Compressor and refrigeration cycle apparatus

Abstract

This compressor is for compressing a refrigerant in a compression mechanism having a compression chamber and disposed inside a sealed container that is an outer shell. The compression mechanism comprises: a cylinder accommodated inside the sealed container; a rolling piston eccentrically rotating along an inner circumferential surface of the cylinder; a vane partitioning a space formed between the inner peripheral surface of the cylinder and an outer peripheral surface of the rolling piston into a suction chamber into which the refrigerant is sucked and a compression chamber in which the refrigerant is compressed; and a spring biasing the vane toward the rolling piston side. The cylinder is provided with a vane groove which is formed to extend radially outwardly from the inner peripheral surface of the cylinder, and in which the vane is disposed, and a suction hole which is formed to penetrate from the inner peripheral surface to the outer peripheral surface of the cylinder, and through which the refrigerant to be sucked into the suction chamber flows. The suction hole includes an outer peripheral-side suction hole connected to the outer peripheral surface of the cylinder and an inner peripheral-side suction hole connected to the inner peripheral surface of the cylinder, and is formed such that, when the suction hole is viewed inwardly in the radial direction of the cylinder, the contour of the inner peripheral-side suction hole is accommodated in the contour of the outer peripheral-side suction hole. When the suction hole is viewed inwardly in the radial direction of the cylinder, the inner peripheral-side suction hole has a vertically long non-circular shape in which an opening width in the circumferential direction of the cylinder is shorter than an opening width in the thickness direction of the cylinder, and the centroid of the inner peripheral-side suction hole in the circumferential direction of the cylinder is eccentric toward the vane groove side relative to the centroid of the outer peripheral-side suction hole.

Description

Compressor and refrigeration cycle device

[0001] The present disclosure relates to a compressor and a refrigeration cycle device, and more particularly to a suction flow path for a refrigerant into a compression chamber.

[0002] Some compressors are equipped with a rotary compression element that includes a rotating shaft having an eccentric shaft portion, a cylindrical cylinder provided on the outer periphery of the eccentric shaft portion, a roller (hereinafter also referred to as a rolling piston) that rotates following the eccentric shaft portion and forms a compression chamber between the roller and the cylinder, and upper and lower shaft bearings that are arranged above and below the cylinder and rotatably support the rotating shaft (see, for example, Patent Document 1).

[0003] The cylinder of Patent Document 1 has a suction hole with an outer circumferential portion (hereinafter also referred to as the outer circumferential suction hole) connected to the outer circumferential surface of the cylinder and into which a suction pipe is inserted, and an inner circumferential portion (hereinafter also referred to as the inner circumferential suction hole) connected to the inner circumferential surface of the cylinder. When viewed radially inward of the cylinder, the outer circumferential suction hole has a circular cross section with a diameter large enough to insert the suction pipe. The inner circumferential suction hole has an elliptical cross section whose opening width in the cylinder circumferential direction, i.e., the direction of roller rotation, is greater than its opening width in the cylinder thickness direction, and the major axis of this elliptical cross section is smaller than the diameter of the circular cross section of the outer circumferential suction hole. By making the inner circumferential suction hole elongated in the cylinder thickness direction, the cross-sectional area of ​​the inner circumferential suction hole is increased, thereby reducing passage resistance for the refrigerant gas and improving adiabatic compression efficiency. In addition, in Patent Document 1, when the cross-sectional area of ​​the inner suction hole is increased, the cross-sectional area is increased only in the cylinder thickness direction, not in the cylinder circumferential direction, so the opening width and position of the suction hole do not change in the direction of roller rotation. As a result, even if the cross-sectional area of ​​the inner suction hole is increased, there is no delay in the start of compression, and the volumetric efficiency is maintained at the desired value.

[0004] Japanese Utility Model Application Publication No. 56-70174

[0005] However, in the compressor of Patent Document 1, the opening width of the inner suction hole in the cylinder circumferential direction is not changed, and the centroid of the outer suction hole and the centroid of the inner suction hole are aligned, so the timing at which the rolling piston passes through the cylinder's inner portion of the suction hole is the same as in the conventional compressor. Therefore, in the compressor of Patent Document 1, although the increase in the cross-sectional area of ​​the inner suction hole has the effect of improving compression efficiency, the timing at which compression starts is the same as in the conventional compressor, so it is not possible to improve volumetric efficiency and further improve compression efficiency, and the effect of improving compression efficiency is limited.

[0006] The present disclosure has been made against the background of the above-mentioned problems, and provides a compressor and a refrigeration cycle device that are expected to have the effect of further improving compression efficiency by starting compression earlier than conventional compressors and improving volumetric efficiency.

[0007] A compressor according to the present disclosure is a compressor that compresses a refrigerant in a compression mechanism that is disposed inside a sealed container that is an outer shell and has a compression chamber, the compression mechanism including a cylinder housed inside the sealed container, a rolling piston that rotates eccentrically along an inner peripheral surface of the cylinder, a vane that divides a space formed between the inner peripheral surface of the cylinder and the outer peripheral surface of the rolling piston into a suction chamber into which the refrigerant is drawn and a compression chamber into which the refrigerant is compressed, and a spring that biases the vane toward the rolling piston, the cylinder having a vane groove that is formed to extend radially outward from the inner peripheral surface of the cylinder and in which the vane is disposed, and a vane groove that is formed to penetrate from the inner peripheral surface to the outer peripheral surface of the cylinder and an inlet hole through which the refrigerant drawn into the inlet chamber flows, the inlet hole having an outer circumferential suction hole connected to the outer circumferential surface of the cylinder and an inner circumferential suction hole connected to the inner circumferential surface of the cylinder, the inlet hole being formed so that the contour of the inner circumferential suction hole fits within the contour of the outer circumferential suction hole when viewed radially inward of the cylinder, the inner circumferential suction hole having a vertically elongated non-circular shape whose opening width in the circumferential direction of the cylinder is shorter than its opening width in the thickness direction of the cylinder when viewed radially inward of the cylinder, and the centroid of the inner circumferential suction hole is eccentric to the vane groove side relative to the centroid of the outer circumferential suction hole when viewed radially inward of the cylinder.

[0008] The refrigeration cycle device according to the present disclosure includes the above-described compressor, a radiator in which the refrigerant compressed by the compressor radiates heat, a pressure reducer that reduces the pressure of the refrigerant that has radiated heat in the radiator, and an evaporator in which the refrigerant that has been depressurized in the pressure reducer evaporates.

[0009] In the compressor and refrigeration cycle device according to the present disclosure, the suction holes are formed so that the contour of the inner suction hole fits within the contour of the outer suction hole when viewed radially inward of the cylinder. The inner suction hole has a vertically elongated, non-circular shape whose opening width in the circumferential direction of the cylinder is shorter than its opening width in the thickness direction of the cylinder. The centroid of the inner suction hole is eccentric toward the vane groove relative to the centroid of the outer suction hole in the circumferential direction of the cylinder. Thus, as in conventional compressors, the cross-sectional area of ​​the inner suction hole is ensured to suppress pressure loss. Furthermore, the eccentricity of the centroid of the inner suction hole accelerates the timing at which the rolling piston passes through the inner suction hole, i.e., the start of compression, thereby improving the volumetric efficiency of the compressor. As a result, the reduced pressure loss and improved volumetric efficiency are expected to significantly improve compression efficiency compared to conventional compressors.

[0010] 6 is a longitudinal sectional view showing the overall configuration of a compressor according to a first embodiment. FIG. 7 is a partial sectional view showing a schematic configuration of the compression mechanism of FIG. 1. FIG. 8 is a refrigerant circuit diagram showing a refrigeration cycle apparatus according to the first embodiment. FIG. 9 is a configuration diagram showing a schematic configuration of the compression mechanism of FIG. 1. FIG. 10 is a CC sectional view of the cylinder of FIG. 4, showing a cross section of an outer circumferential suction hole. FIG. 11 is a DD sectional view of the cylinder of FIG. 4, showing a cross section of an inner circumferential suction hole. FIG. 12 is a schematic view showing a first modified example of the inner circumferential suction hole of FIG. 6. FIG. 13 is a schematic view showing a second modified example of the inner circumferential suction hole of FIG. 6. FIG. 14 is a partially enlarged view showing the structure around the suction hole in the compression mechanism of FIG. 4. FIG. 15 is a view showing a step between the outer circumferential suction hole and the inner circumferential suction hole in the cylinder of FIG. 5. FIG. 16 is a sectional view showing a first example arrangement of a cylinder and the inner circumferential suction hole when the cylinder is placed in the suction hole of FIG. 5. FIG. 17 is a sectional view showing a second example arrangement of a cylinder and the inner circumferential suction hole when the cylinder is placed in the suction hole of FIG. 5. FIG. 18 is a configuration diagram showing a schematic configuration of a compression mechanism used in a second embodiment. FIG. 14 is a partially enlarged view showing the structure around the suction hole in the compression mechanism of FIG. 13. FIG. 15 is a configuration diagram showing the schematic configuration of a compression mechanism used in embodiment 3. FIG. 16 is an E-E cross-sectional view of the cylinder of FIG. 15, showing a cross-section of the suction hole near the inner peripheral surface of the cylinder. FIG. 17 is a configuration diagram showing the schematic configuration of a compression mechanism used in embodiment 4. FIG. 18 is an F-F cross-sectional view of the cylinder of FIG. 17, showing a cross-section of the outer peripheral side suction hole. FIG. 19 is a longitudinal cross-sectional view showing the overall configuration of a compressor according to embodiment 5.

[0011] Embodiments of a compressor according to the present disclosure will be described below with reference to the drawings. The present disclosure is not limited to the following embodiments and may be modified in various ways without departing from the spirit and scope of the present disclosure. Furthermore, the present disclosure includes all possible combinations of the configurations shown in the following embodiments. In particular, the combinations of components are not limited to those in the respective embodiments, and components described in one embodiment may be applied to another embodiment. The compressors shown in the drawings are examples of compressors according to the present disclosure, and the compressors shown in the drawings are not intended to limit the scope of the present disclosure. In the following description, terms indicating directions (e.g., "up," "down," "right," "left," "front," "rear," etc.) are used as appropriate for the purpose of explanation, but these terms are not intended to limit the present disclosure. In the drawings, components designated with the same reference numerals are identical or equivalent, and this applies throughout the specification. The relative dimensions or shapes of components in the drawings may differ from those in actuality.

[0012] Embodiment 1 Fig. 1 is a vertical cross-sectional view showing the overall configuration of a compressor 1 according to embodiment 1. Fig. 2 is a partial cross-sectional view schematically showing the general configuration of a compression mechanism 20 of Fig. 1 .

[0013] [Configuration of Compressor 1] As shown in Fig. 1 , compressor 1 according to embodiment 1 is a rolling piston compressor (rotary compressor) as an example of a compressor according to the present disclosure. Compressor 1 includes a sealed container 10 as an outer shell, a first suction pipe 2A, a second suction pipe 2B, a suction muffler 3, a compression mechanism 20, a rotating electric machine 30, a rotating shaft 40, and a discharge pipe 4. Sealed container 10 constitutes the outer shell of compressor 1. First suction pipe 2A and second suction pipe 2B supply refrigerant into sealed container 10. Suction muffler 3 is disposed outside sealed container 10 and connected to first suction pipe 2A and second suction pipe 2B. Compression mechanism 20 is connected to first suction pipe 2A and second suction pipe 2B and compresses refrigerant. In the first embodiment, the first suction pipe 2A is connected to the compression mechanism 20 via the first connecting pipe 60A, and the second suction pipe 2B is connected to the compression mechanism 20 via the second connecting pipe 60B, but the first suction pipe 2A and the second suction pipe 2B may each be directly connected to the compression mechanism 20. The rotating electric machine 30 includes a rotor 31 and a stator 32. The rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30 and rotates together with the rotor 31. The discharge pipe 4 discharges the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10. The configuration of the compressor 1 will be described in detail below.

[0014] Hereinafter, the first intake pipe 2A and the second intake pipe 2B may be referred to as intake pipes 2 without distinction. Also, the first connecting pipe 60A and the second connecting pipe 60B may be referred to as connecting pipes 60 without distinction.

[0015] (Sealed casing 10) The sealed casing 10, which forms the outer shell of the compressor 1, houses the compression mechanism 20, the rotating electric machine 30, the rotating shaft 40, etc. The sealed casing 10 includes a head 11, a bottom 13, and a body 12. The head 11 forms the outer shell of the upper part of the compressor 1, and the bottom 13 forms the outer shell of the lower part of the compressor 1. The body 12 forms the outer shell of the middle part of the compressor 1, with the head 11 attached to the upper part and the bottom 13 attached to the lower part.

[0016] A head portion 11 constituting the upper portion of the sealed container 10 has, for example, a substantially bowl shape as shown in Fig. 1. A discharge pipe 4 that connects the inside and outside of the sealed container 10 is connected to the head portion 11.

[0017] As shown in Fig. 1 , the body portion 12 constituting the middle portion of the sealed container 10 has, for example, a substantially cylindrical shape. A first suction pipe 2A and a second suction pipe 2B for supplying refrigerant into the sealed container 10 are connected to the body portion 12. A stator 32 of a rotating electric machine 30 is attached to the inner circumferential surface of the body portion 12. A compression mechanism 20 is also attached to the inner circumferential surface of the body portion 12. In the first embodiment, a rolling piston type compression mechanism is used as the compression mechanism 20. In such cases, the compression mechanism 20 is often attached to the inner circumferential surface of the body portion 12, below the position where the stator 32 is attached.

[0018] The bottom 13 constituting the lower part of the sealed container 10 is, for example, substantially bowl-shaped, as shown in Fig. 1. Refrigerating machine oil 6, which is a lubricating oil, is stored in the bottom 13. That is, the refrigerating machine oil 6 is stored inside the sealed container 10. The refrigerating machine oil 6 is then supplied to the compression mechanism 20 and the like by an oil supply mechanism, which will be described later, thereby reducing friction at sliding parts of the compression mechanism 20 and the like.

[0019] (Intake Pipe 2) As described above, the first intake pipe 2A and the second intake pipe 2B are connected to the body 12 of the sealed container 10. One end of the first intake pipe 2A is connected to a first cylinder 21A of the compression mechanism 20 (described later) via a first connecting pipe 60A. The other end of the first intake pipe 2A is connected to the intake muffler 3. One end of the second intake pipe 2B is connected to a second cylinder 21B of the compression mechanism 20 (described later) via a second connecting pipe 60B. The other end of the second intake pipe 2B is connected to the intake muffler 3.

[0020] (Suction muffler 3) The suction muffler 3 functions as a muffler that reduces refrigerant noise and other noise generated when the refrigerant flows into the compressor 1. The suction muffler 3 also functions as an accumulator that can store liquid refrigerant. As described above, the suction muffler 3 communicates with the first suction pipe 2A and the second suction pipe 2B.

[0021] (Compression mechanism 20) The compression mechanism 20 is connected to the rotating shaft 40 and compresses the refrigerant drawn in from the outside using the power of the rotating electric machine 30 transmitted by the rotating shaft 40. In the first embodiment, the refrigerant that flows into the suction muffler 3 is supplied to the compression mechanism 20 via the first suction pipe 2A and the second suction pipe 2B. That is, the compression mechanism 20 draws in the external refrigerant via the first suction pipe 2A and the second suction pipe 2B and compresses this refrigerant. The refrigerant compressed by the compression mechanism 20 is released into the space inside the sealed container 10 and outside the compression mechanism 20.

[0022] 1, the compression mechanism 20 includes a first cylinder 21A, a first rolling piston 22A, an upper bearing 24A, a second cylinder 21B, a second rolling piston 22B, a lower bearing 24B, and a partition plate 25. The compression mechanism 20 is formed by fastening the upper bearing 24A, the first cylinder 21A, the partition plate 25, the second cylinder 21B, and the lower bearing 24B together with screws 26. As will be described later, the first cylinder 21A and the second cylinder 21B have generally the same configuration.

[0023] A first connecting pipe 60A is connected to the first cylinder 21A, and a second connecting pipe 60B is connected to the second cylinder 21B. The first rolling piston 22A is disposed in the first cylinder 21A and rotates slidably within the first cylinder 21A. The second rolling piston 22B is disposed in the second cylinder 21B and rotates slidably within the second cylinder 21B. Hereinafter, the first cylinder 21A and the second cylinder 21B may be referred to as cylinders 21 without distinction. Furthermore, the first rolling piston 22A and the second rolling piston 22B may be referred to as rolling pistons 22 without distinction. The direction of arrow R in FIG. 2 indicates the rotation direction of the rolling piston 22 within the cylinder 21.

[0024] As shown in FIG. 2 , the compression mechanism 20 also includes a vane 50 and a spring 51 in each cylinder 21 .

[0025] 1 and 2, the cylinder 21 is cylindrical and defines a cylinder chamber 55. Since the rolling piston 22 is disposed within the cylinder 21, the space defined between the inner peripheral surface 21i of the cylinder 21 and the outer peripheral surface 22o of the rolling piston 22 essentially constitutes the cylinder chamber 55 (i.e., a compression chamber 58 and a suction chamber 57, which will be described later).

[0026] The cylinder 21 is disposed so that the center C21 of the cylinder 21 shown in Fig. 2 coincides with the rotation center Ax of the rotation shaft 40 shown in Fig. 1. The cylinder 21 is disposed so that the central axis of the cylinder 21 coincides with the rotation center Ax of the rotation shaft 40. In other words, the extension direction of the central axis of the cylinder 21 (hereinafter also referred to as the axial direction of the cylinder 21) is the extension direction of the rotation center Ax of the rotation shaft 40 (hereinafter also referred to as the axial direction of the rotation shaft 40).

[0027] The cylinder 21 is also formed with a suction passage Pin through which the refrigerant is drawn from the suction pipe 2, and a discharge passage Pout through which the refrigerant is discharged to the discharge pipe 4 via the internal space of the sealed container 10. Specifically, as shown in Fig. 1, the cylinder 21 is provided with a suction hole 59 constituting the suction passage Pin, which penetrates the cylinder 21 in the radial direction, and a connecting pipe 60 is press-fitted into the outer peripheral portion of the suction hole 59.

[0028] As shown in FIG. 2 , a vane groove 56 extending radially outward from the inner circumferential surface 21i of the cylinder 21 is formed between the intake flow path Pin and the discharge flow path Pout in the circumferential direction of the cylinder 21. The vane groove 56 penetrates the cylinder 21 in its thickness direction. The thickness direction of the cylinder 21 is the axial direction of the rotating shaft 40 (direction of arrow Z) shown in FIG. 1 . A spring hole 54 is formed in the cylinder 21 at the radially outer end of the vane groove 56. The spring hole 54 is formed by, for example, a drill or the like, at a position overlapping with the vane groove 56 in a plan view, with a depth that does not penetrate from the outer periphery of the cylinder 21 to the cylinder chamber 55. The spring hole 54 in the cylinder 21 communicates with the vane groove 56.

[0029] 2, the vane 50 is a plate-shaped member. The vane 50 is disposed in a vane groove 56 of the cylinder 21, is positioned between the suction flow path Pin and the discharge flow path Pout in the circumferential direction of the cylinder 21, and is disposed so as to extend in the radial direction of the cylinder 21. The vane 50 is biased toward the rolling piston 22 (radially inward) by a spring 51 disposed in a spring hole 54, and divides the cylinder chamber 55 into a suction chamber 57 and a compression chamber 58. The suction chamber 57 is a space within the cylinder chamber 55 that communicates with the suction flow path Pin, and the compression chamber 58 is a space within the cylinder chamber 55 that communicates with the discharge flow path Pout.

[0030] Hereinafter, the cylinder chamber 55 of the first cylinder 21A may be referred to as a first cylinder chamber 55A, and the cylinder chamber 55 of the second cylinder 21B may be referred to as a second cylinder chamber 55B to distinguish it from the first cylinder chamber 55A.

[0031] 1, the upper bearing 24A is disposed so as to contact the upper end surface 21Au of the first cylinder 21A, and closes the first cylinder chamber 55A. The upper bearing 24A supports the rotary shaft 40 so as to be able to rotate freely.

[0032] The lower bearing 24B is disposed so as to abut against a lower end surface 21Bl of the second cylinder 21B, and closes the second cylinder chamber 55B. The lower bearing 24B rotatably supports the rotary shaft 40 below the upper bearing 24A.

[0033] The partition plate 25 is positioned so as to abut against the lower end surface 21Al of the first cylinder 21A and the upper end surface 21Bu of the second cylinder 21B, thereby closing off the first cylinder chamber 55A and the second cylinder chamber 55B.

[0034] Hereinafter, one and the other end faces (upper end face and lower end face) in the thickness direction of the cylinder 21 may be referred to as end faces 21E of the cylinder 21 without distinction.

[0035] As shown in FIGS. 1 and 2 , the rolling piston 22 is a cylindrical member. The rolling piston 22 is fitted to an eccentric shaft portion 41 (first eccentric shaft portion 41A or second eccentric shaft portion 41B) of the rotating shaft 40, and performs rotational motion eccentric to the rotation center Ax of the rotating shaft 40 together with the eccentric shaft portion 41 to compress the refrigerant. Hereinafter, the rotational motion eccentric to the rotation center Ax of the rotating shaft 40 will be referred to as "eccentric rotational motion." Specifically, as shown in FIG. 1 , the first rolling piston 22A is fitted to the first eccentric shaft portion 41A of the rotating shaft 40 and rotates eccentrically together with the first eccentric shaft portion 41A. Meanwhile, the second rolling piston 22B is fitted to a second eccentric shaft portion 41B provided on the rotating shaft 40 below the first eccentric shaft portion 41A and rotates eccentrically together with the second eccentric shaft portion 41B.

[0036] 1, the first rolling piston 22A is connected to the rotary shaft 40 so as to be able to rotate within the first cylinder 21A with a phase shift of 180 degrees relative to the rotational phase of the second rolling piston 22B when it rotates within the second cylinder 21B. In other words, the second rolling piston 22B is connected to the rotary shaft 40 so as to be able to rotate within the second cylinder 21B with a phase shift of −180 degrees relative to the rotational phase of the first rolling piston 22A when it rotates within the first cylinder 21A.

[0037] The upper bearing 24A is provided with a valve (not shown) that releases the refrigerant compressed by the first cylinder 21A and the first rolling piston 22A. The upper bearing 24A is also provided with a first muffler 23A that discharges the refrigerant compressed by the first cylinder 21A and the first rolling piston 22A. When the valve provided on the upper bearing 24A opens, the space formed by the first cylinder 21A and the first rolling piston 22A communicates with the first muffler 23A (described below). In other words, the refrigerant compressed in the compression chamber 58 (see FIG. 2) in the first cylinder 21A can be discharged into the first muffler 23A via the discharge flow path Pout (see FIG. 2).

[0038] The lower bearing 24B is provided with a valve (not shown) that releases the refrigerant compressed by the second cylinder 21B and the second rolling piston 22B. The lower bearing 24B is also provided with a second muffler 23B that discharges the refrigerant compressed by the second cylinder 21B and the second rolling piston 22B. When the valve provided on the lower bearing 24B opens, the space formed by the second cylinder 21B and the second rolling piston 22B communicates with the second muffler 23B (described below). In other words, the refrigerant compressed in the compression chamber 58 (see FIG. 2) in the second cylinder 21B can be discharged into the second muffler 23B via the discharge flow path Pout (see FIG. 2).

[0039] The first muffler 23A is provided with a refrigerant discharge portion (not shown). The refrigerant compressed by the first cylinder 21A and the first rolling piston 22A is discharged into the first muffler 23A and then released from the refrigerant discharge portion into a space inside the sealed container 10 and outside the first muffler 23A. The second muffler 23B is connected to the first muffler 23A via a refrigerant flow path (not shown). The refrigerant compressed by the second cylinder 21B and the second rolling piston 22B is discharged into the second muffler 23B and then flows into the first muffler 23A via the refrigerant flow path (not shown). The refrigerant that has flowed into the first muffler 23A is then released from the refrigerant discharge portion of the first muffler 23A into a space inside the sealed container 10 and outside the first muffler 23A.

[0040] (Rotating electric machine 30 and rotating shaft 40) As shown in Figure 1, the rotating electric machine 30 has a rotor 31 that transmits its own rotation to the rotating shaft 40, and a stator 32 that is configured by attaching multiple phase windings to a laminated core.

[0041] The rotating shaft 40 is connected to the rotating electric machine 30 and rotates by the power of the rotating electric machine 30. The rotating shaft 40 also transmits the power of the rotating electric machine 30 to the compression mechanism 20. The rotating shaft 40 shown in FIG. 1 rotates around a rotation center Ax that is an axis extending in the vertical direction of the page. An upper portion of the rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30, so that the rotating shaft 40 rotates together with the rotation of the rotor 31. A lower portion of the rotating shaft 40 is connected to the compression mechanism 20. More specifically, the lower portion of the rotating shaft 40 is rotatably supported by an upper bearing 24A and a lower bearing 24B of the compression mechanism 20.

[0042] The first rolling piston 22A and the second rolling piston 22B are connected to the rotating shaft 40 between a portion rotatably supported by the upper bearing 24A and a portion rotatably supported by the lower bearing 24B so that they can rotate eccentrically. Specifically, the rotating shaft 40 has a first eccentric shaft portion 41A and a second eccentric shaft portion 41B between a portion rotatably supported by the upper bearing 24A and a portion rotatably supported by the lower bearing 24B. The first eccentric shaft portion 41A and the second eccentric shaft portion 41B are eccentric in opposite directions relative to the rotation center Ax of the rotating shaft 40 so that the first rolling piston 22A rotates with a phase shift of 180 degrees relative to the rotation phase of the second rolling piston 22B.

[0043] As a result, the rotating shaft 40 rotates in conjunction with the rotation of the rotor 31, causing the first rolling piston 22A and the second rolling piston 22B to perform eccentric rotational motion. The refrigerant is compressed by the first cylinder 21A and the first rolling piston 22A, and the refrigerant is compressed by the second cylinder 21B and the second rolling piston 22B. In other words, the compression mechanism 20 compresses the refrigerant drawn in from the outside using the power of the rotating electric machine 30 transmitted by the rotating shaft 40.

[0044] (Discharge pipe 4) The discharge pipe 4 is a pipe that discharges the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10. That is, the discharge pipe 4 is a pipe that discharges the high-temperature, high-pressure refrigerant inside the sealed container 10 to the outside of the sealed container 10. In FIG. 1 , the discharge pipe 4 is installed in the head 11 of the sealed container 10.

[0045] (Oil Supply Mechanism) The rotating shaft 40 is formed with an oil supply hole 42 that opens at one end 40e (the lower end of the rotating shaft 40 in FIG. 1 ) in the axial direction (the direction of the arrow Z). The oil supply hole 42 extends along the rotation center Ax of the rotating shaft 40. The rotating shaft 40 is also formed with a first oil supply port 43 and a second oil supply port 44. The first oil supply port 43 and the second oil supply port 44 serve as flow paths for supplying the refrigeration oil 6 sucked into the oil supply hole 42 to the sliding parts of the compression mechanism 20. One end of each of the first oil supply port 43 and the second oil supply port 44 communicates with the oil supply hole 42. The other end of each of the first oil supply port 43 and the second oil supply port 44 opens at a location on the outer circumferential surface of the rotating shaft 40 that faces the compression mechanism 20. In the first embodiment, the other end of first oil fill port 43 opens at a position facing upper bearing 24A of compression mechanism 20. The other end of second oil fill port 44 opens at a position facing lower bearing 24B of compression mechanism 20.

[0046] The centrifugal pump 45 is provided inside the oil supply hole 42 of the rotating shaft 40. The centrifugal pump 45 is a fluid machine that uses centrifugal force generated by the rotational motion of the rotating shaft 40 to suck up the refrigeration oil 6 as lubricant stored in the bottom 13 of the sealed container 10. The centrifugal pump 45 is formed, for example, by twisting a plate-shaped member.

[0047] Refrigerant oil 6 pumped up into oil feed hole 42 by centrifugal pump 45 is supplied to sliding parts of compression mechanism 20. Specifically, a portion of refrigerant oil 6 pumped up into oil feed hole 42 passes through first oil feed port 43 and is supplied to sliding parts between upper bearing 24A and rotating shaft 40 of compression mechanism 20. Furthermore, a portion of refrigerant oil 6 pumped up into oil feed hole 42 passes through second oil feed port 44 and is supplied to sliding parts between lower bearing 24B and rotating shaft 40 of compression mechanism 20. As refrigerant oil 6, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, polyol ester-based lubricating oil, or the like is used.

[0048] [Operation of the rotating electric machine 30] A current is supplied from a power source (not shown) to windings provided on the laminated core of the stator 32, forming a rotating magnetic field in the stator 32. This causes the rotating magnetic field of the stator 32 to act on the permanent magnets provided in the rotor 31, causing the rotor 31 to rotate. The rotation of the rotor 31 is transmitted to the first rolling piston 22A and the second rolling piston 22B via the rotating shaft 40, causing the first rolling piston 22A and the second rolling piston 22B to perform eccentric rotational motion.

[0049] [Refrigerant Flow] The eccentric rotation of the first rolling piston 22A and the second rolling piston 22B draws refrigerant into the compressor 1. Specifically, the eccentric rotation of the first rolling piston 22A and the second rolling piston 22B causes low-pressure refrigerant outside the compressor 1 to flow into the suction muffler 3. Then, of the low-pressure refrigerant that has flowed into the suction muffler 3, low-pressure gaseous refrigerant flows into the compression mechanism 20 of the compressor 1 via the first suction pipe 2A and the second suction pipe 2B. A portion of the gaseous refrigerant that has flowed into the compression mechanism 20 is compressed by the first cylinder 21A and the first rolling piston 22A to become high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant flows into the first muffler 23A via the valve of the upper bearing 24A. The high-temperature, high-pressure gaseous refrigerant that has flowed into the first muffler 23A is discharged from a refrigerant discharge port (not shown) provided in the first muffler 23A into the space within the sealed container 10. Then, the high-temperature, high-pressure gaseous refrigerant that has been discharged into the space within the sealed container 10 moves to the upper part of the space within the sealed container 10 through gaps, etc., of the rotating electrical machine 30, and is discharged from the discharge pipe 4.

[0050] The remainder of the gaseous refrigerant that has flowed into the compression mechanism 20 is compressed by the second cylinder 21B and the second rolling piston 22B to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant flows into the second muffler 23B through a valve in the lower bearing 24B. The high-temperature, high-pressure gaseous refrigerant that has flowed into the second muffler 23B passes through a refrigerant flow path (not shown) from the second muffler 23B and is sent to the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant sent to the first muffler 23A is then released into the space within the sealed container 10 from a refrigerant discharge port (not shown) provided in the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant released into the space within the sealed container 10 moves to the upper part of the space within the sealed container 10 through gaps, etc., of the rotating electrical machine 30, and is discharged from the discharge pipe 4.

[0051] Furthermore, the refrigeration oil 6 stored in the bottom 13 of the sealed container 10 is sucked up from the lower end of the oil supply hole 42 by a centrifugal pump 45 that rotates together with the rotating shaft 40. The refrigeration oil 6 sucked up from the lower end of the oil supply hole 42 flows as lubricating oil between the upper bearing 24A and the rotating shaft 40 from the first oil supply port 43. The refrigeration oil 6 also flows from the second oil supply port 44 between the lower bearing 24B and the rotating shaft 40. By the refrigeration oil 6 flowing between these, the rotating shaft 40 can smoothly transmit the rotational driving force to the first rolling piston 22A and the second rolling piston 22B.

[0052] Furthermore, a portion of the refrigeration oil 6 that flows from the first oil supply port 43 between the upper bearing 24A and the rotating shaft 40 flows between the upper bearing 24A and the upper surface of the first rolling piston 22A. A portion of the refrigeration oil 6 that flows from the second oil supply port 44 between the lower bearing 24B and the rotating shaft 40 flows between the lower bearing 24B and the lower surface of the second rolling piston 22B. The refrigeration oil 6 is used to smoothly rotate the first rolling piston 22A and the second rolling piston 22B, but a portion of the refrigeration oil 6 is compressed together with the low-pressure gaseous refrigerant and is discharged in a state contained in the high-temperature, high-pressure gaseous refrigerant.

[0053] 3 is a refrigerant circuit diagram showing the refrigeration cycle apparatus 200 according to Embodiment 1. The refrigeration cycle apparatus 200 includes the compressor 1 according to Embodiment 1, a radiator in which the refrigerant compressed by the compressor 1 radiates heat, a pressure reducer 203 such as an electric expansion valve that reduces the pressure of the refrigerant flowing out from the radiator, and an evaporator in which the refrigerant flowing out from the pressure reducer 203 evaporates.

[0054] The refrigeration cycle apparatus 200 is used for various purposes, such as a hot water supply apparatus and a freezing apparatus. FIG. 3 shows an example in which the refrigeration cycle apparatus 200 is used as an air conditioner. Therefore, the refrigeration cycle apparatus 200 shown in FIG. 3 includes an indoor heat exchanger 204 that functions as a radiator during heating operation and an outdoor heat exchanger 202 that functions as an evaporator during heating operation. The refrigeration cycle apparatus 200 shown in FIG. 3 is also capable of cooling operation. Therefore, the refrigeration cycle apparatus 200 includes a four-way switching valve 201. The four-way switching valve 201 switches between the heat exchanger connected to the discharge pipe 4, which is the refrigerant discharge port of the compressor 1, and the heat exchanger connected to the suction muffler 3, which is the refrigerant intake port of the compressor 1. During cooling operation, the indoor heat exchanger 204 functions as an evaporator, and the outdoor heat exchanger 202 functions as a radiator.

[0055] When the refrigeration cycle apparatus 200 is used as an air conditioner, for example, the indoor heat exchanger 204 is mounted in an indoor apparatus (indoor unit 200B), and the compressor 1, the four-way switching valve 201, the outdoor heat exchanger 202, and the pressure reducer 203 are mounted in an outdoor apparatus (outdoor unit 200A).

[0056] Examples of the refrigerant used in the refrigeration cycle device 200 include fluorine-based refrigerants or hydrocarbon-based refrigerants with low global warming potential (GWP). Examples of the refrigerant include a single refrigerant selected from R1234yf, R1234ze, R32, and R290, a mixed refrigerant containing two or more of these, or a mixed refrigerant containing one or more of these with another refrigerant. Examples of the refrigerant include a mixed refrigerant containing R1132(E) or a mixed refrigerant containing R1123. Examples of the refrigerant include a mixed refrigerant of two or more of R516A, R410A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, and R459A.

[0057] The operation of the refrigeration cycle device 200 during heating operation and cooling operation will be described below.

[0058] When the refrigeration cycle apparatus 200 performs heating operation, the four-way switching valve 201 switches to the flow path shown by the solid lines in FIG. 3 . This connects the discharge pipe 4 of the compressor 1 to the indoor heat exchanger 204, and the suction muffler 3 of the compressor 1 to the outdoor heat exchanger 202. That is, the indoor heat exchanger 204 functions as a radiator, and the outdoor heat exchanger 202 functions as an evaporator. In this state, when the high-temperature, high-pressure gaseous refrigerant compressed by the compressor 1 is discharged from the compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the indoor heat exchanger 204. The high-temperature, high-pressure gaseous refrigerant that flows into the indoor heat exchanger 204 condenses while releasing heat to the indoor air, becoming a high-pressure liquid refrigerant that flows out of the indoor heat exchanger 204. At this time, the indoor air is heated. Note that some refrigerants, such as carbon dioxide refrigerants, do not condense when releasing heat. When a refrigerant that condenses when radiating heat is used, the radiator may also be called a condenser.

[0059] The high-pressure liquid refrigerant that flows out of the indoor heat exchanger 204 flows into the pressure reducer 203. The high-pressure liquid refrigerant that flows into the pressure reducer 203 is reduced in pressure by the pressure reducer 203 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant, which flows out of the pressure reducer 203. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows out of the pressure reducer 203 flows into the outdoor heat exchanger 202. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the outdoor heat exchanger 202 absorbs heat from the outdoor air and evaporates, and flows out of the outdoor heat exchanger 202 as a low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant. The low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant that flows out of the outdoor heat exchanger 202 is drawn into the suction muffler 3 of the compressor 1. Then, the low-pressure gaseous refrigerant among the refrigerants sucked into the suction muffler 3 of the compressor 1 is compressed by the compression mechanism 20 of the compressor 1 to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is discharged again from the compressor 1. That is, when the refrigeration cycle apparatus 200 performs heating operation, the refrigerant circulates in the direction indicated by the straight solid arrow in Fig. 3.

[0060] When the refrigeration cycle apparatus 200 performs cooling operation, the four-way switching valve 201 switches to the flow path shown by the dashed lines in Fig. 3 . As a result, the discharge pipe 4 of the compressor 1 is connected to the outdoor heat exchanger 202, and the suction muffler 3 of the compressor 1 is connected to the indoor heat exchanger 204. That is, the outdoor heat exchanger 202 functions as a radiator, and the indoor heat exchanger 204 functions as an evaporator. In this state, when high-temperature, high-pressure gaseous refrigerant compressed by the compressor 1 is discharged from the compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the outdoor heat exchanger 202. The high-temperature, high-pressure gaseous refrigerant that has flowed into the outdoor heat exchanger 202 condenses while releasing heat to the outdoor air, becoming a high-pressure liquid refrigerant that flows out of the outdoor heat exchanger 202.

[0061] The high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 202 flows into the pressure reducer 203. The high-pressure liquid refrigerant that flowed into the pressure reducer 203 is then decompressed by the pressure reducer 203 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant, which flows out of the pressure reducer 203. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows out of the pressure reducer 203 flows into the indoor heat exchanger 204. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the indoor heat exchanger 204 absorbs heat from the indoor air and evaporates, and flows out of the indoor heat exchanger 204 as a low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant. At this time, the indoor air is cooled. The low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant that flows out of the indoor heat exchanger 204 is drawn into the suction muffler 3 of the compressor 1. Then, the low-pressure gaseous refrigerant among the refrigerants sucked into the suction muffler 3 of the compressor 1 is compressed by the compression mechanism 20 of the compressor 1 to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is discharged again from the compressor 1. That is, when the refrigeration cycle apparatus 200 performs cooling operation, the refrigerant circulates in the direction indicated by the dashed arrow in Fig. 3.

[0062] FIG. 4 is a schematic diagram showing the configuration of the compression mechanism 20 of FIG. 1. FIG. 5 is a cross-sectional view of the cylinder 21 of FIG. 4 taken along line CC, showing the cross-section of the outer suction hole 59o. FIG. 6 is a cross-sectional view of the cylinder 21 of FIG. 4 taken along line DD, showing the cross-section of the inner suction hole 59i. FIG. 7 is a schematic diagram showing a first modified example of the inner suction hole 59i of FIG. 6. FIG. 8 is a schematic diagram showing a second modified example of the inner suction hole 59i of FIG. 6. FIG. 9 is a partially enlarged view showing the structure around the suction hole in the compression mechanism 20 of FIG. 4. FIG. 10 is a diagram showing a step 69 between the outer suction hole 59o and the inner suction hole 59i in the cylinder 21 of FIG. 5.

[0063] 1 and 2, and based on Figures 4 to 10, the shape of the suction hole 59 that constitutes the refrigerant suction flow path Pin (see Figure 2) in the cylinder 21 will be described. In Figures 5 to 8 and 10, the left side of the figure is the side where the vane groove 56 is provided, that is, the rear side in the rotation direction (direction of arrow R) of the rolling piston 22 shown in Figure 2.

[0064] 4 and 5, in the first embodiment, the suction hole 59 penetrates the cylinder 21 in the radial direction from the outer peripheral surface 21o to the inner peripheral surface 21i, but does not penetrate in the cylinder thickness direction (arrow Z direction). That is, as shown in Fig. 5, the suction hole 59 is formed between the end faces 21E on both sides in the cylinder thickness direction (arrow Z direction), and the upper and lower ends of the suction hole 59 are covered by the end faces 21E of the cylinder 21.

[0065] 4, the suction hole 59 has an outer circumferential suction hole 59o formed on the outer circumferential side of the cylinder 21, an inner circumferential suction hole 59i formed on the inner circumferential side of the cylinder 21, and a connecting portion 70 connecting the outer circumferential suction hole 59o and the inner circumferential suction hole 59i. An outer circumferential opening 59b into which the connecting pipe 60 is inserted is formed in the outer circumferential surface 21o of the cylinder 21.

[0066] 5, when suction hole 59 is viewed radially inward of cylinder 21, outer suction hole 59o has a circular cross-sectional shape, while inner suction hole 59i has a non-circular cross-sectional shape (i.e., a vertically elongated shape) in which an opening width Wr1 in the cylinder circumferential direction is shorter than an opening width Wz1 in the cylinder thickness direction (direction indicated by arrow Z). When suction hole 59 is viewed radially inward of cylinder 21, the outline of inner suction hole 59i is contained within the outline of outer suction hole 59o.

[0067] In other words, the cross-sectional area of ​​the suction hole 59 is smaller on the inner side than on the outer side, and narrows as it moves from the outer side to the inner side, so that the difference in opening width between the outer suction hole 59o and the inner suction hole 59i is greater particularly in the cylinder circumferential direction than in the cylinder thickness direction (arrow Z direction).

[0068] 5, the centroid 62 of the inner suction hole 59i is offset toward the vane groove 56 in the cylinder circumferential direction, i.e., toward the rear in the rotational direction (direction of arrow R) of the rolling piston 22 shown in FIG. 2, compared to the centroid 61 of the outer suction hole 59o. This allows the timing at which the rolling piston 22 passes through the inner suction hole 59i (particularly the inner opening 59a shown in FIG. 4) to be made earlier than in the conventional case where the centroid 61 of the outer suction hole 59o and the centroid 62 of the inner suction hole 59i are aligned. This therefore increases compression efficiency.

[0069] The position and shape of the inner suction hole 59i will now be described in more detail. As shown in Fig. 4, the outer suction hole 59o extends radially toward the center C21 of the cylinder 21, and the inner suction hole 59i extends such that the centroid line CL62 of the inner suction hole 59i is parallel to the centroid line CL61 of the outer suction hole 59o. As shown in Fig. 4, in a plane (D-D cross section) that is perpendicular to the centroid line CL61 of the outer suction hole 59o and passes through the inner suction hole 59i, the cross section of the inner suction hole 59i is vertically elongated, as shown in Figs. 5 and 6.

[0070] In the example shown in FIG. 6 , the inner suction hole 59i has a straight portion 68 extending in the cylinder thickness direction (arrow Z direction) on the side farther from the vane groove 56 (the right side in FIG. 6 ), i.e., on the forward side in the rotation direction (arrow R direction) of the rolling piston 22 shown in FIG. 2 . As a result, as shown in FIG. 4 , when the rolling piston 22 (see FIG. 2 ) passes through the straight portion 68 of the inner opening 59a on the inner circumferential surface 21i of the cylinder 21, the suction chamber 57 (see FIG. 2 ), which had been in communication with the suction hole 59 until then, can be instantaneously closed to form the compression chamber 58 (see FIG. 2 ). This allows for a good balance between suppressing delays in the start of compression and ensuring a sufficient amount of refrigerant to be compressed.

[0071] The cross-sectional shape of the inner suction hole 59i may be, for example, an upwardly convex curve on the upper side, a downwardly convex curve on the lower side, a straight line on the right side connecting the right ends of the upper and lower curves, and a straight line on the left side connecting the left ends of the upper and lower semicircles. In Figure 6, the cross-sectional shape of the inner suction hole 59i is a vertically elongated oval cross section with an upwardly convex semicircle on the upper side, a downwardly convex semicircle on the lower side, and straight lines on the right and left sides extending in the cylinder thickness direction (arrow Z direction).

[0072] The cross-sectional shape of the inner suction hole 59i is not limited to the oval shape described above, as long as it is a vertically elongated non-circular cross-section. The vertically elongated non-circular cross-section may be, for example, an ellipse as shown in Fig. 7 or a rectangle as shown in Fig. 8. When the cross-sectional shape of the inner suction hole 59i is a rectangle, it is more preferable that the corners of the rectangle are rounded.

[0073] 9, in the first embodiment, the connecting portion 70 connecting the outer suction hole 59o and the inner suction hole 59i has a tapered surface, which prevents a sudden change in the cross-sectional area of ​​the suction hole 59. As a result, when the refrigerant flows from the outer suction hole 59o to the inner suction hole 59i, the tapered surface of the connecting portion 70 allows the refrigerant to flow smoothly, thereby suppressing pressure loss.

[0074] In FIG. 9 , the taper angle of the tapered surface of the connecting portion 70 is set to a constant angle to simplify processing. That is, the relationship between the taper angle α at the position of the connecting portion 70 closest to the vane groove 56 and the taper angle β at the position of the connecting portion 70 farthest from the vane groove 56 is α = β. Furthermore, the relationship between the hole length L1 of the inner suction hole 59i at the position Pb (see FIG. 5 ) closest to the vane groove 56 and the hole length L2 of the inner suction hole 59i at the position Pf (see FIG. 5 ) farthest from the vane groove 56 is L1 > L2. Here, as shown in FIG. 9 , the hole lengths L1 and L2 are the lengths of the inner suction hole 59i in the extension direction, i.e., the lengths from the inner opening 59a to the connecting portion 70.

[0075] By forming suction holes 59 so that L1 > L2 in this way, compared to a conventional case in which suction holes 59 are formed so that L1 = L2 (shown by the dotted line in FIG. 9 ), it is possible to ensure a larger wall portion SW located between suction holes 59 and vane grooves 56 in cylinder 21, thereby increasing the strength of cylinder 21. Specifically, it is possible to ensure a larger thickness in the cylinder circumferential direction of wall portion SW located between connecting portion 70 (tapered surface) of suction hole 59 and outer peripheral suction holes 59o and vane grooves 56 and spring holes 54 in cylinder 21.

[0076] As explained using Fig. 5 , when the suction holes 59 are viewed radially inward of the cylinder 21, the contour of the inner suction holes 59i is contained within the contour of the outer suction holes 59o. As explained using Figs. 4 and 5 , the centroid 62 of the inner suction holes 59i is eccentric to the vane groove 56 in the cylinder circumferential direction (to the left in Figs. 5 and 10 ) relative to the centroid 61 of the outer suction holes 59o. In other words, when the suction holes 59 are viewed radially inward of the cylinder 21 as shown in Fig. 10 , the step 69 between the outer suction holes 59o and the inner suction holes 59i is shortest at a position closer to the vane groove 56 than the centroid 62 of the inner suction hole 59i (to the left in Fig. 10 of the dashed line passing through the centroid 62). Here, the step 69 between the outer circumferential suction hole 59o and the inner circumferential suction hole 59i is the distance between the contour of the outer circumferential suction hole 59o and the contour of the inner circumferential suction hole 59i when the suction hole 59 is viewed radially inward of the cylinder 21. Note that at the position where the step 69 is shortest, there may be no step 69 and the outer circumferential suction hole 59o and the inner circumferential suction hole 59i may be flush with each other.

[0077] Fig. 11 is a cross-sectional view showing a first example of the arrangement of the cylindrical body and the inner suction hole 59i when the cylindrical body is placed in the suction hole 59 shown in Fig. 5. Hereinafter, the suction hole 59 formed in the first cylinder 21A may be referred to as the first suction hole 59A, and the suction hole 59 formed in the second cylinder 21B may be referred to as the second suction hole 59B to distinguish it from the first suction hole 59A.

[0078] In the first embodiment, as shown in FIG. 11 , a connecting pipe 60 that connects the suction pipe 2 and the suction hole 59 is disposed in the outer circumferential suction hole 59o of the suction hole 59. That is, in the first embodiment, the cylindrical body disposed in the suction hole 59 is the connecting pipe 60. More specifically, as shown in FIGS. 1 and 11 , a first connecting pipe 60A that connects the first suction pipe 2A and the first suction hole 59A is disposed in the outer circumferential suction hole 59o of the first suction hole 59A formed in the first cylinder 21A. Furthermore, a second connecting pipe 60B that connects the second suction pipe 2B and the second suction hole 59B is disposed in the outer circumferential suction hole 59o of the second suction hole 59B formed in the second cylinder 21B. The outer circumferential suction hole 59o is formed in a shape and size such that the inner circumferential surface of the outer circumferential suction hole 59o contacts the outer circumferential surface of the connecting pipe 60.

[0079] In this configuration in which the cylindrical body (connecting pipe 60) is disposed within the outer periphery-side suction hole 59o, as shown in Fig. 11, the suction hole 59 and the connecting pipe 60 are preferably formed so that the contour of the inner periphery-side suction hole 59i fits within the contour of the inner periphery surface 60i of the connecting pipe 60. This allows the cross-sectional area of ​​the actual flow path through which the refrigerant flows in the suction hole 59 to be reduced along the direction of refrigerant flow, even when the cylindrical body (connecting pipe 60) is disposed in the outer periphery-side suction hole 59o of the cylinder 21. Here, the actual flow path through which the refrigerant flows is the inside of the connecting pipe 60 on the outer periphery side of the suction hole 59, and is the inner periphery-side suction hole 59i on the inner periphery side of the suction hole 59.

[0080] 12 is a cross-sectional view showing a second example of arrangement of the cylindrical body and the inner suction hole 59i when the cylindrical body is placed in the suction hole 59 shown in FIG. In the second example of arrangement, as in the first example of arrangement, a connecting pipe 60 is placed in the outer suction hole 59o of the suction hole 59, connecting the suction pipe 2 to the suction hole 59. However, in the second example of arrangement shown in FIG. 12, a portion of the outline of the inner suction hole 59i is allowed to extend beyond the outline of the inner circumferential surface 60i of the connecting pipe 60 at a position closer to the vane groove 56 than the centroid 62 of the inner suction hole 59i (in FIG. 11, to the left of the vertical dashed line passing through the centroid 62). Even if a portion of the contour of the inner suction hole 59i is allowed to extend beyond the contour of the inner circumferential surface 60i of the connecting pipe 60 on the eccentric side of the centroid 62, the effect on the flow of the refrigerant is minimal, and allowing this makes it easier to ensure the eccentricity amount E of the centroid 62 of the inner suction hole 59i compared to the first arrangement example shown in Figure 11. This makes it possible to further advance the timing of the start of compression, thereby enhancing the effect of improving the volumetric efficiency of the compressor 1.

[0081] As described above, the compressor 1 according to the first embodiment is a compressor 1 that compresses a refrigerant in a compression mechanism 20 that has a compression chamber 58 and is disposed inside a sealed container 10 that is an outer shell. The compression mechanism 20 includes a cylinder 21 housed inside the sealed container 10, a rolling piston 22 that rotates eccentrically along an inner circumferential surface 21i of the cylinder 21, a vane 50 that divides a space (cylinder chamber 55) formed between the inner circumferential surface 21i of the cylinder 21 and an outer circumferential surface 22o of the rolling piston 22 into a suction chamber 57 where the refrigerant is drawn and a compression chamber 58 where the refrigerant is compressed, and a spring 51 that biases the vane 50 toward the rolling piston 22. The cylinder 21 is provided with a vane groove 56 that is formed to extend radially outward from the inner circumferential surface 21i of the cylinder 21 and in which the vane 50 is disposed, and a suction hole 59 that is formed to penetrate from the inner circumferential surface 21i to the outer circumferential surface 21o of the cylinder 21 and through which the refrigerant drawn into the suction chamber 57 flows. The suction hole 59 has an outer circumferential suction hole 59o connected to the outer circumferential surface 21o of the cylinder 21 and an inner circumferential suction hole 59i connected to the inner circumferential surface 21i of the cylinder 21, and is formed such that the contour of the inner circumferential suction hole 59i fits within the contour of the outer circumferential suction hole 59o when the suction hole 59 is viewed radially inward of the cylinder 21. When the suction hole 59 is viewed radially inward of the cylinder 21, the inner circumferential suction hole 59i has a vertically elongated non-circular shape in which an opening width Wr1 in the circumferential direction of the cylinder 21 is shorter than an opening width Wz1 in the thickness direction of the cylinder 21 (direction of arrow Z), and the centroid 62 of the inner circumferential suction hole 59i is eccentric to the vane groove 56 side relative to the centroid 61 of the outer circumferential suction hole 59o when viewed radially inward of the cylinder 21.

[0082] In this way, suction hole 59 is formed such that the contour of inner suction hole 59i fits within the contour of outer suction hole 59o when suction hole 59 is viewed radially inward of cylinder 21, inner suction hole 59i has a vertically elongated non-circular shape with an opening width Wr1 in the circumferential direction of cylinder 21 that is shorter than an opening width Wz1 in the thickness direction of cylinder 21 (direction of arrow Z), and a centroid 62 of inner suction hole 59i is eccentric toward vane groove 56 relative to centroid 61 of outer suction hole 59o in the circumferential direction of cylinder 21. Thus, as in the conventional case, the cross-sectional area of ​​inner suction hole 59i is secured to suppress pressure loss, and further, eccentricity of centroid 62 of inner suction hole 59i accelerates the timing at which rolling piston 22 passes through inner suction hole 59i, i.e., the start of compression, thereby improving the volumetric efficiency of compressor 1. As a result, the reduction in pressure loss and the improvement in volumetric efficiency are expected to result in a significant improvement in compression efficiency compared to conventional cases.

[0083] In addition, the opening (inner peripheral opening 59a) of the suction hole 59 on the inner peripheral surface 21i of the cylinder 21 has a straight portion 68 extending in the thickness direction of the cylinder 21 (direction of arrow Z) on the side of this opening farther from the vane groove 56.

[0084] As a result, when the rolling piston 22 passes through the straight portion 68 of the inner peripheral opening 59a, the suction chamber 57 is instantly closed to form the compression chamber 58. Therefore, a good balance can be achieved between suppressing delay in the start of compression and ensuring a sufficient amount of refrigerant to be compressed.

[0085] Furthermore, suction hole 59 has a tapered surface (connecting portion 70) connecting outer suction hole 59 o and inner suction hole 59 i. This prevents a sudden change in the cross-sectional area of ​​suction hole 59, and therefore, when refrigerant flows from outer suction hole 59 o to inner suction hole 59 i, the tapered surface of connecting portion 70 allows the flow to be smooth, thereby suppressing pressure loss.

[0086] Furthermore, the radial hole length L1 of the inner suction hole 59i at a position Pb closest to the vane groove 56 is greater than the radial hole length L2 of the inner suction hole 59i at a position Pf farthest from the vane groove 56. This makes it possible to secure a larger wall portion SW located between the suction hole 59 and the vane groove 56 in the cylinder 21, compared to a conventional configuration in which L1 = L2, thereby increasing the strength of the cylinder 21.

[0087] Furthermore, the centroid line CL61 of the outer suction hole 59o is oriented toward the center C21 of the cylinder 21 and is parallel to the centroid line CL62 of the inner suction hole 59i. This makes it easier to perform cutting and grinding finish processing on the outer suction hole 59o and the inner suction hole 59i during manufacturing of the cylinder 21, compared to a case in which the centroid line CL61 and the centroid line CL62 are not parallel.

[0088] Furthermore, when suction holes 59 are viewed radially inward of cylinder 21, step 69, which is the distance between the contour of outer suction hole 59o and the contour of inner suction hole 59i, is shortest at a position closer to vane groove 56 than centroid 62 of inner suction hole 59i. By providing step 69 in this manner, it is possible to achieve the configuration in which centroid 62 of inner suction hole 59i is eccentric toward vane groove 56 with respect to centroid 61 of outer suction hole 59o, as described above.

[0089] The compression mechanism 20 also includes a cylindrical body (e.g., a connecting pipe 60) disposed in the outer circumferential suction hole 59o of the suction hole 59. The cylindrical body and the suction hole 59 are arranged such that the outer circumferential surface of the cylindrical body contacts the inner circumferential surface of the outer circumferential suction hole 59o, and the contour of the inner circumferential suction hole 59i fits within the contour of the inner circumferential surface 60i of the cylindrical body when the cylindrical body and the suction hole 59 are viewed radially inward of the cylinder 21.

[0090] This allows the cross-sectional area of ​​the actual flow path through which the refrigerant flows in the suction hole 59 (the interior of the cylindrical body on the outer periphery side of the suction hole 59, and the inner periphery side suction hole 59i on the inner periphery side of the suction hole 59) to be configured to decrease along the direction in which the refrigerant flows. Therefore, the refrigerant can flow appropriately from the inside of the cylindrical body (for example, the connecting pipe 60) to the inner periphery side suction hole 59i.

[0091] The refrigeration cycle apparatus 200 according to the first embodiment includes the compressor 1, a radiator (e.g., indoor heat exchanger 204) from which the refrigerant compressed by the compressor 1 radiates heat, a pressure reducer 203 that reduces the pressure of the refrigerant that has radiated heat in the radiator, and an evaporator (e.g., outdoor heat exchanger 202) from which the refrigerant decompressed by the pressure reducer 203 evaporates. Thus, by using the compressor 1 with higher compression efficiency than conventional compressors, the capacity of the refrigeration cycle apparatus 200 is improved.

[0092] Second Embodiment Fig. 13 is a diagram showing the schematic configuration of a compression mechanism 20 used in a second embodiment. Fig. 14 is a partially enlarged view showing the structure around the suction hole 59 in the compression mechanism 20 of Fig. 13. The configuration of the second embodiment will be described using Figs. 13 and 14. In the second embodiment, the shape of the connection portion 170 of the suction hole 159 formed in the cylinder 21 is different from that in the first embodiment. Note that in the second embodiment, components having the same functions and actions as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted.

[0093] In the first embodiment described above, the outer circumferential suction hole 59o and the inner circumferential suction hole 59i of the suction hole 59 are connected via a connecting portion 70 which is a tapered surface. In the second embodiment, as shown in Figures 13 and 14, the connecting portion 170 between the outer circumferential suction hole 59o and the inner circumferential suction hole 59i of the suction hole 159 is an orthogonal surface which is orthogonal to the axis of the outer circumferential suction hole 59o.

[0094] In the second embodiment, as in the first embodiment, the outer periphery suction hole 59o extends radially toward the center C21 of the cylinder 21 and has a circular cross-sectional shape. Therefore, the axis of the outer periphery suction hole 59o is the centroid line CL61 of the outer periphery suction hole 59o.

[0095] Also, in the second embodiment, as in the first embodiment, when suction hole 159 is viewed radially inward of cylinder 21, the contour of inner suction hole 59i is contained within the contour of outer suction hole 59o, and centroid 62 of inner suction hole 59i is eccentric toward vane groove 56 compared to centroid 61 of outer suction hole 59o. In other words, step 169, which is connection 170 between outer suction hole 59o and inner suction hole 59i, is shortest at a position closer to vane groove 56 than centroid 62 of inner suction hole 59i.

[0096] As described above, in the compressor 1 according to the second embodiment, as in the first embodiment, the suction holes 159 are formed such that the contour of the inner suction holes 59i is contained within the contour of the outer suction holes 59o when the suction holes 159 are viewed radially inward of the cylinder 21, and the inner suction holes 59i have a vertically elongated non-circular shape, and the centroid 62 of the inner suction holes 59i is offset toward the vane groove 56 relative to the centroid 61 of the outer suction holes 59o in the circumferential direction of the cylinder 21. Therefore, in the compressor 1 according to the second embodiment, as in the first embodiment, the cross-sectional area of ​​the inner suction holes 59i is ensured, thereby suppressing pressure loss and accelerating the timing of the start of compression, thereby improving the volumetric efficiency of the compressor 1, and achieving a significant improvement in compression efficiency.

[0097] Furthermore, in the second embodiment, the outer periphery suction hole 59o and the inner periphery suction hole 59i are connected via an orthogonal surface (connection portion 170) that is orthogonal to the axis (centroid line CL61) of the outer periphery suction hole 59o. As a result, the orthogonal surface, that is, the connection portion 170, can be formed by forming the outer periphery suction hole 59o from the outer periphery side of the cylinder 21, and processing a tapered surface (i.e., an inclined surface) as in the first embodiment is not required. This simplifies the processing of the suction hole 159 in the cylinder 21.

[0098] Third Embodiment. FIG. 15 is a diagram showing a schematic configuration of a compression mechanism 20 used in a third embodiment. FIG. 16 is a cross-sectional view taken along the line E-E of the cylinder 21 in FIG. 15, showing a cross-section of the suction hole 59 near the inner circumferential surface 21i of the cylinder 21. The configuration of the third embodiment will be described using FIGS. 1, 15, and 16. The third embodiment differs from the second embodiment in that a groove is formed in the circumferential wall of the inner suction hole 59i of the cylinder 21. Note that in the third embodiment, components having the same functions and actions as those in the second embodiment are denoted by the same reference numerals, and their description will be omitted. The grooves of the third embodiment can also be applied to the first embodiment.

[0099] In the second embodiment, the suction hole 159 penetrates the cylinder radially but not in the cylinder thickness direction (arrow Z direction). In the third embodiment, as shown in Figures 15 and 16, a groove (hereinafter referred to as suction groove 71) that penetrates the cylinder thickness direction (arrow Z direction) is provided in the peripheral wall of the inner suction hole 59i.

[0100] Hereinafter, the suction groove 71 provided in the inner suction hole 59i of the upper first cylinder 21A of the two cylinders 21 shown in Figure 1 may be referred to as the first suction groove 71A, and the suction groove 71 provided in the inner suction hole 59i of the lower second cylinder 21B may be referred to as the second suction groove 71B.

[0101] As shown in FIG. 16 , the suction groove 71 is provided in the peripheral wall of the inner suction hole 59i, extending to the end face 21E of the cylinder 21. That is, the suction groove 71 connects the inner peripheral surface of the inner suction hole 59i to the end face 21E on one side in the thickness direction (Z direction) of the cylinder 21. Specifically, in the first cylinder 21A (see FIG. 1 ), a first suction groove 71A is formed in the peripheral wall of the inner suction hole 59i. The first suction groove 71A is connected to the upper end of the inner suction hole 59i and extends to the upper end face 21Au (see FIG. 1 ) of the first cylinder 21A. When the components of the compression mechanism 20 are fastened (see FIG. 1 ), the first suction groove 71A is closed by the lower end face of the upper bearing 24A (see FIG. 1 ). Furthermore, in the peripheral wall of the inner suction hole 59i of the second cylinder 21B (see FIG. 1), a second suction groove 71B is formed. The second suction groove 71B is connected to the lower end of the inner suction hole 59i and extends to the lower end surface 21Bl (see FIG. 1) of the second cylinder 21B. When the components of the compression mechanism 20 are fastened (see FIG. 1), the second suction groove 71B is closed by the upper end surface of the lower bearing 24B (see FIG. 1).

[0102] Even if the suction groove 71 is formed in the peripheral wall of the inner suction hole 59i in each cylinder 21 in this manner, extending to the end face 21E of the cylinder 21, the suction groove 71 is blocked by the upper bearing 24A or the lower bearing 24B shown in Figure 1, so that refrigerant does not leak through the suction groove 71 to the outside of the compression mechanism 20. Furthermore, by providing the suction groove 71 in the peripheral wall of the inner suction hole 59i, the flow path area can be expanded, and as a result, pressure loss can be reduced.

[0103] 16 , the suction groove 71 was defined as being provided only on one of the upper and lower sides of the inner suction hole 59i in each cylinder 21. However, the suction groove 71 may be provided on both the upper and lower sides of the inner suction hole 59i. Furthermore, the above description was defined as the first suction groove 71A being formed above the inner suction hole 59i in the first cylinder 21A and the second suction groove 71B being formed below the inner suction hole 59i in the second cylinder 21B. However, the arrangement of the suction grooves 71 is not limited to this. For example, the suction groove 71 may be provided above the inner suction hole 59i in both the first cylinder 21A and the second cylinder 21B.

[0104] The suction grooves 71 are provided throughout or in part of the inner suction hole 59i in the radial direction of the cylinder 21. In the example shown in FIG. 15 , the suction grooves 71 are provided only on the inner side of the inner suction hole 59i, including the inner opening 59a, and are not provided on the side of the inner suction hole 59i that is closer to the outer suction hole 59o. If the cross-sectional shape of the inner suction hole 59i that is closer to the outer suction hole 59o were to be irregular, the flow of refrigerant flowing from the outer suction hole 59o to the inner suction hole 59i could be disrupted, resulting in pressure loss. To avoid this, it is preferable to provide the suction grooves 71 only near the inner opening 59a. Furthermore, the main purpose of providing the suction grooves 71 is to facilitate the flow of refrigerant from the suction hole 59 to the cylinder chamber 55. To achieve this purpose, it is important to ensure a sufficient flow path area in the inner suction hole 59i, particularly near the inner opening 59a.

[0105] As described above, in the compressor 1 according to the third embodiment, as in the first and second embodiments, the suction hole 159 is formed such that the contour of the inner suction hole 59i fits within the contour of the outer suction hole 59o when the suction hole 159 is viewed radially inward of the cylinder 21, and the inner suction hole 59i has a vertically elongated non-circular shape, and the centroid 62 of the inner suction hole 59i is offset toward the vane groove 56 relative to the centroid 61 of the outer suction hole 59o in the circumferential direction of the cylinder 21. Therefore, in the compressor 1 according to the third embodiment, as in the first and second embodiments, the cross-sectional area of ​​the inner suction hole 59i is ensured, thereby suppressing pressure loss and accelerating the timing of the start of compression, thereby improving the volumetric efficiency of the compressor 1, and achieving a significant improvement in compression efficiency.

[0106] Furthermore, in the compressor 1 of the third embodiment, an intake groove 71 is formed in the peripheral wall of the inner suction hole 59i in the cylinder 21, connecting the inner suction hole 59i to the end face 21E of the cylinder 21. This increases the flow path area of ​​the intake flow path Pin (see FIG. 2) on the inner periphery of the cylinder 21, thereby reducing pressure loss.

[0107] Fourth Embodiment. FIG. 17 is a schematic diagram showing the configuration of a compression mechanism 20 used in a fourth embodiment. FIG. 18 is a cross-sectional view of the cylinder 21 of FIG. 17 taken along the line F-F, showing a cross section of the outer periphery-side suction hole 459o. The configuration of the fourth embodiment will be described using FIGS. 17 and 18 with reference to FIGS. 1 and 2. In the fourth embodiment, the shape of the outer periphery-side suction hole 459o of the suction holes 459 formed in the cylinder 21 and the shape of the connecting pipe 460 disposed in the outer periphery-side suction hole 459o are different from those in the second embodiment. Note that in the fourth embodiment, components having the same functions and actions as those in the second embodiment are denoted by the same reference numerals, and their description will be omitted. The shape of the outer periphery-side suction hole 459o and the shape of the connecting pipe 460 in the fourth embodiment can also be applied to the first and third embodiments.

[0108] In the second embodiment, the cross-sectional shape of the outer periphery suction hole 59o was circular. In the fourth embodiment, as shown in Figures 17 and 18, the cross-sectional shape of the outer periphery suction hole 459o is non-circular (i.e., vertically elongated) in which the opening width Wr2 in the cylinder circumferential direction is shorter than the opening width Wz2 in the cylinder thickness direction (direction indicated by arrow Z). As shown in Figure 17, the outer periphery suction hole 459o extends radially toward the center C21 of the cylinder 21, and the inner periphery suction hole 59i extends such that the centroid line CL62 of the inner periphery suction hole 59i is parallel to the centroid line CL461 of the outer periphery suction hole 459o.

[0109] 18, the cross-sectional shape of the inner suction hole 59i in the fourth embodiment is the same as that in the second embodiment. That is, the cross-sectional shape of the inner suction hole 59i is non-circular (i.e., vertically elongated) in which the opening width Wr1 in the cylinder circumferential direction is shorter than the opening width Wz1 in the cylinder thickness direction (direction of arrow Z).

[0110] Also, in the fourth embodiment, as in the second embodiment, when the suction hole 459 is viewed radially inward of the cylinder 21, the contour of the inner suction hole 59i is contained within the contour of the outer suction hole 459o, and the centroid 62 of the inner suction hole 59i is eccentric toward the vane groove 56 (to the left in FIG. 18 ) relative to the centroid 461 of the outer suction hole 459o. In other words, a step 469, which is a connection 470 between the outer suction hole 459o and the inner suction hole 59i, is shortest at a position closer to the vane groove 56 than the centroid 62 of the inner suction hole 59i. As shown in FIG. 17 , the connection 470 between the outer suction hole 459o and the inner suction hole 59i is an orthogonal plane perpendicular to the axis of the outer suction hole 459o (centroid line CL461 in the examples of FIGS. 17 and 18 ).

[0111] In the fourth embodiment, as shown in FIG. 18, the inner peripheral surface 460i of the connecting pipe 460 is non-circular (i.e., vertically elongated) so that the distance between the wall surfaces in the cylinder circumferential direction is shorter than the distance between the wall surfaces in the cylinder thickness direction (arrow Z direction).

[0112] In the example shown in FIGS. 17 and 18 , the inner circumferential surface 460i of the connecting pipe 460 has a first flat portion S1 extending linearly along the cylinder thickness direction (arrow Z direction) on the side closer to the vane groove 56, i.e., on the rear side in the rotation direction (arrow R direction) of the rolling piston 22 shown in FIG. 2 . The inner circumferential surface of the inner suction hole 59i has a second flat portion S2 extending linearly along the cylinder thickness direction (arrow Z direction) on the side closer to the vane groove 56. The first flat portion S1 on the inner circumferential surface 460i of the connecting pipe 460 and the second flat portion S2 on the inner circumferential surface of the inner suction hole 59i are configured to be flush with each other. This configuration can partially eliminate the step 469 from the connecting pipe 460 to the inner suction hole 59i, thereby smoothing the flow of refrigerant into the inner suction hole 59i and suppressing pressure loss.

[0113] As described above, in the compressor 1 according to the fourth embodiment, as in the first to third embodiments, the suction hole 459 is formed such that the contour of the inner suction hole 59i fits within the contour of the outer suction hole 459o when the suction hole 459 is viewed radially inward of the cylinder 21, and the inner suction hole 59i has a vertically elongated non-circular shape, and the centroid 62 of the inner suction hole 59i is offset toward the vane groove 56 relative to the centroid 461 of the outer suction hole 459o in the circumferential direction of the cylinder 21. Therefore, in the compressor 1 according to the fourth embodiment, as in the first to third embodiments, the cross-sectional area of ​​the inner suction hole 59i is ensured, thereby suppressing pressure loss and accelerating the timing of the start of compression, thereby improving the volumetric efficiency of the compressor 1, and achieving a significant improvement in compression efficiency.

[0114] Furthermore, in compressor 1 of embodiment 4, compression mechanism 20 includes a cylindrical body (e.g., connecting pipe 460) disposed in outer circumferential suction hole 459o of suction hole 459. The cylindrical body and suction hole 459 are arranged such that the outer circumferential surface of the cylindrical body contacts the inner circumferential surface of outer circumferential suction hole 459o, and the contour of inner circumferential suction hole 459i is contained within the contour of inner circumferential surface 460i of the cylindrical body when viewed radially inward of cylinder 21. When suction hole 459 is viewed radially inward of cylinder 21, outer circumferential suction hole 459o has a vertically elongated non-circular shape in which an opening width Wr2 in the circumferential direction of cylinder 21 is shorter than an opening width Wz2 in the thickness direction (direction of arrow Z) of cylinder 21, and inner circumferential surface 460i of the cylindrical body has a vertically elongated non-circular shape in which the distance between the wall surfaces in the circumferential direction of cylinder 21 is shorter than the distance between the wall surfaces in the thickness direction of cylinder 21. The inner peripheral surface 460i of the cylinder has a first flat surface S1 that extends linearly in the thickness direction of the cylinder 21 on the side closer to the vane groove 56, and the inner peripheral surface of the inner suction hole 59i has a second flat surface S2 that extends linearly in the thickness direction of the cylinder 21 on the side closer to the vane groove 56. The first flat surface S1 and the second flat surface S2 are provided flush with each other without any step 469.

[0115] In this way, the first flat surface S1 of the inner surface 460i of the cylindrical body (connecting pipe 460) and the second flat surface S2 of the inner surface of the inner suction hole 59i are flush with each other, which facilitates the flow of refrigerant and further reduces pressure loss.

[0116] Fifth Embodiment. Figure 19 is a longitudinal cross-sectional view showing the overall configuration of a compressor 1 according to a fifth embodiment. The configuration of the fifth embodiment will be described using Figure 19 and with reference to Figures 1 and 4. The fifth embodiment differs from the first embodiment in that the cylindrical bodies disposed in the suction holes 59 (first suction hole 59A, second suction hole 59B) of the cylinder 21 are suction pipes 502 (first suction pipe 502A, second suction pipe 502B). Note that in the fifth embodiment, components having the same functions and actions as those in the first embodiment are denoted by the same reference numerals, and their description will be omitted. The configuration of the fifth embodiment can also be applied to the second to fourth embodiments.

[0117] In the first embodiment described above, a first connecting pipe 60A is disposed in the first suction hole 59A of the upper first cylinder 21A to connect the first suction pipe 2A to the first suction hole 59A, and a second connecting pipe 60B is disposed in the second suction hole 59B of the lower second cylinder 21B to connect the second suction pipe 2B to the second suction hole 59B (see FIGS. 1 and 4). In the fifth embodiment, as shown in FIG. 19, a first suction pipe 502A is directly connected to the first suction hole 59A, and a second suction pipe 502B is directly connected to the second suction hole 59B. That is, in this embodiment 5, the ends of the suction pipes 502 (first suction pipes 502A, second suction pipes 502B) are arranged as cylindrical bodies in the outer suction holes 59o (see Figure 4) of the suction holes 59 (first suction hole 59A, second suction hole 59B) in the cylinders 21 (first cylinder 21A, second cylinder 21B).

[0118] In each cylinder 21, the shape of the end of the intake pipe 502 that is placed inside the intake hole 59 and the relationship between this end of the intake pipe 502 and other parts are similar to the shape of the connecting pipe 60 and the relationship between the connecting pipe 60 and other parts described in embodiment 1.

[0119] As described above, in the compressor 1 according to the fifth embodiment, as in the first embodiment, the suction holes 59 are formed so that the contour of the inner suction holes 59i is contained within the contour of the outer suction holes 59o when the suction holes 59 are viewed radially inward of the cylinder 21, and the inner suction holes 59i have a vertically elongated non-circular shape, and the centroid 62 of the inner suction holes 59i is offset toward the vane groove 56 relative to the centroid 61 of the outer suction holes 59o in the circumferential direction of the cylinder 21. Therefore, in the compressor 1 according to the fifth embodiment, as in the first embodiment, the cross-sectional area of ​​the inner suction holes 59i is ensured, thereby suppressing pressure loss and accelerating the timing of the start of compression, thereby improving the volumetric efficiency of the compressor 1, and achieving the effect of significantly improving the compression efficiency.

[0120] In the compressor 1 of the fifth embodiment, the cylindrical body disposed in the outer circumferential suction hole 59o is the end of the suction pipe 502 (the first suction pipe 502A and the second suction pipe 502B). As a result, in the fifth embodiment, the number of components constituting the compressor 1 can be reduced compared to the case where the connecting pipe 60 is provided as in the first embodiment.

[0121] 1 Compressor, 2A First suction pipe, 2B Second suction pipe, 3 Suction muffler, 4 Discharge piping, 6 Refrigerating machine oil, 10 Sealed container, 11 Head, 12 Body, 13 Bottom, 20 Compression mechanism, 21 Cylinder, 21A First cylinder, 21Al Lower end surface, 21Au Upper end surface, 21B Second cylinder, 21Bl Lower end surface, 21Bu Upper end surface, 21E End surface, 21i Inner peripheral surface, 21o Outer peripheral surface, 22 Rolling piston, 22A First rolling piston, 22B Second rolling piston, 22o Outer peripheral surface, 23A First muffler, 23B Second muffler, 24A Upper bearing, 24B Lower bearing, 25 Partition plate, 26 Screw, 30 Rotating electric machine, 31 Rotor, 32 Stator, 40 Rotating shaft, 40e End, 41 Eccentric shaft portion, 41A First eccentric shaft portion, 41B Second eccentric shaft portion, 42 Oil supply hole, 43 First oil supply port, 44 Second oil supply port, 45 Centrifugal pump, 50 Vane, 51 Spring, 54 Spring hole, 55 Cylinder chamber, 55A First cylinder chamber, 55B Second cylinder chamber, 56 Vane groove, 57 Suction chamber, 58 Compression chamber, 59 Suction hole, 59A First suction hole, 59B Second suction hole, 59a Inner circumference side opening, 59b Outer circumference side opening, 59i Inner circumference side suction hole, 59o Outer circumference side suction hole, 60 Connecting pipe, 60A First connecting pipe, 60B Second connecting pipe, 60i Inner circumference surface, 61 Centroid, 62 Centroid, 68 Straight portion, 69 Step, 70 Connecting portion, 71 Intake groove, 159 suction hole, 169 step, 170 connection portion, 200 refrigeration cycle device, 200A outdoor unit, 200B indoor unit, 201 four-way switching valve, 202 outdoor heat exchanger, 203 pressure reducer, 204 indoor heat exchanger, 459 suction hole, 459o outer circumferential suction hole, 460 connecting pipe, 460i inner circumferential surface, 461 centroid, 469 step, 470 connection portion, 502A first suction pipe, 502B second suction pipe, Ax rotation center, C21 cylinder center, CL461 centroid line, CL61 centroid line, CL62 centroid line, E eccentricity amount, Pin suction flow path, Pout discharge flow path, S1 first flat portion, S2 second flat portion, SW wall portion, Wr1 opening width, Wr2 Opening width, Wz1 opening width, Wz2 opening width, α taper angle, β taper angle.

Claims

1. A compressor which compresses a refrigerant in a compression mechanism having a compression chamber disposed inside a sealed container which is an outer shell, the compression mechanism comprising: a cylinder housed inside the sealed container; a rolling piston which rotates eccentrically along the inner circumferential surface of the cylinder; a vane which divides a space formed between the inner circumferential surface of the cylinder and the outer circumferential surface of the rolling piston into a suction chamber where the refrigerant is sucked in and the compression chamber where the refrigerant is compressed; and a spring which biases the vane towards the rolling piston; the cylinder is provided with a vane groove which is formed so as to extend radially outward from the inner circumferential surface of the cylinder and in which the vane is disposed, and a suction hole which is formed so as to penetrate from the inner circumferential surface to the outer circumferential surface of the cylinder and through which the refrigerant sucked into the suction chamber flows; The suction hole has an outer circumferential suction hole connected to the outer circumferential surface of the cylinder and an inner circumferential suction hole connected to the inner circumferential surface of the cylinder, and is formed such that the contour of the inner suction hole fits within the contour of the outer circumferential suction hole when viewed radially inward of the cylinder, wherein when the suction hole is viewed radially inward of the cylinder, the inner suction hole has a vertically elongated non-circular shape whose opening width in the circumferential direction of the cylinder is shorter than its opening width in the thickness direction of the cylinder, and the centroid of the inner suction hole is eccentric to the vane groove side relative to the centroid of the outer circumferential suction hole in the circumferential direction of the cylinder.

2. The compressor according to claim 1, wherein an opening of the suction hole in the inner peripheral surface of the cylinder has a straight portion extending in the thickness direction of the cylinder on a side of the opening farther from the vane groove.

3. A compressor according to claim 1 or 2, wherein the suction hole has a tapered surface connecting the outer circumferential side suction hole and the inner circumferential side suction hole.

4. The compressor according to claim 3, wherein the hole length in the radial direction at the position closest to the vane groove in the inner suction hole is greater than the hole length in the radial direction at the position furthest from the vane groove in the inner suction hole.

5. A compressor as claimed in any one of claims 1 to 4, wherein the centroid line of the outer circumferential suction hole is directed to the centre of the cylinder and is parallel to the centroid line of the inner circumferential suction hole.

6. A compressor as claimed in any one of claims 1 to 5, wherein a step, which is a distance between the contour of the outer circumferential suction hole and the contour of the inner circumferential suction hole when the suction hole is viewed radially inward of the cylinder, is shortest at a position on the vane groove side of the centroid of the inner circumferential suction hole.

7. The compressor according to any one of claims 1 to 6, wherein a suction groove is formed in the peripheral wall of the inner suction hole in the cylinder, connecting the inner suction hole and an end face of the cylinder.

8. A compressor as described in any one of claims 1 to 7, wherein the compression mechanism comprises a cylinder placed in the outer circumferential suction hole of the suction hole, and the cylinder and the suction hole are arranged such that the outer circumferential surface of the cylinder contacts the inner circumferential surface of the outer circumferential suction hole, and the contour of the inner circumferential suction hole fits within the contour of the inner circumferential surface of the cylinder when the cylinder and the suction hole are viewed radially inward of the cylinder.

9. The compressor described in claim 8, wherein, when the suction hole is viewed radially inward of the cylinder, the outer suction hole has a vertically elongated non-circular shape with an opening width in the circumferential direction of the cylinder shorter than the opening width in the thickness direction of the cylinder, the inner surface of the cylindrical body has a vertically elongated non-circular shape with a distance between the wall surfaces in the circumferential direction of the cylinder shorter than the distance between the wall surfaces in the thickness direction of the cylinder and has a first flat surface on a side closer to the vane groove that extends linearly in the thickness direction of the cylinder, and the inner surface of the inner suction hole has a second flat surface on a side closer to the vane groove that extends linearly in the thickness direction of the cylinder, and the first flat surface and the second flat surface are provided flush with each other without any steps.

10. A refrigeration cycle device comprising: a compressor according to any one of claims 1 to 9; a radiator in which the refrigerant compressed by the compressor radiates heat; a pressure reducer that reduces the pressure of the refrigerant whose heat has been radiated by the radiator; and an evaporator in which the refrigerant depressurized by the pressure reducer evaporates.

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