JP7634716B2 - Compressor and refrigeration cycle device - Google Patents

Description

The present disclosure relates to a compressor that compresses and discharges a refrigerant and a refrigeration cycle device equipped with the compressor, and in particular to a suction mechanism that forms a refrigerant path to a compression chamber.

A conventional rotary compressor is equipped with 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 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 through the refrigeration cycle device to achieve the desired refrigeration capacity is increased. 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.

JP 2013-139726 A

In a rotary compressor, the pressure loss of the suction refrigerant is reduced when the suction hole of the cylinder is enlarged. However, threaded holes and spring holes are generally formed around the suction hole of the cylinder of a rotary compressor. The threaded holes are holes for placing screws to fasten the components that make up the compression mechanism together, and the spring holes are holes for placing springs that operate vanes that separate the high-pressure chamber and the low-pressure chamber within the compression mechanism. Interference between the suction hole and the threaded hole, or between the suction hole and the spring hole, restricts the enlargement of the suction hole, making it impossible to secure a sufficient flow area for the suction hole, which may reduce the efficiency of the compressor under operating conditions using a high flow rate refrigerant.

The present disclosure is intended to solve the problems described above, 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.

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 in a radial direction of the cylinder and separates the cylinder chamber into a suction chamber and a compression chamber, and a bearing that is provided on an end surface of the cylinder and closes the cylinder chamber. The cylinder has 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 has a suction hole outer diameter connection part which forms a space located on the radially outer periphery side of the cylinder, and a suction hole inner diameter connection part which forms a space located on the radially inner periphery side of the cylinder, and the cross-sectional area of the suction hole outer diameter connection part in a cross section perpendicular to the radial direction of the cylinder is formed larger than the cross-sectional area of the suction hole inner diameter connection part in a cross section perpendicular to the radial direction of the cylinder, and the cross-sectional shape of the suction hole inner diameter connection part in the cross section perpendicular to the radial direction of the cylinder 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 , and the cylinder has a wall between the suction hole inner diameter connection part and at least one of the end faces of the cylinder in the thickness direction of the cylinder, the wall having a suction hole inner diameter connection part which penetrates in the thickness direction of the cylinder. a suction groove is formed in the cylinder, the suction groove is formed so as to open to the radially inner periphery of the cylinder from the suction hole inner diameter connection part in the thickness direction of the cylinder to the end face of the cylinder, and the bearing further has a plurality of screws for fastening the bearing and the cylinder, the cylinder is formed with a plurality of screw holes penetrating the cylinder in the thickness direction of the cylinder and in which the plurality of screws are respectively arranged, and the cylinder is a portion where the distance between the suction hole outer diameter connection part and the end face of the cylinder in the thickness direction of the cylinder is smallest in the circumferential direction of the cylinder, the portion being a part of the wall constituting the cylinder, a second thin-walled portion, wherein a thickness t1 of the first thin-walled portion in the thickness direction of the cylinder is formed larger than a thickness t2 of the second thin-walled portion in the circumferential direction of the cylinder, and further comprising a spring for biasing the vane so as to press the tip of the vane against the outer peripheral wall of the rolling piston, and a spring hole for arranging the spring is formed in the cylinder so as to extend in the radial direction of the cylinder, and the cylinder further comprises a third 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 spring hole is smallest in the circumferential direction of the cylinder, and wherein a thickness t1 of the first thin-walled portion is formed larger than a thickness t3 of the third thin-walled portion in the circumferential direction of the cylinder .

The refrigeration cycle device according to the present disclosure includes a compressor according to the present disclosure, an outdoor heat exchanger that exchanges heat between outdoor air and the refrigerant flowing inside, an indoor heat exchanger that exchanges heat 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.

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, thereby reducing 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 at an earlier timing 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.

1 is a vertical sectional view of a compressor according to a first embodiment. FIG. 1 is a cross-sectional view that shows a schematic cross section of a compression mechanism of a compressor according to a first embodiment of the present invention. 2 is a schematic diagram showing the structure of a cylinder in a compression mechanism of the compressor according to the first embodiment; FIG. 4 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. 4 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. 2 is a side view showing a schematic structure of a suction hole in a compression mechanism of the compressor according to the first embodiment; FIG. 2 is a vertical cross-sectional view showing a schematic structure of a suction hole portion in a compression mechanism of the compressor according to the first embodiment. FIG. 3 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. 1 is a configuration diagram of a refrigeration cycle device including a compressor according to a first embodiment. 10 is a schematic diagram showing the structure of a cylinder in a compression mechanism of a compressor according to a second embodiment of the present invention; FIG. 10 is a partial cross-sectional view showing a schematic structure of a suction hole, a threaded hole, and a spring hole in a cylinder of a compressor according to a second embodiment. FIG. 11 is a longitudinal sectional view showing a schematic structure of a suction hole portion in a compression mechanism of a compressor according to a third embodiment. FIG. 13 is a longitudinal sectional view showing a schematic structure of a suction hole portion in a compression mechanism of a compressor according to a fourth embodiment of the present invention. FIG.

The compressor and refrigeration cycle device according to the embodiment will be described below with reference to the drawings. Note that in the following drawings, including FIG. 1, the relative dimensional relationships and shapes of the components may differ from the actual ones. In addition, in the following drawings, the same reference numerals are used to denote the same or equivalent objects, and this applies throughout the entire specification. In addition, to facilitate understanding, directional terms (e.g., "up," "down," "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 or orientation of the device or parts.

Embodiment 1.
[Configuration of compressor 100]
Fig. 1 is a vertical cross-sectional view of a compressor 100 according to embodiment 1. 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.

For example, a one-cylinder type rotary compressor having one cylinder 23 as shown in FIG. 1, i.e., a single rotary compressor, is used for the compressor 100. The compressor 100 is not limited to a single rotary compressor, and may be a rotary compressor having multiple cylinders 23. For example, a twin rotary compressor having two cylinders 23 or other structures may be used for the compressor 100. In particular, in a compressor that flows a high flow rate of refrigerant, it is necessary to effectively reduce the pressure loss in the suction path of the refrigerant. Therefore, a twin rotary compressor that requires a high flow rate and high capacity may be used as the compressor 100.

(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.

On the outside of the sealed container 10, a suction muffler 101 is provided 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 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 liquid refrigerant flows into the cylinder of the compression mechanism and is compressed by the compression mechanism, it may cause the compression mechanism to malfunction.

The 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 sucked into the compression mechanism 20 as much as possible, i.e., to send only the refrigerant gas to the cylinder chamber 23a. The suction muffler 101 is connected via the refrigerant suction pipe 107 and the suction hole 40 of the cylinder 23 (see Figure 3), and the low-pressure refrigerant gas sent from the suction muffler 101 is sucked into the cylinder chamber 23a via the refrigerant suction pipe 107. The suction muffler 101 also serves as a muffler to reduce or eliminate noise generated by the flowing refrigerant.

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.

The compressor 100 has, 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 using the 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.

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.

The inside of the sealed container 10 is filled with high-temperature, high-pressure refrigerant gas compressed by the compression mechanism 20, and refrigeration oil used to lubricate the compression mechanism 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 20. An oil pump (not shown) is provided at the bottom of 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 20. The compression mechanism 20 ensures mechanical lubrication by supplying oil to each sliding part.

(Motor section 30)
The electric motor unit 30 is an electric motor disposed within 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.

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

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 guided to the top of the sealed container 10 together with the refrigerant gas to the bottom of the sealed container 10.

The rotating shaft 21 is fixed to the rotor 32 at the center of the rotor 32, passing through the rotor 32 in the axial direction. The rotating shaft 21 transmits the rotational driving force of the rotor 32 to the compression mechanism 20. The inner diameter of the iron core constituting the rotor 32 is smaller than the outer diameter of the rotating shaft 21, and the iron core of the rotor 32 is fixed to the main shaft portion 21a of the rotating shaft 21.

(Rotation shaft 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 order of the main shaft portion 21a, the eccentric shaft portion 21b, and the counter shaft portion 21c in the axial direction from the top to the bottom of 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.

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

(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 line A-A in Fig. 1 and viewed from the top. In Fig. 2, in order to explain the basic structure of the compression mechanism 20, an intake hole 40, a screw hole 50, a spring hole 60, etc., which will be described later, are omitted. The basic structure of the compression mechanism 20 will be explained using Fig. 2.

The compression mechanism unit 20 is driven by the electric motor unit 30 and compresses the refrigerant gas sucked in 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.

As shown in Figures 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.

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 is open at both ends in the axial direction of the rotating shaft 21, 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 circumferential surface of the cylinder 23, the inner wall surface of the upper bearing 24, and the inner wall surface of the lower bearing 25.

The cylinder chamber 23a contains an eccentric shaft portion 21b of the rotating 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 divides the space formed by the inner peripheral wall 23e that forms the cylinder chamber 23a and the outer peripheral wall 22a of the rolling piston 22 is contained within the cylinder chamber 23a.

In the compression mechanism 20, one end of the vane 26, which reciprocates radially in a groove provided in the cylinder 23, abuts against the outer peripheral wall 22a of the rolling piston 22, and the vane 26 separates 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.

The cylinder 23 has a suction hole 40 (see FIG. 3) through which the refrigerant gas sucked into the cylinder chamber 23a from the outside of the sealed container 10 passes. The cylinder 23 has a suction hole 40 through which the refrigerant gas supplied from the refrigerant suction pipe 107 passes, penetrating from the outer peripheral surface to the inner peripheral surface of the cylinder 23, 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.

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 inside of the rolling piston 22 is slidably fitted with the eccentric shaft portion 21b of the rotating shaft 21.

The vane 26 is provided in a vane groove 23c formed to extend radially 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.

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 countershaft portion 21c of the rotating shaft 21 and rotatably supports the countershaft portion 21c. The lower bearing 25 is provided on the end face of the cylinder 23 opposite 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.

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 out of the cylinder chamber 23a.

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 from the cylinder 23 through the discharge port. The discharge valve closes until the refrigerant gas compressed in the cylinder chamber 23a of the cylinder 23 reaches a predetermined pressure, and when the refrigerant gas reaches or exceeds the predetermined pressure, the valve opens to discharge the high-temperature, high-pressure refrigerant gas out of the cylinder chamber 23a.

In the cylinder chamber 23a, the refrigerant is repeatedly sucked in, compressed, and discharged, and the refrigerant gas is intermittently discharged from the discharge port, which may cause noise such as pulsating sounds to be generated from the cylinder 23. To reduce such noise, a discharge muffler 27 is attached to the outside of the upper bearing 24, which is the side where the electric motor unit 30 is located, so as to cover the upper bearing 24.

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

(Detailed Structure of Cylinder 23)
FIG. 3 is a schematic diagram showing the structure of the cylinder 23 in the compression mechanism 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 as viewed from the circumferential direction of the cylinder 23 of the compression mechanism 20 according to the first embodiment. FIG. 4 is a schematic cross-sectional view of the compression mechanism 20 cut along the line H-H in FIG. 5 and the cylinder 23 as viewed in the circumferential direction. FIG. 5 is a conceptual diagram of the vane groove 23c and the spring hole 60 as viewed from the radial direction of the cylinder 23 of the compression mechanism 20 according to the first embodiment. FIG. 5 is a schematic cross-sectional view of the compression mechanism 20 cut along the line G-G in FIG. 4 and the cylinder 23 as viewed in the radial direction. Note that in FIGS. 3 to 5, the vanes 26 are omitted in order to explain the structure of the vane groove 23c and the spring hole 60. The structure of the cylinder 23 will be explained in more detail with reference to FIGS. 2 to 4.

The cylinder 23 is formed with a vane groove 23c that communicates with the cylinder chamber 23a and extends in the radial direction of the cylinder 23 centered on the rotating shaft 21. The vane groove 23c has an opening 23d formed at one end located on the inner periphery of the cylinder 23, and a back pressure chamber 23b formed at the other end located on the outer periphery of the cylinder 23. The opening 23d is provided in the inner periphery wall 23e of the cylinder 23 and opens into the cylinder chamber 23a.

The vane groove 23c is a groove that penetrates the inner diameter side of the cylinder 23 and communicates with the cylinder chamber 23a, but does not penetrate the outer diameter side of the cylinder 23. Also, the vane groove 23c is a groove that penetrates from the front side to the back side when the cylinder 23 is viewed from the front, that is, when viewed from the 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.

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 process, 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, with the tip of the vane 26 remaining 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.

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 to limit 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.

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 part 63. In the spring fixing part 63, the seat winding part 62a of the vane spring 62 is pressed 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 winding part 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.

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, the high-pressure refrigerant gas in the sealed container 10 flows into the back pressure chamber 23b, and 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 creates a force that moves the vane 26 radially toward the center of 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.

The force that moves the vane 26 radially causes one end of the vane 26, i.e., the end on the cylinder chamber 23a side, to abut against the outer peripheral wall 22a of the cylindrically formed rolling piston 22. As a result, the vane 26 can separate the space formed by the inner peripheral wall 23e of the cylinder 23 and the outer peripheral wall 22a of the rolling piston 22, as described above.

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.

(Suction hole 40)
FIG. 6 is a side view showing the 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 showing the 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 showing the 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 is a view of 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 D-D 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 using FIG. 3 to FIG. 8.

3 and 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. Note that 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 in FIG. 6.

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.

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

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 the suction hole outer diameter connection part 40a and connected to the refrigerant suction pipe 107. 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.

As shown in Figure 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 Figure 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 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.

In other words, 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 an ellipse whose length in the thickness direction of the cylinder 23 is longer than in the circumferential direction of the cylinder 23. In the cylinder 23, the 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 is circular, and 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 non-circular.

The cross-sectional shape of the suction hole inner diameter connection part 40b is not limited to an elliptical shape. The cross-sectional shape of the suction hole inner diameter connection 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 connection part 40b is an ellipse, the major axis direction of the suction hole inner diameter connection part 40b coincides with the thickness direction of the cylinder 23.

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 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 an ellipse, 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 a cross section perpendicular to the radial direction of the cylinder 23 may be non-circular, and 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 may be non-circular.

In the compression mechanism 20, the long diameter direction in 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 completed is earlier than when it is a perfect circle with the same diameter as the long diameter of the suction hole inner diameter connection part 40b.

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 those 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.

The long diameter of the suction hole inner diameter connection part 40b formed in an oval shape in a cross section perpendicular to the radial direction of the cylinder 23 is 18 mm, and the short diameter is 15 mm. The thickness t1 of the first thin wall part 23g of the cylinder 23 formed by this is 2 mm. The first thin wall part 23g is a wall part of the cylinder 23 that constitutes a part of the suction hole outer diameter connection part 40a, and is a part that constitutes a part of the wall of the cylinder 23 between the suction hole outer diameter connection part 40a and the end face 23h in the thickness direction of the cylinder 23. The thickness t1 of the first thin wall part 23g is the distance between the suction hole outer diameter connection part 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.

The first thin-walled portion 23g is a portion of the cylinder 23 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 end face 23h of the cylinder 23 is the axial end face of the cylinder 23, and is the end face of the cylinder 23 on which the upper bearing 24 or the lower bearing 25 is disposed.

In the cylinder 23, the diameter of the suction hole outer diameter connection part 40a differs from the diameter of the suction hole inner diameter connection part 40b 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. Inside the suction hole 40, the step part 41 faces the outer periphery of the cylinder 23, and constitutes the 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.

The suction hole 40 of the cylinder 23 has a representative dimension of the suction hole outer diameter connection part 40a that 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 process 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 easily processed, and manufacturing costs can be reduced.

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, if 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.

The diameter of the suction hole outer diameter connection 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 connection 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 connection part 40a and the suction hole inner diameter connection part 40b are formed to a constant dimension from the inner circumference side to the outer circumference side in the radial direction. The suction hole outer diameter connection part 40a forms a cylindrical space S1, and the suction hole inner diameter connection 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.

However, the cylinder 23 is not limited to one in which the diameters of the suction hole outer diameter connection part 40a and the suction hole inner diameter connection part 40b are formed to be constant from the inner circumference side to the outer circumference side in the radial direction. The cylinder 23 may have a different diameter of the suction hole outer diameter connection part 40a from the inner circumference side to the outer circumference side in the radial direction as long as the cylinder 23 has a step part 41 inside the suction hole 40. Also, the cylinder 23 may have a different diameter of the suction hole inner diameter connection part 40b from the inner circumference side to the outer circumference side in the radial direction as long as the cylinder 23 has a step part 41 inside the suction hole 40.

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 and the center in the thickness direction of the cylinder 23 do not have to coincide with each other in the axial direction of the rotating shaft 21.

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). The compression mechanism 20 forms a cylindrical cylinder chamber 23a with the cylinder 23 forming the side of the compression chamber and the two bearings forming the end faces of the compression chamber. The compression mechanism 20 also 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.

(Screw hole 50)
Next, the screw holes 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.

As described above, the cylinder 23 has screws 80 for fastening the cylinder 23, the upper bearing 24, and the lower bearing 25, and threaded holes 50 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.

As shown in Fig. 3, multiple screw holes 50 are formed along the circumferential direction of the cylinder 23. In the cylinder 23 according to the first embodiment, six screw holes 50 are formed along 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 screw 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.

In a rotary compressor, the screws 80 for fastening the cylinder 23, upper bearing 24, and lower bearing 25 are often arranged approximately evenly in the circumferential direction of the cylinder 23. In other words, when one circumference of the cylinder 23 in the circumferential direction is 360° around the center AX of the cylinder 23, the screws 80 are arranged at positions at angles that divide the 360° angle approximately evenly, and the screw holes 50 are formed.

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 to 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° from the center axis CS in the counterclockwise direction.

That is, when the central axis CS of the 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 positioned near the suction hole 40. The reason that the first screw 80 is positioned at approximately 30° from the central axis CS and is positioned near the suction hole 40 is that many operating parts are positioned around the vane groove 23c, and therefore the screw 80 cannot be positioned around the vane groove 23c.

In the cylinder 23 of the first embodiment, the suction hole 40 is formed so 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. In other words, the vane groove 23c and the suction hole 40 are formed in the cylinder 23 so 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.

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 screw hole 50 through which the screw 80 passes has a diameter of 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.

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. In addition, 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.

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 that constitutes 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.

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., in 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. In other words, 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.

The cylinder 23 is 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).

A copper or iron refrigerant suction pipe 107 is driven into the suction hole outer diameter connection 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 connection process of the refrigerant suction pipe 107.

In contrast, the suction hole inner diameter connection portion 40b of the suction hole 40 may be affected by the screw fastening from the threaded hole 50 into which the screw 80 for fastening the cylinder 23, etc. 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 manufacture.

The cross-sectional shape of the suction hole outer diameter connection part 40a is circular as described above. By making the suction hole outer diameter connection 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 molded individually at low cost, and the work of driving the piping into the cylinder 23 can be performed simply and easily.

However, this does not limit 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 like the suction hole inner diameter connection part 40b, or it may be an ellipse shape. Also, for example, the cross-sectional shape of the suction hole inner diameter connection part 40b may be a vertical oval shape that is long in the axial direction of the cylinder 23, while the suction hole outer diameter connection part 40a may be a horizontal oval shape that is long in the circumferential direction of the cylinder 23.

In the first embodiment, the portion forming the second thin portion 23j of the cylinder 23 is the 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 is formed, which is elliptical. 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 be enlarged in diameter without interfering with the threaded hole 50. Therefore, the compressor 100 can reduce pressure loss during refrigerant intake 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 enlarged.

(Spring hole 60)
The cylinder 23 includes 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 housing 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.

In the cylinder 23, a spring hole 60 for arranging the vane spring 62 is formed 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 outer diameter side of the cylinder 23 and does not penetrate the inner diameter side of the cylinder 23. In addition, the spring hole 60 is a hole whose cross section in a cross section perpendicular to the radial direction of the cylinder 23, that is, the direction in which the spring hole 60 extends, is a hole having a perfect circular shape. 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 in the radial direction of the cylinder 23.

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.

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 by deepening the depth of the spring hole 60, the design tolerance of the vane spring 62 that operates inside can be increased. The spring hole cone portion 61 is formed at the bottom of the spring hole 60 by the tip of a drill. The spring hole cone portion 61 is a space portion formed in a cone shape inside the cylinder 23. Note that 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]. 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.

If the depth of the spring hole 60 is not deep enough, the force pushing the vane 26 will be small, and the force with which the vane 26 follows the rolling piston 22 revolving inside the compression chamber will also be 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, high-pressure refrigerant leaks to the low-pressure refrigerant side, 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 by the stress generated when the vane 26 collides with the rolling piston 22, deteriorating reliability.

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 the 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 the portion where the distance between the suction hole inner diameter connection 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.

The thickness t3 [mm] of the third thin-walled portion 23k is expressed as the distance between the suction hole inner diameter connection 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 connection portion 40b of the suction hole 40 and the spring hole 60 is the smallest in the circumferential direction of the cylinder 23.

The cylinder 23 is 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).

As described above, the copper or iron refrigerant suction pipe 107 is driven into the suction hole outer diameter connection 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 connection process of the refrigerant suction pipe 107.

In response to this, the vane spring 62 may be lightly pressed into the spring hole 60 to fix it therein, 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 than the third thin-walled portion 23k during assembly of the compression mechanism 20, 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 t3 of the third thin-walled portion 23k, the compression mechanism 20 can suppress distortion of the cylinder 23 during manufacture.

The cross-sectional shape of the suction hole outer diameter connection part 40a is circular as described above. By making the suction hole outer diameter connection 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 molded individually at low cost, and the work of driving the piping into the cylinder 23 can be performed simply and easily.

In the first embodiment, the portion forming the third thin-walled portion 23k of the cylinder 23 is the portion between the spring hole 60 and the portion of the suction hole 40 whose cross section is formed in an elliptical shape. In other words, the portion of the suction hole 40 where the spring hole 60 is closest to the suction hole 40 is near 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 refrigerant intake 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 a screw hole 50 is formed near the suction hole outer diameter connection portion 40a.

[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, which is 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.

In the compressor 100, first, the suction chamber and the suction hole 40 are connected, and low-pressure refrigerant gas is sucked into the cylinder chamber 23a. Next, the rolling piston 22 closes the connection between the compression chamber in which the refrigerant gas is compressed and the suction hole 40, and the refrigerant gas in the compression chamber is compressed as the volume of the compression chamber decreases. Finally, the compression chamber is connected to the discharge port (not shown), and after the refrigerant gas in the compression chamber reaches a predetermined pressure, the 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.

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

[Functions and 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, in the compressor 100, the flow passage area of the refrigerant is increased as a whole in the suction hole 40 without expanding the radial inner circumferential side of the suction hole 40 in the circumferential direction of the cylinder 23, and the pressure loss of the refrigerant flow can be reduced. 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 at 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 of 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.

The cylinder 23 is 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. Since the refrigerant suction pipe 107 is driven into the suction hole outer diameter connection 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 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 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.

The cylinder 23 is 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. As described above, the refrigerant suction pipe 107 is driven into the suction hole outer diameter connection portion 40a of the cylinder 23, so that 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 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 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.

In addition, the cross-sectional shape of the suction hole outer diameter connection part 40a of the cylinder 23 in a cross section perpendicular to the radial direction of the cylinder 23 is circular, and 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 non-circular. Since suction pipes such as the refrigerant suction pipe 107 are often formed with 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 relatively more 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.

In addition, the cylinder 23 may have a non-circular cross-sectional shape of the suction hole outer diameter connection part 40a2 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 the cross-sectional shape of the suction hole outer diameter connection part 40a is non-circular, 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 connection part 40a non-circular, the refrigerant flow path area can be further expanded and pressure loss can be reduced. The non-circular 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 connection part 40a can be expanded without changing the thickness t1 of the first thin-walled part 23g. In other words, 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 connecting portion 40b side of the suction hole 40, and there is a comparatively large space at the suction hole outer diameter connecting portion 40a of the suction hole 40. Therefore, the suction hole outer diameter connecting portion 40a of the suction hole 40, which has a comparatively large space, can extend the flow passage cross-sectional shape of the suction hole 40 in the circumferential direction of the cylinder 23, thereby expanding the flow passage area.

In addition, 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 an ellipse whose length in the thickness direction of the cylinder 23 is longer than in the circumferential direction of the cylinder 23. By having a cylinder 23 with this structure, the compressor 100 can improve the volumetric efficiency of the compressor 100 by having the rolling piston 22 complete closing of the suction hole 40 earlier than in a conventional compressor in which all the suction holes are circular.

[Configuration of refrigeration cycle device 200]
9 is a configuration diagram of a refrigeration cycle apparatus 200 including a 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 and air conditioning apparatus, 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, and the pressure reducing device 105 are often mounted on an apparatus disposed outdoors.

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

The flow path switching device 103 is, for example, a four-way valve, and switches the direction in which the refrigerant flows. 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 direction in which the refrigerant flows. 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.

The pressure reducing device 105 is, for example, an electronic expansion valve that can adjust the aperture, and controls the pressure of the refrigerant flowing into the outdoor heat exchanger 104 or the indoor heat exchanger 106 by adjusting the aperture. 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 direction of the refrigerant flow. The refrigeration cycle device 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.

[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 .

The high-temperature, high-pressure refrigerant compressed by the compressor 100 flows into the indoor heat exchanger 106, where it condenses and liquefies. After flowing out of the indoor heat exchanger 106, it 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 that has been 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, and after flowing out of the outdoor heat exchanger 104, it passes through the flow switching device 103 and returns to the compressor 100 again.

When the refrigeration cycle device 200 is an air conditioner and the air conditioner is in heating operation, the refrigerant circulates through the refrigeration circuit 201 as shown by the solid arrows in Figure 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. 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.

The refrigeration cycle device 200 is an air conditioner, and the operation of the refrigeration cycle device 200 when the air conditioner is performing cooling operation will be described. When the air conditioner is performing cooling operation, the flow path switching device 103 connects the pipes connected to the flow path switching device 103 to form a circuit on the dashed line side of Figure 9.

The high-temperature, high-pressure refrigerant compressed by the compressor 100 flows into the outdoor heat exchanger 104, where it condenses and liquefies. After flowing out of the outdoor heat exchanger 104, it 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 that has been 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.

When the refrigeration cycle device 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 device 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 Figure 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.

[Effects of the refrigeration cycle device 200]
The refrigeration cycle apparatus 200 includes the compressor 100 according to the first embodiment. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the compressor 100 according to the first embodiment.

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 screw 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 E-E in FIG. 10. Components having the same functions and actions as the stator 31 according to the first embodiment are given the same reference numerals and their description is omitted. The following description will focus on the differences between the second embodiment and the first embodiment, and the configuration not described in the second embodiment is the same as that of the first embodiment. The cylinder 23 according to the second embodiment is different from the cylinder 23 according to the first embodiment in the structure of the suction hole 40.

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 Figures 10 and 11, a portion of the suction hole 40 penetrates the cylinder 23 in the thickness direction.

In the cylinder 23 according to the second embodiment, an intake groove 42 is formed in the intake hole inner diameter connection portion 40b of the intake hole 40. More specifically, the cylinder 23 is formed with an intake groove 42 that penetrates the wall of the cylinder 23 between the intake hole inner diameter connection portion 40b and at least one of the end faces of the cylinder 23 in the thickness direction of the cylinder 23 in the thickness direction.

The suction groove 42 is a through hole that forms a groove penetrating the cylinder 23 in the thickness direction and communicates the suction hole inner diameter connection part 40b with the outside of 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.

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 wall 23e of the cylinder 23 to the outer 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 from the inner wall 23e of the cylinder 23 to the step part 41 in the suction hole inner diameter connection part 40b.

The width dimension of the suction groove 42 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 width dimension of the suction groove 42 is smaller than the minor axis of the suction hole inner diameter connection part 40b, that is, the width of the suction hole inner diameter connection part 40b in the circumferential direction of the cylinder 23. The depth dimension of the suction groove 42 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 wall 23e of the cylinder 23 to the outer 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.

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 the cylinder 23 is 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 will not leak outside the compression mechanism 20. That is, even if the suction hole inner diameter connection part 40b of the suction hole 40 is penetrated in the direction of the end face of the cylinder 23, the refrigerant will 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.

[Effects of Compressor 100]
The cylinder 23 is formed with an inlet groove 42 penetrating the wall of the cylinder 23 between the inlet hole inner diameter connection part 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 at the inlet hole inner diameter connection part 40b of the cylinder 23, the compression mechanism part 20 according to the second embodiment can further increase the area of the inlet path compared to the compression mechanism part 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.

[Effects of the refrigeration cycle device 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.

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 description will focus on the differences between the first and second embodiments and the configurations not explained in the third embodiment are the same as those in the first or second embodiment.

The compression mechanism 20 according to the third embodiment differs from the compression mechanism 20 according to the first and second embodiments in the structure of the upper bearing 24 and the lower bearing 25. The compression mechanism 20 according to the third embodiment has an intake groove 42 formed in the cylinder 23, similar to the compression mechanism 20 according to the second embodiment.

In the compression mechanism 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 20 according to the third embodiment, the upper bearing 24 has an end face groove 24a formed in the end face 24b on the cylinder 23 side of the upper bearing 24. Also, in the compression mechanism 20 according to the third embodiment, the lower bearing 25 has an end face groove 25a formed in the end face 25b on the cylinder 23 side of the lower bearing 25.

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

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.

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.

The end face grooves 24a and 25a are formed at positions where the axial end faces of the rolling piston 22 do not pass through when the rolling piston 22 moves with the rotation of the rotating shaft 21. Note that only one of the end face grooves 24a and 25a may be formed.

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

The radial dimension of the end face groove 24a in the radial direction of the cylinder 23 is 4 mm. 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. 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.

[Functions and Effects of Compressor 100]
In the compression mechanism unit 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. By being provided with this configuration, the compression mechanism unit 20 according to the third embodiment can further increase the flow path area through which the refrigerant flowing into the cylinder chamber 23a passes, compared to the compression mechanism unit 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.

[Effects of the refrigeration cycle device 200]
The refrigeration cycle apparatus 200 includes the compressor 100 according to the third embodiment. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the compressor 100 according to the third embodiment.

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. In Fig. 13, 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 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.

In the third embodiment, the compression mechanism 20 is a single rotary compressor having one cylinder 23, but in the fourth embodiment, the compression mechanism 20 is a twin rotary compressor having two cylinders 23. The compression mechanism 20 according to the fourth embodiment has the same structure as the compression mechanism 20 according to the third embodiment in terms of the cylinder 23, upper bearing 24, and lower bearing 25.

The compression mechanism 20 according to the fourth embodiment has an intake groove 42 formed in the cylinder 23, similar to the compression mechanism 20 according to the third embodiment. In the compression mechanism 20 according to the fourth embodiment, the upper bearing 24 has an end face groove 24a formed in the end face 24b of the upper bearing 24 on the cylinder 23 side. In the compression mechanism 20 according to the fourth embodiment, the lower bearing 25 has an end face groove 25a formed in the end face 25b of the lower bearing 25 on the cylinder 23 side.

The end face 24b of the upper bearing 24 covers one end face of the cylinder 23 in the axial direction of the rotating shaft 21, and closes the opening 23m on the side of the upper bearing 24 of the cylinder 23 that is the upper of the two cylinders 23. The end face 25b of the lower bearing 25 covers one end face of the cylinder 23 in the axial direction of the rotating shaft 21, and closes the opening 23n on the side of the lower bearing 25 of the cylinder 23 that is the lower of the two cylinders 23.

The compression mechanism 20 according to the fourth embodiment has two cylinders 23. The compression mechanism 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 FIG. 13 describes a twin rotary compressor having two cylinders 23 in the compression mechanism 20, the number of cylinders 23 constituting the compression mechanism 20 according to the fourth embodiment is not limited to two, and may be three or more.

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

The intermediate plate 28 has a groove-shaped recessed intermediate plate groove 28a1 formed on the plate surface 28a on the side of the cylinder 23 arranged above the intermediate plate 28, i.e., the plate surface 28a on the side where the upper bearing 24 is arranged. The intermediate plate 28 also has a groove-shaped recessed intermediate plate groove 28b1 formed on the plate surface 28b on the side of the cylinder 23 arranged below the intermediate plate 28, i.e., the plate surface 28b on the side where the lower bearing 25 is arranged.

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.

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.

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 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.

[Functions and Effects of Compressor 100]
The compression mechanism 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. The compression mechanism 20 according to the fourth embodiment is also 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. The compression mechanism 20 according to the fourth embodiment is provided with this configuration, and thus 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.

[Effects of the refrigeration cycle device 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.

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

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 rotating shaft 21. However, when the compressor 100 is a twin rotary compressor, as in 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 will be reduced. Therefore, the center of the suction holes 40 of the two cylinders 23 may be offset toward the bearing side against which the cylinder 23 abuts, that is, in the direction away from the other suction hole 40. With this configuration, the same effect as the compressor 100 according to the first to third embodiments can be obtained.

In the compressor 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 compressor 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 the wall between the end face of the cylinder 23 and the suction hole 40. On the other hand, if 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 strength constraints 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 by 0.5 mm toward the bearing side.

Considering the decrease in efficiency of the 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 the compressor 100 is a twin rotary type having two cylinders 23. However, due to structural constraints, the compressor 100 needs to offset the suction hole 40 toward the bearing side to maximize the flow path area of the suction hole 40 while avoiding the structural constraints.

Here, when the compressor 100 is a twin rotary type compressor, the distance between the two suction holes 40 is called 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) will decrease and cause rupture, 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 expand the closest distance CD between the two suction holes 40 by offsetting the upper cylinder 23 of the two cylinders 23 to the upper bearing 24 side and the lower cylinder 23 to the lower bearing 25 side. If the opening diameter of the suction hole 40 is expanded without offsetting the cylinder 23, the closest distance CD will be caught by the constraint of the wall thickness between the suction holes 40 required for the structure, so the compressor 100 cannot sufficiently expand the opening diameter of the suction hole 40.

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 by the suction hole 40 so that the largest suction hole diameter can be secured while satisfying the inequalities "thickness t1 > thickness t2" and "thickness t1 > thickness t3".

10 sealed container, 11 upper container, 12 lower container, 20 compression mechanism, 21 rotating shaft, 21a main shaft, 21b eccentric shaft, 21c sub-shaft, 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 (6)

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 end surface of the cylinder in the thickness direction of the cylinder,
the suction groove is formed so as to open to a radially inner peripheral side of the cylinder from the suction hole inner diameter connection portion in a 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 formed larger 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. 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. 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. 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. 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. 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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