Rotary compressors and equipment

Abstract

To provide a rotary compressor that has a vane with sliding resistance against a vane groove and can improve the workability and toughness of a cylindrical portion, and a device using this rotary compressor. [Solution] The compression mechanism section 30 has a cylinder 31, a piston 32, and a vane 33. The shaft 40 has an eccentric section 42. The cylinder 31 has a vane groove 36 in which the vane 33 is disposed. The eccentric section 42 is disposed within the cylinder 31. The piston 32 is fitted into the eccentric section 42. The piston 32 has a cylindrical groove 32a with an arc angle exceeding 180°. The end of the vane 33 has a cylindrical section 33b disposed in the cylindrical groove 32a. The vane 33 operates without being separated from the piston 32. The vane 33 has a vane side section 33a which slides against the vane groove 36. The surface hardness of at least a part of the cylindrical section 33b is made lower than the surface hardness of the vane side section 33a.

Description

[Technical field]

[0001] The present invention relates to a rotary compressor in which vanes operate without being separated from pistons, and to a device using this rotary compressor. [Background technology]

[0002] Patent Document 1 discloses a rotary compressor in which a cylindrical groove is formed in the piston and a cylindrical portion is formed at the end of the vane to be placed in the cylindrical groove, thereby enabling the vane to operate without separating from the piston. Furthermore, the vanes, particularly the ends of the vanes, are subjected to a hardening treatment to increase the surface hardness by heat treatment or surface coating (Patent Document 2). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 3-185291 [Patent Document 2] Japanese Patent Application Publication No. 7-145787 Summary of the Invention [Problem to be solved by the invention]

[0004] Finishing a highly hardened vane with high precision requires a great deal of technical and time effort, and in particular, in compressors where the vane is fitted to the piston, it is not easy to carry out high-precision processing that leaves a high-hardness layer on the cylindrical part at the end of the vane.

[0005] Therefore, an object of the present invention is to provide a rotary compressor that has the sliding resistance of the vanes against the vane grooves and can improve the workability and toughness of the cylindrical portion, and a device using this rotary compressor. [Means for solving the problem]

[0006] The rotary compressor 1 of the present invention described in claim 1 includes an electric motor unit 20 and a compression mechanism unit 30 in a sealed container 10, the electric motor unit 20 and the compression mechanism unit 30 are connected by a shaft 40, the compression mechanism unit 30 includes a cylinder 31, a piston 32 arranged in the cylinder 31, and a vane 33 that divides the inside of the cylinder 31, the shaft 40 has an eccentric portion 42, the cylinder 31 is formed with a vane groove 36 in which the vane 33 is arranged, the eccentric portion 42 is arranged in the cylinder 31, and the piston 32 is arranged in the cylinder 31. The rotary compressor 1 is characterized in that the piston 32 is fitted into the eccentric portion 42, the piston 32 is formed with a cylindrical groove 32a having an arc angle exceeding 180°, and the end of the vane 33 is formed with a cylindrical portion 33b disposed in the cylindrical groove 32a, and the vane 33 operates without separating from the piston 32, and the vane 33 has a vane side portion 33a that slides against the vane groove 36, and the surface hardness of at least a part of the cylindrical portion 33b is made lower than the surface hardness of the vane side portion 33a. The present invention described in claim 2 is characterized in that, in the rotary compressor 1 described in claim 1, the Vickers hardness of at least the part of the cylindrical portion 33b is lower by Hv200 or more than the Vickers hardness of the vane side portion 33a. The present invention as set forth in claim 3 is characterized in that in the rotary compressor 1 as set forth in claim 1 or claim 2, the vane side surface portion 33a is subjected to a hard coating treatment. A fourth aspect of the present invention is characterized in that, in the rotary compressor 1 according to the third aspect, the hard coating treatment is a nitriding treatment or a DLC treatment. The present invention described in claim 5 is characterized in that, in the rotary compressor 1 described in claim 1 or claim 2, the vane 33 has a constricted portion 33c connecting the vane side portion 33a and the cylindrical portion 33b, and the surface hardness of the constricted portion 33c is made lower than the surface hardness of the vane side portion 33a. The equipment of the present invention described in claim 6 is an equipment using the rotary compressor 1 described in claim 1 or claim 2, characterized in that the rotary compressor 1, the condenser 2, the pressure reducing device 3, and the evaporator 4 are connected in a circular shape by piping. Effect of the Invention

[0007] According to the present invention, by making the surface hardness of the vane side portion higher than that of the cylindrical portion, it is possible to provide sliding resistance to the vane groove, and by making the surface hardness of the cylindrical portion lower than that of the vane side portion, it is possible to improve the workability and toughness of the cylindrical portion. [Brief description of the drawings]

[0008] [Figure 1] FIG. 1 is a cross-sectional view showing a rotary compressor according to an embodiment of the present invention. [Diagram 2] AA line arrow view shown in Figure 1 [Diagram 3] FIG. 2 is a diagram showing a piston and a vane used in the rotary compressor according to the embodiment. [Figure 4] 5A and 5B are diagrams showing a manufacturing process of a vane used in the rotary compressor according to the embodiment; DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] In a rotary compressor according to a first embodiment of the present invention, the vane has a vane side portion that slides against the vane groove, and the surface hardness of at least a part of the cylindrical portion is made lower than the surface hardness of the vane side portion. According to this embodiment, by making the surface hardness of the vane side portion higher than the surface hardness of at least a part of the cylindrical portion, it is possible to provide sliding resistance against the vane groove, and by making the surface hardness of at least a part of the cylindrical portion lower than the surface hardness of the vane side portion, it is possible to improve the workability and toughness of the cylindrical portion.

[0010] In the second embodiment of the present invention, in the rotary compressor according to the first embodiment, the Vickers hardness of at least a part of the cylindrical portion is lower than the Vickers hardness of the vane side surface portion by Hv200 or more. According to this embodiment, it is possible to provide the vane groove with sufficient sliding resistance.

[0011] In a third embodiment of the present invention, in the rotary compressor according to the first or second embodiment, a hard coating is applied to the side surface of the vane. According to this embodiment, the hard coating can provide the vane with resistance to sliding.

[0012] A fourth embodiment of the present invention is a rotary compressor according to the third embodiment, wherein the hard coating treatment is a nitriding treatment or a DLC treatment. According to this embodiment, the nitriding treatment or the DLC treatment is suitable for the hard coating treatment.

[0013] In a fifth embodiment of the present invention, in the rotary compressor according to the first or second embodiment, the vane has a constricted portion connecting the vane side portion and the cylindrical portion, and the surface hardness of the constricted portion is made lower than that of the vane side portion. According to this embodiment, by making the surface hardness of the constricted portion lower than that of the vane side portion, the workability and toughness of the constricted portion can be improved, and by making the surface hardness of the vane side portion higher than that of the constricted portion, it is possible to provide sliding resistance to the vane groove.

[0014] The sixth embodiment of the present invention is an apparatus using the rotary compressor according to the first or second embodiment, in which the rotary compressor, a condenser, a pressure reducing device, and an evaporator are connected in a circular manner by piping. According to this embodiment, a highly reliable apparatus can be provided. EXAMPLES

[0015] FIG. 1 is a cross-sectional view showing a rotary compressor according to an embodiment of the present invention, and FIG. 2 is a view taken along line AA shown in FIG. The rotary compressor 1 according to this embodiment includes an electric motor unit 20 and a compression mechanism unit 30 in a sealed container 10. The electric motor unit 20 and the compression mechanism unit 30 are connected by a shaft 40. The electric motor section 20 is composed of a stator 21 fixed to the inner surface of the sealed container 10 and a rotor 22 that rotates within the stator 21 . The compression mechanism 30 has a cylinder 31, a piston 32 disposed in the cylinder 31, and a vane 33 (see FIG. 2) that divides the inside of the cylinder 31. An upper bearing 51 is disposed on one surface of the cylinder 31, and a lower bearing 52 is disposed on the other surface of the cylinder 31. The shaft 40 is made up of a main shaft portion 41 to which the rotor 22 is attached and which is supported by an upper bearing 51 , an eccentric portion 42 to which the piston 32 is attached, and a counter shaft portion 43 which is supported by a lower bearing 52 . The upper bearing 51 is fixed to the sealed container 10. The piston 32 is fitted to the eccentric portion 42 of the shaft 40 which passes through the cylinder 31 so as to be able to rotate freely. An upper cover 53 is provided on the upper bearing 51. A sound-absorbing chamber 54 is formed between the upper bearing 51 and the upper cover 53. High-pressure refrigerant gas compressed by the compression mechanism 30 is discharged into the sound-absorbing chamber 54. The high-pressure refrigerant gas discharged into the sound-absorbing chamber 54 is discharged into the sealed container 10.

[0016] An oil reservoir 11 is formed at the bottom of the sealed container 10. The oil reservoir 11 stores refrigeration oil. An oil supply passage 46 in the axial direction is formed inside the shaft 40. A communication passage 47 for supplying refrigeration oil to the sliding surface of the compression mechanism 30 is formed inside the eccentric portion 42. The refrigeration oil in the oil reservoir 11 is introduced into the shaft oil supply passage 46 from the lower end of the shaft 40. A part of the refrigeration oil introduced into the shaft oil supply passage 46 is supplied to the sliding surface of the compression mechanism 30 from a communication passage 47. A suction pipe 12 is connected to the side of the sealed container 10, and a discharge pipe 13 is connected to the top of the sealed container 10. The suction pipe 12 guides the refrigerant to the compression mechanism 30. The discharge pipe 13 guides the refrigerant compressed by the compression mechanism 30 and discharged into the sealed container 10 to the outside of the sealed container 10. An accumulator 14 is provided upstream of the suction pipe 12 .

[0017] In the rotary compressor 1 according to this embodiment, a condenser 2, a pressure reducing device 3, and an evaporator 4 are connected in a ring shape by piping. The condenser 2 condenses the refrigerant discharged from a discharge pipe 13. The pressure reducing device 3 reduces the pressure of the refrigerant condensed by the condenser 2. The evaporator 4 evaporates the refrigerant reduced in pressure by the pressure reducing device 3. The refrigerant evaporated in the evaporator 4 is returned to the accumulator 14. The accumulator 14 has an external cylinder 14a, a refrigerant suction pipe 14b, and a separation plate 14c. An external cylinder inlet 14d is provided at the top of the external cylinder 14a, through which the refrigerant from the evaporator 4 is introduced. The refrigerant suction pipe 14b has a suction pipe inlet 14e inside the external cylinder 14a. The separation plate 14c is disposed between the external cylinder inlet 14d and the suction pipe inlet 14e. A liquid reservoir 14f is formed at the inner bottom of the outer cylinder 14a. The liquid refrigerant is stored in the liquid reservoir 14f. The liquid refrigerant can be stored up to the height H of the suction pipe inlet 14e. Therefore, the volume of the liquid reservoir 14f is up to the height H of the suction pipe inlet 14e. Note that there is no particular limitation on the specific driving method of the rotary compressor 1. For example, the rotary compressor 1 may be driven by simple on-off control, or may be inverter-driven at a plurality of operating frequencies. In the inverter drive, in order to optimize the operation control of the rotary compressor 1, a low rotation region where the rotation speed of the electric motor unit 20 decreases or a high rotation region where the rotation speed of the electric motor unit 20 increases occurs.

[0018] The compression chamber 34 shown in FIG. 2 is formed between the inner circumferential surface of the cylinder 31 and the outer circumferential surface of the piston 32 between the upper bearing 51 and the lower bearing 52 . The suction pipe 12 is connected to a suction passage 35 of the compression mechanism 30 . The suction passage 35 is connected to the compression chamber 34 . Rotation of the shaft 40 causes the piston 32 to revolve. The vane 33 reciprocates in the vane groove 36 due to the piston 32 revolving along the inner wall surface of the cylinder 31 . Compression chamber 34 is divided by vane 33 into suction space 34a communicating with suction passage 35 and compression space 34b communicating with discharge hole 37. The suction volume formed in cylinder 31 is the volume of suction space 34a when suction passage 35 is blocked by piston 32, and is the volume when suction space 34a is at its maximum space. The gas refrigerant is drawn into the compression chamber 34 through the suction passage 35 from the suction pipe 12 by the revolution of the piston 32, and is compressed in the compression chamber 34 and then discharged from the discharge hole 37 into the muffling chamber 54. The refrigerant gas discharged into the sound-absorbing chamber 54 is discharged into the sealed container 10 and then discharged from the discharge pipe 13 to the outside of the sealed container 10. The high-pressure refrigerant gas discharged to the outside of the sealed container 10 passes through the condenser 2, the pressure reducing device 3, and the evaporator 4, becomes a low-pressure refrigerant gas, and is returned to the compression mechanism 30 via the accumulator 14.

[0019] FIG. 3 shows a piston and vane used in the rotary compressor of the same embodiment, where FIG. 3(a) is an oblique view of the piston and vane separated from each other, FIG. 3(b) is a plan view of the piston and vane separated from each other, and FIG. 3(c) is an oblique view of the vane seen from a different direction.

[0020] A cylindrical groove 32a having an arc angle α of more than 180° is formed on the outer circumferential surface of the piston 32. The cylindrical groove 32a extends from one end face of the piston 32 to the other end face. The vane 33 has a vane side surface portion 33a that slides in the vane groove 36, a cylindrical portion 33b that is disposed in the cylindrical groove 32a, and a constricted portion 33c that connects the vane side surface portion 33a and the cylindrical portion 33b. The cylindrical portion 33b is formed at the end of the vane 33. By engaging the cylindrical portion 33b with the cylindrical groove 32a, the vane 33 operates without being separated from the piston 32. The cylindrical portion 33b has a cutout 33d formed therein, which extends from one end face of the cylindrical portion 33b to the other end face thereof. The cutout 33d divides the arcuate surface 33e of the cylindrical portion 33b into a plurality of parts. In this manner, the outer peripheral surface of the cylindrical portion 33b has an arcuate surface 33e separated into at least two parts by the cutout 33d. Each of the arcuate surfaces 33e has an arcuate angle β of less than 180°, and each of the cutout portions 33d has an arcuate angle γ of less than 45°. By forming the cutout portion 33d at an arc angle γ of less than 45°, the contact area between the cylindrical groove 32a and the cylindrical portion 33b can be increased, and refrigerant leakage can be reliably prevented. In this embodiment, the notch 33d is formed at the vane tip of the vane 33. That is, the notch 33d is formed at the tip of the cylindrical portion 33b. Since the vane tip is not easily subjected to load, the notch 33d can form the suction side arc surface 33e1 and the discharge side arc surface 33e2 symmetrically by forming the notch 33d at the vane tip. In this embodiment, the notch 33d is formed as a flat surface, but the notch 33d may be a curved surface or may not be formed as a single flat surface as long as it is cut out so that the inner surface is closer to the arc-shaped outer circumferential surface of the cylindrical portion 33b. It is preferable to dispose the two arc surfaces 33e formed at positions closest to the virtual plane X extending from the side surface of the vane side surface portion 33a. In this way, since the point in the cylindrical portion 33b closest to the virtual plane X extending from the side surface of the vane side surface portion 33a is located on the arc surfaces 33e, refrigerant leakage can be reliably prevented.

[0021] The Vickers hardness of the surface of the piston 32 is set to Hv 400 or less. By using a low hardness material for the piston 32, the cylindrical groove 32a can be easily formed, and the surface support between the cylindrical portion 33b and the cylindrical groove 32a provides high wear resistance. The Vickers hardness of the surface of the piston 32 is preferably in the range of Hv80 to Hv400, and more preferably in the range of Hv180 to Hv250. The piston 32 is preferably made of gray cast iron, which makes it easier to form the cylindrical groove 32a.

[0022] The vane side surface portion 33a, i.e., the side surface of the vane 33, is subjected to a surface treatment so that the side surface of the vane 33 has a Vickers hardness exceeding Hv1000. Therefore, the vane groove 36 can have sufficient sliding resistance. Nitriding or DLC treatment is suitable for the surface treatment of the vane side surface portion 33a. By carrying out the nitriding or DLC treatment, the vane side surface portion 33a can be hard-coated.

[0023] The surface hardness of at least a part of the cylindrical portion 33b is lower than the surface hardness of the vane side surface portion 33a. Note that at least a part of the cylindrical portion 33b is the arc surface 33e. The same applies to the following description. In this way, by making the surface hardness of at least a part of the cylindrical portion 33b lower than the surface hardness of the vane side surface portion 33a, the cylindrical portion 33b has sliding resistance against the vane groove 36, and by making the surface hardness of at least a part of the cylindrical portion 33b lower than the surface hardness of the vane side surface portion 33a, the cylindrical portion 33b can have improved workability and toughness. It is preferable that the Vickers hardness of at least a part of the cylindrical portion 33b is lower by Hv200 or more than the Vickers hardness of the vane side surface portion 33a. In other words, by performing a hard coating process on the vane side surface portion 33a, the Vickers hardness of the vane side surface portion 33a can be made higher by Hv200 or more than the Vickers hardness of at least a part of the cylindrical portion 33b, and sufficient sliding resistance can be provided to the vane groove 36. The surface hardness of the constricted portion 33c is set lower than the surface hardness of the vane side surface portion 33a. By making the surface hardness of the constricted portion 33c lower than the surface hardness of the vane side surface portion 33a, the workability and toughness of the constricted portion 33c can be improved, and by making the surface hardness of the vane side surface portion 33a higher than the surface hardness of the constricted portion 33c, the vane groove 36 can be provided with sliding resistance. The surface hardness of the constricted portion 33c is preferably lower than that of the cylindrical portion 33b. By making the surface hardness of the constricted portion 33c lower than that of the vane side portion 33a and the cylindrical portion 33b, the workability and toughness of the constricted portion 33c can be improved. Furthermore, the surface hardness of the arcuate surface 33e is preferably lower than that of the cutout portion 33d. By making the surface hardness of the arcuate surface 33e lower than that of the cutout portion 33d, the workability and toughness of the arcuate surface 33e can be improved.

[0024] FIG. 4 is a diagram showing a manufacturing process of the vane used in the rotary compressor according to the embodiment. FIG. 4(a) shows the base material of the vane 33. The vane 33 is made of an iron alloy mainly composed of iron (Fe) and containing chromium (Cr), or a high-carbon steel material to which metal materials such as chromium (Cr), tungsten (W), vanadium (V), and molybdenum (Mo) are added. FIG. 4(b) shows a state in which the base material of the vane 33 shown in FIG. 4(a) has been subjected to a hard coating treatment. As shown in FIG. 4(c), the base material of the vane 33 that has been subjected to the hard coating treatment is fixed to a jig Y, and a cutting tool Z is used to machine the cylindrical portion 33b and the narrowed portion 33c. As shown in FIG. 4(c), in order to form a cylindrical portion 33b with an arc angle α exceeding 180°, finishing must be performed in two or more steps, which reduces the machining accuracy at the joint M of the machined surface. However, by dividing arcuate surface 33e of cylindrical portion 33b into a plurality of portions by cutout portion 33d and setting each arcuate surface 33e to an arc angle β of less than 180°, the machining accuracy of arcuate surface 33e of cylindrical portion 33b can be improved. In particular, by forming the notch 33d at the connecting surface M, i.e., the tip of the cylindrical portion 33b, the machining can be performed by just two finishing processes, that is, the finishing process for the suction side arcuate surface 33e1 and the finishing process for the discharge side arcuate surface 33e2.

[0025] The working fluid and the refrigerating machine oil described as the refrigerant in this embodiment are in a two-phase separation state at a temperature condition of 25°C. In this way, by using a refrigerating machine oil that is less compatible with the working fluid, particularly in the low rotation range of the rotary compressor 1, it is possible to ensure lubricating performance and maintain a good sliding state even when liquid compression operation is unavoidable. Here, the low rotation range is a rotation speed range of 900 rpm or less, particularly 600 rpm or less. In the low rotation range, liquid compression is likely to occur, and by ensuring lubricating performance in the low rotation range where liquid compression is likely to occur, operation in the low rotation range, i.e., low capacity operation, can be performed stably. Moreover, in a mixture in which the working fluid is dissolved to the maximum extent in the refrigeration oil under temperature conditions of 0° C. to 25° C., the ratio of the working fluid is 1 wt % or more and less than 30 wt %. In this way, by using a refrigeration oil that has low compatibility with the working fluid, especially in the low rotation range, it is possible to ensure lubricating performance and maintain a good sliding state even in cases where liquid compression operation is unavoidable.

[0026] In this embodiment, the accumulator 14 is provided upstream of the suction pipe 12, but the accumulator 14 can be eliminated. In other words, by using a refrigerating machine oil that has low compatibility with the working fluid, even in the case where liquid compression operation is unavoidable, the lubricating performance of the refrigerating machine oil can be ensured and a good sliding state can be maintained, so that the accumulator 14 does not need to be provided. In addition, the volume of the liquid reservoir 14f of the accumulator 14 can be set to be equal to or less than twice the suction volume formed in the cylinder 31. That is, by using a refrigeration oil that has low compatibility with the working fluid, even in cases where liquid compression operation is unavoidable, lubricating performance can be ensured and a good sliding state can be maintained, so that the accumulator 14 can be made smaller.

[0027] In particular, by using R32 as the working fluid and alkylbenzene oil as the refrigeration oil, compatibility is low, lubricating performance can be ensured, and a good sliding condition can be maintained. In addition, by using carbon dioxide as the working fluid and polyalkylene glycol oil as the refrigeration oil, compatibility is low, lubricating performance can be ensured, and a good sliding state can be maintained. In addition, by using R290 as the working fluid and polyalkylene glycol oil as the refrigeration oil, compatibility is low, lubricating performance can be ensured, and a good sliding condition can be maintained. The refrigeration oil preferably has a kinetic viscosity of 35 mm / s or less.

[0028] The equipment according to this embodiment, in which the rotary compressor 1, the condenser 2, the pressure reducing device 3, and the evaporator 4 are connected in a ring shape by piping, is highly reliable. [Industrial Applicability]

[0029] An apparatus using the rotary compressor of the present invention is useful as a refrigeration cycle apparatus such as a hot water heating apparatus, an air conditioner, a water heater, a refrigerator, a showcase, a chiller, a dehumidifier, or a refrigerator. [Explanation of symbols]

[0030] 1 Rotary Compressor 2 Condenser 3 Pressure reducing device 4. Evaporator 10. Airtight containers 11 Oil Sump 12 Suction pipe 13 Discharge pipe 14 Accumulator 14a External cylinder 14b Refrigerant suction pipe 14c Separation plate 14d External cylinder inlet 14e Suction pipe inlet 14f Liquid reservoir 20 Electric motor section 21 Stator 22 Rotor 30 Compression mechanism 31 Cylinder 32 Piston 32a Cylindrical groove 33 Vane 33a Vane side part 33b Cylinder section 33c Waist 33d Cutout 33e Circular surface 33e1 Intake side arc surface 33e2 Discharge side arc surface 34 Compression chamber 34a Suction space 34b Compressed Space 35 Suction passage 36 Vane groove 37 Discharge hole 40 Shaft 41 Main shaft part 42 Eccentric part 43 Secondary shaft part 46 Oil supply passage in shaft 47 Communication path 51 Upper bearing 52 Lower bearing 53 Top cover 54 Sound deadening room H Height M Joint surface X-extended virtual plane Y jig Z cutting tool α, β, γ arc angles

Claims

1. A motor unit and a compression mechanism unit are provided in a sealed container, The electric motor unit and the compression mechanism unit are connected by a shaft, The compression mechanism includes a cylinder, a piston disposed in the cylinder, and a vane that divides the inside of the cylinder. The shaft has an eccentric portion, A vane groove in which the vane is disposed is formed in the cylinder, The eccentric portion is disposed within the cylinder, The piston is fitted to the eccentric portion, The piston is provided with a cylindrical groove having an arc angle of more than 180°. A cylindrical portion is formed at an end of the vane and is disposed in the cylindrical groove; A rotary compressor in which the vanes operate without separating from the pistons, The vane has a vane side surface portion that slides in the vane groove, The surface hardness of at least a part of the cylindrical portion is made lower than the surface hardness of the vane side portion. A rotary compressor characterized by:

2. The Vickers hardness of at least the part of the cylindrical portion is lower by Hv200 or more than the Vickers hardness of the vane side surface portion.

2. The rotary compressor according to claim 1 .

3. The vane side surface is hard-coated.

3. The rotary compressor according to claim 1 or 2.

4. The hard coating treatment is a nitriding treatment or a DLC treatment.

4. The rotary compressor according to claim 3.

5. The vane has a constricted portion connecting the vane side portion and the cylindrical portion, The surface hardness of the constricted portion is made lower than the surface hardness of the vane side portion.

3. The rotary compressor according to claim 1 or 2.

6. An apparatus using the rotary compressor according to claim 1 or 2, The rotary compressor, the condenser, the pressure reducing device, and the evaporator are connected in a ring shape by piping. The device characterized by:

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