[0105] In addition, the cylinder 23 may have a noncircular cross-sectional shape of the suction hole outer diameter connecting part 40a2 in a cross section perpendicular to the radial direction of the cylinder 23, and a noncircular cross-sectional shape of the suction hole inner diameter connecting part 40b in a cross section perpendicular to the radial direction of the cylinder 23. Since the cross-sectional shape of the suction hole outer diameter connecting part 40a is noncircular, it is difficult to drive the refrigerant suction tube 107 into the cylinder 23. However, by making the cross-sectional shape of the suction hole outer diameter connecting part 40a noncircular, the refrigerant flow path area can be further increased and pressure loss can be reduced. The noncircular shape is, for example, an elliptical shape having a major axis in the circumferential direction of the cylinder 23, and the refrigerant flow path area in the suction hole outer diameter connecting part 40a can be increased without changing the thickness t1 of the first thin-walled part 23g. That is, the suction hole 40 may be formed in the cylinder 23 so that the diameter of the elliptical shape in the cross-sectional shape of the suction hole 40 is larger in the circumferential direction of the cylinder 23 than in the height direction of the cylinder 23. The suction hole 40 is likely to interfere with the spring hole 60 or the threaded hole 50 on the suction hole inner diameter connection 40b side of the suction hole 40, and there is relatively more space at the suction hole outer diameter connection 40a of the suction hole 40. Therefore, the suction hole outer diameter connection 40a of the suction hole 40, which has relatively more space, can extend the flow path cross-sectional shape of the suction hole 40 in the circumferential direction of the cylinder 23, thereby expanding the flow path area.

[0106] Furthermore, the cross-sectional shape of suction hole inner diameter connection part 40b in a cross section perpendicular to the radial direction of cylinder 23 is an ellipse whose length in the thickness direction of cylinder 23 is longer than in the circumferential direction of cylinder 23. By having cylinder 23 with this structure, compressor 100 can hasten the timing at which rolling piston 22 completes blocking of suction hole 40, and improve the volumetric efficiency of compressor 100, compared to conventional compressors in which the entire suction hole is circular.

[0107] [Configuration of the refrigeration cycle device 200] 9 is a configuration diagram of a refrigeration cycle apparatus 200 including the compressor 100 according to the first embodiment. The refrigeration cycle apparatus 200 includes the compressor 100, a flow path switching device 103, an outdoor heat exchanger 104, a pressure reducing device 105, and an indoor heat exchanger 106. The refrigeration cycle apparatus 200 also includes an intake muffler 101, which is connected to the intake side of the compressor 100. In the refrigeration cycle apparatus 200 such as a refrigeration air conditioner, the indoor heat exchanger 106 is often mounted on an apparatus disposed indoors, and the compressor 100, the flow path switching device 103, the outdoor heat exchanger 104, the pressure reducing device 105, and the like are often mounted on an apparatus disposed outdoors.

[0108] In the refrigeration cycle apparatus 200, a compressor 100, a flow switching device 103, an outdoor heat exchanger 104, a pressure reducing device 105, and an indoor heat exchanger 106 are sequentially connected by refrigerant piping to form a refrigeration circuit 201 through which a refrigerant circulates. Although R407C refrigerant, R410A refrigerant, R32 refrigerant, or the like is used as the refrigerant flowing through the refrigeration circuit 201, the compressor efficiency can be further improved by using a low GWP refrigerant such as R1234yf refrigerant or R290 refrigerant.

[0109] The flow path switching device 103 is, for example, a four-way valve, and switches the flow direction of the refrigerant. The flow path switching device 103 is connected to the discharge side of the compressor 100. The outdoor heat exchanger 104 exchanges heat between the outdoor air and the refrigerant flowing inside the outdoor heat exchanger 104. The outdoor heat exchanger 104 functions as a condenser or an evaporator depending on the flow direction of the refrigerant. The pressure reducing device 105 reduces the pressure of the refrigerant that flows out of the condenser and into the pressure reducing device 105 and flows inside the pressure reducing device 105.

[0110] The pressure reducing device 105 is, for example, an electronic expansion valve capable of adjusting the opening degree of a throttle, and controls the pressure of the refrigerant flowing into the outdoor heat exchanger 104 or the indoor heat exchanger 106 by adjusting the opening degree. The indoor heat exchanger 106 exchanges heat between the indoor air and the refrigerant flowing inside the indoor heat exchanger 106. The indoor heat exchanger 106 functions as an evaporator or a condenser depending on the flow direction of the refrigerant. The refrigeration cycle apparatus 200 may have an outdoor blower (not shown) that sends outdoor air to the outdoor heat exchanger 104, or may have an outdoor blower (not shown) that sends indoor air to the indoor heat exchanger 106.

[0111] [Operation of the refrigeration cycle device 200] The refrigeration cycle apparatus 200 is an air conditioner, and the operation of the refrigeration cycle apparatus 200 when the air conditioner performs heating operation will be described. In the heating operation of the air conditioner, the flow path switching device 103 connects the pipes connected to the flow path switching device 103 to each other so as to form a circuit on the solid line side in FIG. 9.

[0112] The high-temperature, high-pressure refrigerant compressed by the compressor 100 flows into the indoor heat exchanger 106, where it condenses and liquefies, and after flowing out of the indoor heat exchanger 106, flows into the pressure reducing device 105, where it is throttled and becomes a low-temperature, low-pressure, two-phase gas-liquid state. The refrigerant throttled in the pressure reducing device 105 and becomes a low-temperature, low-pressure, two-phase gas-liquid state flows into the outdoor heat exchanger 104, where it evaporates and gasifies, flows out of the outdoor heat exchanger 104, passes through the flow switching device 103, and returns to the compressor 100 again.

[0113] When the refrigeration cycle device 200 is an air conditioner and the air conditioner performs heating operation, the refrigerant circulates through the refrigeration circuit 201 as indicated by the solid arrows in Fig. 9. This circulation of the refrigerant causes heat exchange between the outside air and the refrigerant in the outdoor heat exchanger 104, which is an evaporator, and the refrigerant sent to the outdoor heat exchanger 104 absorbs heat, and the refrigerant that has absorbed heat is sent to the indoor heat exchanger 106, which is a condenser, where it exchanges heat with the indoor air and warms the indoor air.

[0114] The refrigeration cycle apparatus 200 is an air conditioner, and the operation of the refrigeration cycle apparatus 200 when the air conditioner performs cooling operation will be described. In cooling operation of the air conditioner, the flow path switching device 103 connects the pipes connected to the flow path switching device 103 to each other so as to form a circuit on the dashed line side in FIG. 9.

[0115] The high-temperature, high-pressure refrigerant compressed by the compressor 100 flows into the outdoor heat exchanger 104, where it condenses and liquefies, and after flowing out of the outdoor heat exchanger 104, flows into the pressure reducing device 105, where it is throttled and becomes a low-temperature, low-pressure, two-phase gas-liquid state. The refrigerant throttled in the pressure reducing device 105 and becomes a low-temperature, low-pressure, two-phase gas-liquid state flows into the indoor heat exchanger 106, where it evaporates and gasifies, and after flowing out of the indoor heat exchanger 106, it passes through the flow switching device 103 and returns to the compressor 100 again.

[0116] When the refrigeration cycle apparatus 200 switches from heating operation to cooling operation, the indoor heat exchanger 106 switches from a condenser to an evaporator, and the outdoor heat exchanger 104 switches from an evaporator to a condenser. When the refrigeration cycle apparatus 200 is an air conditioner and the air conditioner performs cooling operation, the refrigerant circulates through the refrigeration circuit 201 as shown by the dashed arrow in Fig. 2. This circulation of the refrigerant causes heat exchange between the indoor air and the refrigerant in the indoor heat exchanger 106, which is an evaporator, and absorbs heat from the indoor air, i.e., cools the indoor air, and the refrigerant that has absorbed heat is sent to the outdoor heat exchanger 104, which is a condenser, where it exchanges heat with the outdoor air and releases heat to the outdoor air.

[0117] [Functions and Effects of the Refrigeration Cycle Apparatus 200] The refrigeration cycle apparatus 200 includes the compressor 100 according to the embodiment 1. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the compressor 100 according to the embodiment 1.

[0118] Embodiment 2 FIG. 10 is a schematic diagram showing the structure of the cylinder 23 in the compression mechanism 20 of the compressor 100 according to the second embodiment. FIG. 11 is a partial cross-sectional view showing the structure of the suction hole 40, the threaded hole 50, and the spring hole 60 in the cylinder 23 of the compressor 100 according to the second embodiment. FIG. 11 is a cross-sectional view taken along the line EE in FIG. Components having the same functions and actions as the stator 31 according to the first embodiment are given the same reference numerals and will not be described. The following description will focus on the differences between the second embodiment and the first embodiment, and the configurations not described in the second embodiment are the same as those in the first embodiment. The cylinder 23 according to the second embodiment differs from the cylinder 23 according to the first embodiment in the structure of the suction hole 40.

[0119] In the cylinder 23 according to the first embodiment, the suction hole 40 penetrates the cylinder 23 in the radial direction, but does not penetrate the cylinder 23 in the thickness direction. In the cylinder 23 according to the second embodiment, as shown in Figs. 10 and 11, a portion of the suction hole 40 penetrates the cylinder 23 in the thickness direction.

[0120] In the cylinder 23 according to the second embodiment, a suction groove 42 is formed in the suction hole inner diameter connecting portion 40b of the suction hole 40. More specifically, the cylinder 23 is formed with the suction groove 42 penetrating in the thickness direction of the cylinder 23 through the wall of the cylinder 23 between the suction hole inner diameter connecting portion 40b and at least one of the end faces of the cylinder 23 in the thickness direction of the cylinder 23.

[0121] The suction groove 42 forms a groove penetrating the cylinder 23 in the thickness direction, and is a through hole that communicates the suction hole inner diameter connection part 40b with the outside on the end face side of the cylinder 23. When the axial direction of the rotating shaft 21 is the up-down direction, the suction groove 42 is provided at the upper and lower parts of the suction hole inner diameter connection part 40b. In the cylinder 23 according to the second embodiment, the suction hole 40 penetrates the cylinder 23 in the thickness direction by the suction hole inner diameter connection part 40b, the suction groove 42 provided at the upper part of the suction hole inner diameter connection part 40b, and the suction groove 42 provided at the lower part of the suction hole inner diameter connection part 40b.

[0122] The suction groove 42 is formed to communicate with the cylinder chamber 23a, and is formed in a part of the suction hole inner diameter connection part 40b in the radial direction of the cylinder 23. The suction groove 42 is formed to extend from the inner peripheral wall 23e of the cylinder 23 to the outer peripheral wall 23f of the cylinder 23 in the radial direction of the cylinder 23. The suction groove 42 is not limited to being formed in a part of the suction hole inner diameter connection part 40b along the radial direction of the cylinder 23, but may be formed in the entire suction hole inner diameter connection part 40b along the radial direction of the cylinder 23. That is, the suction groove 42 may be formed in the suction hole inner diameter connection part 40b from the inner peripheral wall 23e of the cylinder 23 to the step part 41.

[0123] The dimension of the suction groove 42 in the width direction is 10 [mm]. That is, the dimension of the suction groove 42 in the circumferential direction of the cylinder 23 is 10 [mm]. As shown in FIG. 10 and FIG. 11, the dimension of the suction groove 42 in the width direction is smaller than the minor diameter of the suction hole inner diameter connecting part 40b, that is, the width of the suction hole inner diameter connecting part 40b in the circumferential direction of the cylinder 23. The dimension of the suction groove 42 in the depth direction is 5 [mm]. That is, the dimension of the suction groove 42 in the radial direction of the cylinder 23 is 5 [mm]. The depth of the suction groove 42 is the length of the suction groove 42 extending from the inner peripheral wall 23e of the cylinder 23 to the outer peripheral wall 23f side in the radial direction of the cylinder 23. Note that the above-mentioned dimensions of the cylinder 23 are one example, and are not limited to the above-mentioned dimensions of the cylinder 23.

[0124] The opening formed by the suction groove 42 penetrating the end face in the thickness direction of the cylinder 23 is blocked by the upper bearing 24 and the lower bearing 25. When the cylinder 23 is sandwiched between the upper bearing 24 and the lower bearing 25 and fastened together with the upper bearing 24 and the lower bearing 25 by the screw 80, the opening of the suction groove 42 formed in the cylinder 23 is blocked by the end faces of the upper bearing 24 and the lower bearing 25 on the cylinder 23 side. Therefore, even if the suction groove 42 is formed in the cylinder 23, the refrigerant does not leak outside the compression mechanism unit 20. That is, even if the suction hole inner diameter connection part 40b of the suction hole 40 is penetrated toward the end face of the cylinder 23, the refrigerant does not leak because it is blocked by the end face of the upper bearing 24 or the lower bearing 25. In addition, the end face of the upper bearing 24 or the lower bearing 25 forms a part of the flow path wall of the suction hole 40.

[0125] [Effects of Compressor 100] In the cylinder 23, an inlet groove 42 is formed penetrating the wall of the cylinder 23 between the inlet hole inner diameter connecting portion 40b and at least one of the end faces of the cylinder 23 in the thickness direction of the cylinder 23. By providing the inlet groove 42 in the inlet hole inner diameter connecting portion 40b of the cylinder 23, the compression mechanism unit 20 according to the second embodiment can further increase the area of ​​the inlet path compared to the compression mechanism unit 20 according to the first embodiment. Therefore, the compressor 100 according to the second embodiment can reduce pressure loss and improve compressor efficiency compared to a compressor not having this configuration.

[0126] [Functions and Effects of the Refrigeration Cycle Apparatus 200] The refrigeration cycle apparatus 200 includes the compressor 100 according to the second embodiment. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the compressor 100 according to the second embodiment.

[0127] Embodiment 3 Fig. 12 is a vertical cross-sectional view showing a schematic structure of the suction hole 40 portion of the compression mechanism 20 of the compressor 100 according to the third embodiment. In Fig. 12, the structure inside the cylinder chamber 23a is omitted in order to explain the structures of the cylinder 23, the upper bearing 24, and the lower bearing 25. Also, components having the same functions and actions as those of the compression mechanism 20 according to the first and second embodiments are denoted by the same reference numerals and their explanations are omitted. The following explanation will focus on the differences between the first and second embodiments and the third embodiment, and the configuration not explained in the third embodiment is the same as the first or second embodiment.

[0128] The compression mechanism part 20 according to the third embodiment differs from the compression mechanism part 20 according to the first and second embodiments in the structures of the upper bearing 24 and the lower bearing 25. The compression mechanism part 20 according to the third embodiment has a suction groove 42 formed in the cylinder 23, similar to the compression mechanism part 20 according to the second embodiment.

[0129] In the compression mechanism unit 20 according to the first and second embodiments, the shapes of the end faces of the upper bearing 24 and the lower bearing 25 on the cylinder 23 side are not specified. In the compression mechanism unit 20 according to the third embodiment, the upper bearing 24 has an end face groove 24a formed in its end face 24b on the cylinder 23 side. Also, in the compression mechanism unit 20 according to the third embodiment, the lower bearing 25 has an end face groove 25a formed in its end face 25b on the cylinder 23 side.

[0130] End face 24b of upper bearing 24 is an end face of upper blocking portion 24c formed in a plate shape on the cylinder 23 side. End face 24b of upper bearing 24 covers one end face of cylinder 23 in the axial direction of rotating shaft 21, and closes one opening 23m of cylinder 23. End face 25b of lower bearing 25 is an end face of lower blocking portion 25c formed in a plate shape on the cylinder 23 side. End face 25b of lower bearing 25 covers the other end face of cylinder 23 in the axial direction of rotating shaft 21, and closes the other opening 23n of cylinder 23.

[0131] The end face groove 24a is formed on the end face 24b of the upper blocking portion 24c and is formed in a groove-like recessed shape. The end face groove 24a is a non-through hole and opens to the cylinder 23 side in the compression mechanism section 20. The end face groove 24a is formed so as to communicate with at least a part of the suction groove 42 formed in the upper part of the cylinder 23. The end face groove 24a forms a space integral with the suction groove 42 formed in the upper part of the cylinder 23. The end face groove 24a is formed so as to extend in the radial direction of the cylinder 23 along the suction groove 42 formed in the upper part of the cylinder 23.

[0132] The end face groove 25a is formed on the end face 25b of the lower blocking portion 25c and is formed in a groove-like recessed shape. The end face groove 25a is a non-through hole and opens to the cylinder 23 side in the compression mechanism section 20. The end face groove 25a is formed so as to communicate with at least a part of the suction groove 42 formed in the lower part of the cylinder 23. The end face groove 25a forms a space integral with the suction groove 42 formed in the lower part of the cylinder 23. The end face groove 25a is formed so as to extend in the radial direction of the cylinder 23 along the suction groove 42 formed in the lower part of the cylinder 23.

[0133] The end face groove 24a and the end face groove 25a are formed at positions where the axial end face of the rolling piston 22 does not pass when the rolling piston 22 moves in accordance with the rotation of the rotating shaft 21. Note that only one of the end face groove 24a and the end face groove 25a may be formed.

[0134] The dimension of the end face groove 24a in the width direction is 10 [mm]. That is, the dimension of the end face groove 24a in the circumferential direction of the cylinder 23 is 10 [mm]. Similarly, the dimension of the end face groove 25a in the width direction is 10 [mm]. That is, the dimension of the end face groove 25a in the circumferential direction of the cylinder 23 is 10 [mm].

[0135] The radial dimension of the end face groove 24a in the radial direction of the cylinder 23 is 4 [mm]. In addition, the depth dimension of the end face groove 24a in the axial direction of the rotating shaft 21 is 3 [mm]. Similarly, the radial dimension of the end face groove 25a in the radial direction of the cylinder 23 is 4 [mm]. In addition, the depth dimension of the end face groove 25a in the axial direction of the rotating shaft 21 is 3 [mm]. Note that the above-mentioned dimensions of the cylinder 23 are only an example, and are not limited to the above-mentioned dimensions of the cylinder 23. For example, the radial dimension of the end face groove 24a in the radial direction of the cylinder 23 and the depth dimension of the end face groove 24a in the axial direction of the rotating shaft 21 may be the same length. Similarly, the radial dimension of the end face groove 25a in the radial direction of the cylinder 23 and the depth dimension of the end face groove 25a in the axial direction of the rotating shaft 21 may be the same length.

[0136] [Effects of Compressor 100] In the compression mechanism section 20 according to the third embodiment, the end face groove 24a is formed so as to communicate with at least a part of the suction groove 42 formed in the upper part of the cylinder 23, and the end face groove 25a is formed so as to communicate with at least a part of the suction groove 42 formed in the lower part of the cylinder 23. The compression mechanism section 20 according to the third embodiment has this configuration, and thus can further increase the flow path area through which the refrigerant flowing into the cylinder chamber 23a passes, compared to the compression mechanism section 20 according to the second embodiment. Therefore, the compressor 100 according to the third embodiment can reduce pressure loss and improve compressor efficiency, compared to a compressor not having this configuration.

[0137] [Functions and Effects of the Refrigeration Cycle Apparatus 200] The refrigeration cycle apparatus 200 includes the compressor 100 according to the embodiment 3. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the compressor 100 according to the embodiment 3.

[0138] Embodiment 4 Fig. 13 is a vertical cross-sectional view showing a schematic structure of the suction hole 40 portion of the compression mechanism 20 of the compressor 100 according to the fourth embodiment. Note that Fig. 13 omits the illustration of the structure inside the cylinder chamber 23a in order to explain the structures of the cylinder 23, the upper bearing 24, and the lower bearing 25. Also, components having the same functions and actions as those of the compression mechanism 20 according to the first to third embodiments are given the same reference numerals and their explanations are omitted. The following description will focus on the differences between the first to third embodiments and the fourth embodiment, and the configurations not explained in the fourth embodiment are the same as those in the first to third embodiments.

[0139] The third embodiment has been described with reference to the case where the compression mechanism unit 20 is a single rotary compressor having one cylinder 23, whereas the fourth embodiment will be described with reference to the case where the compression mechanism unit 20 is a twin rotary compressor having two cylinders 23. The compression mechanism unit 20 according to the fourth embodiment has the same structures as the compression mechanism unit 20 according to the third embodiment in terms of the cylinder 23, the upper bearing 24, and the lower bearing 25.

[0140] The compression mechanism unit 20 according to the fourth embodiment has a suction groove 42 formed in the cylinder 23, similar to the compression mechanism unit 20 according to the third embodiment. Moreover, in the compression mechanism unit 20 according to the fourth embodiment, an end face groove 24a is formed in an end face 24b of the upper bearing 24 on the cylinder 23 side. Moreover, in the compression mechanism unit 20 according to the fourth embodiment, an end face groove 25a is formed in an end face 25b of the lower bearing 25 on the cylinder 23 side.

[0141] End face 24b of upper bearing 24 covers one end face of cylinder 23 in the axial direction of rotating shaft 21, and closes opening 23m of cylinder 23 positioned above cylinder 23 on the side where upper bearing 24 is arranged. End face 25b of lower bearing 25 covers one end face of cylinder 23 in the axial direction of rotating shaft 21, and closes opening 23n of cylinder 23 positioned below cylinder 23 on the side where lower bearing 25 is arranged.

[0142] The compression mechanism section 20 according to the fourth embodiment has two cylinders 23. The compression mechanism section 20 according to the fourth embodiment is disposed between the two cylinders 23 and has an intermediate plate 28 that closes the cylinder chamber 23a. Note that, although a twin rotary compressor having two cylinders 23 in the compression mechanism section 20 is described in Fig. 13, the number of cylinders 23 constituting the compression mechanism section 20 according to the fourth embodiment is not limited to two, and may be three or more.

[0143] The intermediate plate 28 is formed in a plate shape. The plate surface 28a of the intermediate plate 28 covers the other end faces of the cylinders 23 in the axial direction of the rotating shaft 21, and closes the opening 23n of the cylinder 23 arranged above the intermediate plate 28 on the side where the lower bearing 25 is arranged. The plate surface 28b of the intermediate plate 28 covers the other end faces of the cylinders 23 in the axial direction of the rotating shaft 21, and closes the opening 23m of the cylinder 23 arranged below the intermediate plate 28 on the side where the upper bearing 24 is arranged.

[0144] In the intermediate plate 28, a groove-shaped recessed intermediate plate groove 28a1 is formed on a plate surface 28a facing the cylinder 23 arranged above the intermediate plate 28, i.e., on the plate surface 28a on the side where the upper bearing 24 is arranged. In addition, in the intermediate plate 28, a groove-shaped recessed intermediate plate groove 28b1 is formed on a plate surface 28b facing the cylinder 23 arranged below the intermediate plate 28, i.e., on the plate surface 28b on the side where the lower bearing 25 is arranged.

[0145] The intermediate plate groove 28a1 is formed in the plate surface 28a of the intermediate plate 28 and is formed in a groove-like recessed shape. The intermediate plate groove 28a1 is a non-through hole and opens to the side where the upper bearing 24 is arranged in the compression mechanism section 20. The intermediate plate groove 28a1 is formed so as to communicate with at least a part of the suction groove 42 formed in the lower part of the cylinder 23 arranged above the intermediate plate 28. The intermediate plate groove 28a1 forms a space integral with the suction groove 42 formed in the lower part of the cylinder 23 arranged above the intermediate plate 28. The intermediate plate groove 28a1 is formed so as to extend in the radial direction of the cylinder 23 along the suction groove 42 formed in the lower part of the cylinder 23 arranged above the intermediate plate 28.

[0146] The intermediate plate groove 28b1 is formed in the plate surface 28b of the intermediate plate 28 and is formed in a groove-like recessed shape. The intermediate plate groove 28b1 is a non-through hole and opens to the side where the lower bearing 25 is arranged in the compression mechanism section 20. The intermediate plate groove 28b1 is formed so as to communicate with at least a part of the suction groove 42 formed in the upper part of the cylinder 23 arranged below the intermediate plate 28. The intermediate plate groove 28b1 forms a space integral with the suction groove 42 formed in the upper part of the cylinder 23 arranged below the intermediate plate 28. The intermediate plate groove 28b1 is formed so as to extend in the radial direction of the cylinder 23 along the suction groove 42 formed in the upper part of the cylinder 23 arranged below the intermediate plate 28.

[0147] The intermediate plate groove 28a1 and the intermediate plate groove 28b1 are formed at positions where the axial end face of the rolling piston 22 does not pass when the rolling piston 22 moves in accordance with the rotation of the rotating shaft 21. Note that only one of the intermediate plate groove 28a1 and the intermediate plate groove 28b1 may be formed.

[0148] [Effects of Compressor 100] The compression mechanism section 20 according to the fourth embodiment is formed so that the intermediate plate groove 28a1 communicates with at least a part of the suction groove 42 formed in the lower part of the cylinder 23 arranged above the intermediate plate 28. Also, the compression mechanism section 20 according to the fourth embodiment is formed so that the intermediate plate groove 28b1 communicates with at least a part of the suction groove 42 formed in the upper part of the cylinder 23 arranged below the intermediate plate 28. By having this configuration, the compression mechanism section 20 according to the fourth embodiment can further increase the flow path area through which the refrigerant flowing into the cylinder chamber 23a passes, compared to a compressor not having this configuration. Therefore, the compressor 100 according to the fourth embodiment can reduce pressure loss and improve compressor efficiency, compared to a compressor not having this configuration.

[0149] [Functions and Effects of the Refrigeration Cycle Apparatus 200] The refrigeration cycle apparatus 200 includes the compressor 100 according to the fourth embodiment. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the compressor 100 according to the fourth embodiment.

[0150] The configurations shown in the above embodiments are merely examples, and may be combined with other known techniques, and parts of the configurations may be omitted or modified without departing from the spirit of the invention. The configurations shown in the embodiments may be appropriately combined with multiple components disclosed in the above embodiments.

[0151] For example, in the first to third embodiments, the center of the suction hole outer diameter connection part 40a coincides with the center of the cylinder 23 in the thickness direction in the axial direction of the rotary shaft 21. However, in the case where the compressor 100 is a twin rotary compressor like the compressor 100 according to the fourth embodiment, if the distance between the suction holes 40 of the two cylinders 23 is too close, the pressure resistance of the sealed container 10 decreases. Therefore, the center of the suction holes 40 of the two cylinders 23 may be offset toward the bearing side with which the cylinder 23 abuts, that is, in the direction away from the other suction hole 40. With this configuration, it is possible to obtain the same effect as the compressor 100 according to the first to third embodiments.

[0152] In the compressors 100 according to the first to fourth embodiments, it is necessary to suppress assembly distortion caused by driving in the refrigerant suction pipe 107 connected to the cylinder 23. Therefore, in the compressors 100 according to the first to fourth embodiments, it is necessary to ensure a specific thickness for the first thin-walled portion 23g that constitutes a wall between the end face of the cylinder 23 and the suction hole 40. On the other hand, when the plate thickness of the sealed container 10 is thin, it may be possible to ensure a larger suction path by offsetting the center of the suction hole 40 due to the constraints on the strength of the sealed container 10. In this case, for example, in the cylinder 23 according to the first embodiment, the suction hole 40 may be offset toward the bearing side by 0.5 mm at a time.

[0153] Considering the decrease in efficiency of compressor 100 due to pressure loss of the refrigerant flow, it is desirable for the flow path area of ​​each suction hole 40 to be as large as possible when compressor 100 is a twin rotary type having two cylinders 23. However, due to structural constraints, compressor 100 needs to offset suction hole 40 toward the bearing side to maximize the flow path area of ​​suction hole 40 while avoiding structural constraints.

[0154] Here, when the compressor 100 is a twin rotary type compressor, the distance between the two suction holes 40 is referred to as the closest distance CD (see FIG. 13). If the closest distance CD is too short, the pressure resistance of the sealed container 10 (see FIG. 1) decreases, causing it to burst, so the closest distance CD needs to be a certain length. When the compressor 100 is a twin rotary type compressor, the compressor 100 can increase the closest distance CD between the two suction holes 40 by offsetting the upper cylinder 23 of the two cylinders 23 toward the upper bearing 24 and the lower cylinder 23 toward the lower bearing 25. If the opening diameter of the suction holes 40 is increased without offsetting the cylinders 23, the closest distance CD will be subject to the constraint of the wall thickness between the suction holes 40 required for the structure, and the compressor 100 will not be able to sufficiently increase the opening diameter of the suction holes 40.

[0155] Therefore, when the suction hole 40 is offset, the cylinder 23 is preferably formed so that the thickness t1 [mm] of the first thin-walled portion 23g is greater than the thickness t2 [mm] of the second thin-walled portion 23j (thickness t1>thickness t2). When the suction hole 40 is offset, the cylinder 23 is preferably formed so that the thickness t1 [mm] of the first thin-walled portion 23g is greater than the thickness t3 [mm] of the third thin-walled portion 23k (thickness t1>thickness t3). The cylinder 23 is preferably offset so that the suction hole 40 can be made as large as possible while satisfying the inequalities "thickness t1>thickness t2" and "thickness t1>thickness t3". [Explanation of symbols]

[0156] 10 sealed container, 11 upper container, 12 lower container, 20 compression mechanism, 21 rotating shaft, 21a main shaft, 21b eccentric shaft, 21c countershaft, 22 rolling piston, 22a outer peripheral wall, 23 cylinder, 23a cylinder chamber, 23b back pressure chamber, 23c vane groove, 23d opening, 23e inner peripheral wall, 23f outer peripheral wall, 23g first thin wall portion, 23h end face, 23j second thin wall portion, 23k third thin wall portion, 23m opening, 23n opening, 24 upper bearing, 24a end face groove, 24b end face, 24c upper blocking portion, 25 lower bearing, 25a end face groove, 25b end face, 25c lower blocking portion, 26 vane, 27 discharge muffler, 28 intermediate plate, 28a Plate surface, 28a1 intermediate plate groove, 28b plate surface, 28b1 intermediate plate groove, 30 motor section, 31 stator, 32 rotor, 33 lead wire, 34 refrigerant flow path, 40 suction hole, 40a suction hole outer diameter connection section, 40a1 inner peripheral wall, 40a2 suction hole outer diameter connection section, 40b suction hole inner diameter connection section, 40b1 inner peripheral wall, 41 step section, 42 suction groove, 50 screw hole, 60 spring hole, 61 spring hole cone section, 62 vane spring, 62a seat roll section, 62b seat roll section, 63 spring fixing section, 80 screw, 100 compressor, 101 suction muffler, 102 discharge pipe, 103 flow path switching device, 104 outdoor heat exchanger, 105 pressure reducing device, 106 Indoor heat exchanger, 107 refrigerant suction pipe, 200 refrigeration cycle device, 201 refrigeration circuit.

Claims

1. The compressor includes an electric motor unit, a rotating shaft having an eccentric shaft unit and driven to rotate by the electric motor unit, and a compression mechanism unit that compresses a refrigerant by a driving force transmitted from the electric motor unit via the rotating shaft, the compressor being disposed inside the sealed container. The compression mechanism includes: a cylindrical cylinder fixed to the sealed container and forming a cylinder chamber in a hollow portion; a rolling piston that is fitted to the eccentric shaft portion and accommodated in the cylinder chamber and rotates eccentrically together with the eccentric shaft portion to compress the refrigerant; a vane provided in a vane groove formed to extend in a radial direction of the cylinder and separating the cylinder chamber into a suction chamber and a compression chamber; a bearing provided on an end surface of the cylinder and closing the cylinder chamber; having The cylinder has a suction hole extending in a radial direction of the cylinder through which the refrigerant passes to be drawn into the cylinder chamber. The suction hole is a suction hole outer diameter connection portion that forms a space located on the radial outer periphery side of the cylinder; a suction hole inner diameter connection portion that forms a space located on a radially inner circumferential side of the cylinder; having a cross-sectional area of ​​the suction hole outer diameter connection portion in a cross section perpendicular to a radial direction of the cylinder is formed larger than a cross-sectional area of ​​the suction hole inner diameter connection portion in a cross section perpendicular to the radial direction of the cylinder, a cross-sectional shape of the suction hole inner diameter connection portion in a cross section perpendicular to a radial direction of the cylinder, the cross-sectional shape being such that an opening width in a circumferential direction of the cylinder is smaller than an opening width in a thickness direction of the cylinder, The cylinder includes: a suction groove is formed penetrating a wall of the cylinder between the suction hole inner diameter connection portion and at least one of the end faces of the cylinder in the thickness direction of the cylinder, the suction groove is formed to open to the radially inner circumferential side of the cylinder from the suction hole inner diameter connection portion in the thickness direction of the cylinder to an end face of the cylinder, The cylinder further includes a plurality of screws for fastening the bearing and the cylinder, The cylinder has a plurality of screw holes formed therein, the screw holes penetrating the cylinder in a thickness direction of the cylinder and into which the plurality of screws are respectively disposed, The cylinder is a first thin-walled portion that constitutes a part of the wall of the cylinder between the suction hole outer diameter connection portion and an end surface of the cylinder in a thickness direction; a second thin-walled portion which is a part of a wall constituting the cylinder and is a portion where a distance between the suction hole inner diameter connection portion and a screw hole among the plurality of screw holes which is located closest to the suction hole inner diameter connection portion is smallest in a circumferential direction of the cylinder; having a thickness t1 of the first thin-walled portion in a thickness direction of the cylinder is greater than a thickness t2 of the second thin-walled portion in a circumferential direction of the cylinder, The vane is further provided with a spring for biasing the vane so as to press a tip end of the vane against an outer peripheral wall of the rolling piston, The cylinder has a spring hole for arranging the spring therein, the spring hole extending in a radial direction of the cylinder. The cylinder is a third thin-walled portion which is a part of a wall constituting the cylinder and which is a portion where a distance between the suction hole inner diameter connection portion and the spring hole is smallest in a circumferential direction of the cylinder, A compressor, wherein a thickness t1 of the first thin-walled portion is formed larger than a thickness t3 of the third thin-walled portion in a circumferential direction of the cylinder.

2. 2. The compressor according to claim 1, wherein a cross-sectional shape of the suction hole outer diameter connection portion in a cross section perpendicular to the radial direction of the cylinder is circular, and a cross-sectional shape of the suction hole inner diameter connection portion in a cross section perpendicular to the radial direction of the cylinder is non-circular.

3. 3. The compressor according to claim 1, wherein a cross-sectional shape of the suction hole inner diameter connection portion in a cross section perpendicular to a radial direction of the cylinder is an elliptical shape whose length in a thickness direction of the cylinder is longer than its circumferential direction.

4. The bearing has an end face groove formed on an end face on the cylinder side, The compressor according to any one of claims 1 to 3, wherein the end face groove is formed so as to communicate with at least a part of the suction groove formed in the cylinder, and is formed at a position where an end face of the rolling piston does not pass through when the rolling piston moves in association with rotation of the rotating shaft.

5. The cylinder includes two cylinders. an intermediate plate disposed between the two cylinders and closing the cylinder chamber; The intermediate plate has an intermediate plate groove formed on the plate surface facing the cylinder, The compressor according to any one of claims 1 to 4, wherein the intermediate plate groove is formed so as to communicate with at least a part of the suction groove formed in the cylinder, and is formed at a position where an end face of the rolling piston does not pass when the rolling piston moves in association with the rotation of the rotating shaft.

6. A compressor according to any one of claims 1 to 5; an outdoor heat exchanger that exchanges heat between outdoor air and a refrigerant flowing therein; an indoor heat exchanger that exchanges heat between indoor air and a refrigerant flowing therein; a pressure reducing device that reduces the pressure of the refrigerant flowing into the outdoor heat exchanger or the indoor heat exchanger; A refrigeration cycle device comprising:

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