Rotary compressor and apparatus

Abstract

The utility model provides a rotary compressor (1) and equipment using the rotary compressor, a compression mechanism part (30) is provided with a cylinder (31), a piston (32) configured in the cylinder and blades (33) for separating the inside of the cylinder, a shaft (40) is provided with an eccentric part (42), a blade groove (36) for configuring the blades is formed on the cylinder (31), the eccentric part (42) is configured in the cylinder, the piston (32) is embedded with the eccentric part (42), and the blade groove (36) is embedded with the eccentric part (42). A cylindrical groove (32a) having an arc angle alpha exceeding 180 DEG is formed in the piston (32), a cylindrical portion (33b) disposed in the cylindrical groove (32a) is formed at an end of the vane (33), the vane (33) operates without leaving the piston (32), and the Vickers hardness of the surface of the piston (32) is set to Hv400 or less, thereby facilitating formation of the cylindrical groove (32a) in the piston (32), and the wear resistance of the piston (32) and the vane (33) is high.

Description

TECHNICAL FIELD

[0001] The utility model relates to a rotary compressor whose vane does not leave the piston to act and an apparatus using the rotary compressor. BACKGROUND

[0002] Patent Document 1 discloses a rotary compressor in which a vane does not leave a piston to act by forming a cylindrical groove in the piston and forming a cylindrical portion of the vane at the end portion to be arranged in the cylindrical groove.

[0003] In addition, in order to make the sliding property of the vane good, the piston is subjected to a solidification treatment for improving the surface hardness by heat treatment or surface coating (Patent Document 2).

[0004] PRIOR ART DOCUMENTS

[0005] PATENT DOCUMENTS

[0006] Patent Document 1: Japanese Patent Application Publication No. H3-185291

[0007] Patent Document 2: Japanese Patent Application Publication No. H7-145787 SUMMARY

[0008] PROBLEMS TO BE SOLVED BY THE INVENTION

[0009] As the piston described in Patent Document 1, it is difficult to form a circular-arc-shaped groove in the outer peripheral portion of the piston subjected to the solidification treatment. In the machining of the piston subjected to the solidification treatment, the material structure sometimes falls off from the surface of the piston. In addition, the life of the tool used for the machining of the piston is reduced. Further, the machining time of the piston is too long.

[0010] In a general rotary compressor, the vane that slides in the vane groove is subjected to high-hardness surface treatment.

[0011] When the vane subjected to the high-hardness surface treatment slides against the piston, the sliding portion of the piston not subjected to the solidification treatment is abraded.

[0012] Therefore, the object of the utility model is to provide a rotary compressor in which a cylindrical groove is easily formed in a piston and the piston and the vane have high abrasion resistance and an apparatus using the rotary compressor.

[0013] METHOD FOR SOLVING THE PROBLEMS

[0014] The utility model discloses a first aspect provides a kind of rotary compressor 1 is provided with motor portion 20 and compression mechanism portion 30 in closed container 10, the motor portion 20 and the compression mechanism portion 30 are connected by shaft 40, the compression mechanism portion 30 has cylinder 31, piston 32 configured in the cylinder 31, and vane 33 separating the cylinder 31, the shaft 40 has eccentric portion 42, the vane slot 36 of the vane 33 is formed on the cylinder 31, the eccentric portion 42 is configured in the cylinder 31, the piston 32 is embedded with the eccentric portion 42, the cylindrical slot 32a of the circular arc angle α exceeding 180 ° is formed on the piston 32, the cylindrical portion 33b configured in the cylindrical slot 32a is formed in the end of the vane 33, the vane 33 does not act away from the piston 32, and the rotary compressor 1 is characterized in that the vickers hardness of the surface of the piston 32 is set to Hv400 or less.

[0015] The rotary compressor 1 of the second aspect of the utility model is characterized in that the piston 32 is made of gray cast iron material on the basis of the first aspect.

[0016] The rotary compressor 1 of the third aspect of the utility model is characterized in that the side surface of the vane 33 is surface treated, and the vickers hardness of the side surface of the vane 33 exceeds Hv1000 on the basis of the first or second aspect.

[0017] The rotary compressor 1 of the fourth aspect of the utility model is characterized in that the surface treatment is nitriding treatment or DLC treatment on the basis of the third aspect.

[0018] The fifth aspect of the utility model provides a kind of equipment, which uses the rotary compressor 1 described in the first or second aspect, and is characterized in that the rotary compressor 1, condenser 2, pressure reducing device 3 and evaporator 4 are connected into annular shape by piping.

[0019] Utility model effect

[0020] According to the utility model, since the piston uses low-hardness material, the cylindrical slot is easily formed, and the surface bearing formed by the cylindrical portion and the cylindrical slot is also high in wear resistance. BRIEF DESCRIPTION OF DRAWINGS

[0021] Figure 1 It is the sectional view of the rotary compressor of one embodiment of the utility model.

[0022] Figure 2 It is Figure 1 The A-A line view shown.

[0023] Figure 3 It is the drawing for piston and vane of rotary compressor of same embodiment.

[0024] Figure 4 FIG. 1 is a view showing a manufacturing process of a vane for a rotary compressor according to an embodiment.

[0025] BRIEF DESCRIPTION OF DRAWINGS

[0026] 1 rotary compressor

[0027] 2 condenser

[0028] 3 pressure reducing device

[0029] 4 evaporator

[0030] 10 hermetic container

[0031] 11 oil reservoir

[0032] 12 suction pipe

[0033] 13 discharge pipe

[0034] 14 accumulator

[0035] 14a outer cylinder

[0036] 14b refrigerant suction pipe

[0037] 14c separation plate

[0038] 14d outer cylinder inlet

[0039] 14e suction pipe inlet

[0040] 14f liquid reservoir

[0041] 20 motor portion

[0042] 21 stator

[0043] 22 rotor

[0044] 30 compression mechanism portion

[0045] 31 cylinder

[0046] 32 piston

[0047] 32a cylindrical groove

[0048] 33 vane

[0049] 33a vane side portion

[0050] 33b cylindrical portion

[0051] 33c narrowed portion

[0052] 33d notch portion

[0053] 33e circular arc surface

[0054] 33e1 suction side circular arc surface

[0055] 33e2 discharge side circular arc surface

[0056] 34 compression chamber

[0057] 34a suction space

[0058] 34b compression space

[0059] 35 suction passage

[0060] 36 vane groove

[0061] 37 discharge hole

[0062] 40 shaft

[0063] 41 main shaft portion

[0064] 42 eccentric portion

[0065] 43 sub shaft portion

[0066] 46 shaft inner oil supply passage

[0067] 47 communication passage

[0068] 51 upper bearing

[0069] 52 lower bearing

[0070] 53 upper cover

[0071] 54 sound deadening chamber

[0072] H height

[0073] M connecting surface

[0074] X extended imaginary surface

[0075] Y jig

[0076] Z cutting tool

[0077] α, β, γ circular arc angle DETAILED DESCRIPTION

[0078] The rotary compressor of the first embodiment of the present application sets the Vickers hardness of the surface of the piston to Hv400 or less. According to the present embodiment, since the piston uses a low hardness member, a cylindrical groove is easily formed, and since the surface formed by the cylindrical portion and the cylindrical groove is received, the wear resistance is also high.

[0079] The second embodiment of the present application is based on the rotary compressor of the first embodiment, and the piston is made of gray cast iron. According to the second embodiment, the cylindrical groove is easily formed.

[0080] The third embodiment of the present application is based on the rotary compressor of the first or second embodiment, and the side surface of the vane is surface-treated, and the Vickers hardness of the side surface of the vane exceeds Hv1000. According to the third embodiment, the vane groove has sufficient sliding resistance.

[0081] The fourth embodiment of the present application is based on the rotary compressor of the third embodiment, and the surface treatment is nitriding treatment or DLC treatment. According to the fourth embodiment, the nitriding treatment or DLC treatment is suitable for the hard coating treatment.

[0082] The fifth embodiment of the present application is based on the rotary compressor of the first or second embodiment, and the rotary compressor, the condenser, the pressure reducing device, and the evaporator are connected in a ring shape by piping. According to the fifth embodiment, the device having high reliability can be provided.

[0083]

Embodiment

[0084] Figure 1 is a cross-sectional view of the rotary compressor of the embodiment of the present application, Figure 2 is Figure 1 the A-A line view shown in FIG. 1.

[0085] The rotary compressor 1 of the embodiment includes a motor portion 20 and a compression mechanism portion 30 in a hermetic container 10. The motor portion 20 and the compression mechanism portion 30 are connected by a shaft 40.

[0086] The motor portion 20 is composed of a stator 21 fixed to the inner surface of the hermetic container 10 and a rotor 22 rotating in the stator 21.

[0087] The compression mechanism portion 30 has a cylinder 31, a piston 32 arranged in the cylinder 31, and a vane 33 (refer to FIG. 1) partitioning the inside of the cylinder 31. Figure 2 ).

[0088] An upper bearing 51 is arranged on one side of the cylinder 31, and a lower bearing 52 is arranged on the other side of the cylinder 31.

[0089] The shaft 40 is composed of a main shaft portion 41 on which the rotor 22 is mounted and which is supported by the upper bearing 51, an eccentric portion 42 for mounting the piston 32, and a sub shaft portion 43 supported by the lower bearing 52.

[0090] The upper bearing 51 is fixed to the hermetic container 10. The piston 32 is fitted to the eccentric portion 42 of the shaft 40 penetrating the inside of the cylinder 31 so as to be rotatable.

[0091] An upper cover 53 is provided on an upper portion of the upper bearing 51. A sound deadening chamber 54 is formed between the upper bearing 51 and the upper cover 53. The high-pressure refrigerant gas compressed by the compression mechanism portion 30 is discharged into the sound deadening chamber 54. The high-pressure refrigerant gas discharged into the sound deadening chamber 54 is discharged into the sealed container 10.

[0092] An oil reservoir portion 11 is formed in a bottom portion of the sealed container 10. The oil reservoir portion 11 stores refrigerant oil. An inner shaft oil supply passage 46 is formed in an inner portion of the shaft 40 in an axial direction. A communication passage 47 for supplying refrigerant oil to sliding surfaces of the compression mechanism portion 30 is formed in an inner portion of the eccentric portion 42.

[0093] The refrigerant oil in the oil reservoir portion 11 is introduced into the inner shaft oil supply passage 46 from a lower end of the shaft 40. A portion of the refrigerant oil introduced into the inner shaft oil supply passage 46 is supplied to the sliding surfaces of the compression mechanism portion 30 from the communication passage 47.

[0094] An intake pipe 12 is connected to a side surface of the sealed container 10, and a discharge pipe 13 is connected to an upper surface of the sealed container 10. The intake pipe 12 guides refrigerant to the compression mechanism portion 30. The discharge pipe 13 guides refrigerant compressed by the compression mechanism portion 30 and discharged into the sealed container 10 to the outside of the sealed container 10.

[0095] A reservoir 14 is provided on an upstream side of the intake pipe 12.

[0096] In the rotary compressor 1 of the present 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 refrigerant discharged from the discharge pipe 13. The pressure reducing device 3 reduces the pressure of refrigerant condensed by the condenser 2. The evaporator 4 evaporates refrigerant reduced in pressure by the pressure reducing device 3.

[0097] Refrigerant evaporated by the evaporator 4 is returned to the reservoir 14.

[0098] The reservoir 14 has an outer cylinder 14a, a refrigerant intake pipe 14b, and a separation plate 14c. The outer cylinder 14a has an outer cylinder inlet 14d for introducing refrigerant from the evaporator 4 in an upper portion thereof. The refrigerant intake pipe 14b has an intake pipe inlet 14e in an inner portion of the outer cylinder 14a. The separation plate 14c is disposed between the outer cylinder inlet 14d and the intake pipe inlet 14e.

[0099] A liquid storage portion 14f is formed in an inner bottom portion of the outer cylinder 14a. Liquid refrigerant is stored in the liquid storage portion 14f. The liquid refrigerant can be stored up to a height H of the intake pipe inlet 14e. Therefore, the height H of the intake pipe inlet 14e becomes the volume of the liquid storage portion 14f.

[0100] Further, the specific driving method of the rotary compressor 1 is not particularly limited. For example, the rotary compressor 1 can be driven by simple on-off control, but can also be inverter-driven at multiple operating frequencies. In inverter driving, a low-rotation region in which the rotational speed of the motor portion 20 is reduced or a high-rotation region in which the rotational speed of the motor portion 20 is increased is generated in order to optimize the motion control of the rotary compressor 1.

[0101] Figure 2 The compression chamber 34 is formed between the upper bearing 51 and the lower bearing 52 and between the inner peripheral surface of the cylinder 31 and the outer peripheral surface of the piston 32.

[0102] The suction pipe 12 is connected to the suction passage 35 of the compression mechanism portion 30.

[0103] The suction passage 35 is connected to the compression chamber 34.

[0104] The piston 32 performs a revolution motion by the rotation of the shaft 40.

[0105] The vane 33 is reciprocated in the vane groove 36 by the piston 32 that performs a revolution motion along the inner wall surface of the cylinder 31.

[0106] The compression chamber 34 is divided by the vane 33 into a suction space 34a that communicates with the suction passage 35 and a compression space 34b that communicates with the discharge hole 37. The suction volume formed in the cylinder 31 is the volume of the suction space 34a in a state in which the suction passage 35 is occluded by the piston 32, and is the volume in a state in which the suction space 34a becomes a maximum space.

[0107] The gas refrigerant that has passed through the suction passage 35 from the suction pipe 12 and has been sucked into the compression chamber 34 by the revolution motion of the piston 32 is discharged into the muffling chamber 54 from the discharge hole 37 after being compressed by the compression chamber 34.

[0108] The refrigerant gas that has been discharged into the muffling chamber 54 is discharged into the sealed container 10, and is discharged from the discharge pipe 13 to the outside of the sealed container 10. The high-pressure refrigerant gas that has been discharged to the outside of the sealed container 10 becomes a low-pressure refrigerant gas via the condenser 2, the pressure-reducing device 3, and the evaporator 4, and is returned to the compression mechanism portion 30 via the accumulator 14.

[0109] Figure 3 is a view showing a piston and a vane for a rotary compressor according to the embodiment, Figure 3 (a) is a perspective view in which the piston and the vane are in a separated state, Figure 3 (b) is a plan view in which the piston and the vane are in a separated state, Figure 3 (c) is a perspective view in which the vane is viewed from a different direction.

[0110] A cylindrical groove 32a of which the circular arc angle α exceeds 180° is formed in the outer peripheral surface of the piston 32. The cylindrical groove 32a is formed from one end surface to the other end surface of the piston 32.

[0111] The vane 33 has a vane side surface portion 33a which slides with the vane groove 36, a cylindrical portion 33b which is arranged in the cylindrical groove 32a, and a narrowed portion 33c which connects the vane side surface portion 33a and the cylindrical portion 33b. The cylindrical portion 33b is formed in the end portion of the vane 33.

[0112] By engaging the cylindrical portion 33b with the cylindrical groove 32a, the vane 33 operates without departing from the piston 32.

[0113] A notch portion 33d is formed in the cylindrical portion 33b from one end surface to the other end surface of the cylindrical portion 33b. The cylindrical portion 33b divides the circular arc surface 33e of the cylindrical portion 33b into a plurality of portions by the notch portion 33d. In this way, the circular arc surface 33e which is divided into at least two portions by the notch portion 33d is formed in the outer peripheral surface of the cylindrical portion 33b.

[0114] Each of the circular arc surfaces 33e is set to a circular arc angle β which is greater than 90° and less than 180°, and the notch portion 33d is set to a circular arc angle γ which is less than 45°. Further, the circular arc angle β is preferably 110° or more and 150° or less.

[0115] By setting the notch portion 33d to the circular arc angle γ which is less than 45°, the contact area of the cylindrical groove 32a and the cylindrical portion 33b can be increased, and refrigerant leakage can be reliably prevented.

[0116] In the present embodiment, the notch portion 33d is formed in the vane front end portion of the vane 33. That is, the notch portion 33d is formed in the front end of the cylindrical portion 33b. Since it is difficult to apply a load to the vane front end portion, by forming the notch portion 33d in the vane front end portion, the suction side circular arc surface 33el and the discharge side circular arc surface 33e2 can be formed symmetrically by the notch portion 33d. Further, in the present embodiment, the notch portion 33d is formed in a flat surface, but as long as the notch portion 33d is cut inward from the circular arc outer peripheral surface of the cylindrical portion 33b, it can also be formed in a curved surface, and can also be formed in one flat surface.

[0117] It is preferable that the two circular arc surfaces 33e which are formed are arranged in the position closest to the extended imaginary surface X from the side surface of the vane side surface portion 33a. In this way, since the point of the side surface of the vane side surface portion 33a in the cylindrical portion 33b which is closest to the extended imaginary surface X is located on the circular arc surface 33e, refrigerant leakage can be reliably prevented.

[0118] The Vickers hardness of the surface of the piston 32 is set to Hv400 or less. Since the piston 32 itself uses a low hardness member, the cylindrical groove 32a is easily formed, and the wear resistance is also high due to the face support by the cylindrical portion 33b and the cylindrical groove 32a.

[0119] The Vickers hardness of the surface of the piston 32 is preferably set to a range of Hv80 to Hv400, and more preferably a range of Hv180 to Hv250.

[0120] The piston 32 preferably uses a gray cast iron material. Since the gray cast iron material is used, the cylindrical groove 32a is easily formed. In addition, the piston 32 can be formed of a sintered material. In the case where the piston 32 uses a sintered material, the Vickers hardness is preferably set to Hv400 or less.

[0121] The blade side portion 33a, that is, the side surface of the blade 33 is surface treated, and the side surface of the blade 33 is set to a hardness exceeding Hv1000. Thus, sufficient sliding resistance with respect to the blade groove 36 can be obtained.

[0122] The nitriding treatment or the DLC treatment is suitable for the surface treatment of the blade side portion 33a. By performing the nitriding treatment or the DLC treatment, the blade side portion 33a can be subjected to the hard coating treatment.

[0123] The surface hardness of at least a portion of the cylindrical portion 33b is lower than the surface hardness of the blade side portion 33a. In addition, the at least a portion of the cylindrical portion 33b refers to the arc surface 33e. The same applies to the following description. In this way, by making the surface hardness of at least a portion of the cylindrical portion 33b lower than the surface hardness of the blade side portion 33a, the machinability and the toughness of the cylindrical portion 33b can be improved, and the sliding resistance with respect to the blade groove 36 can be obtained.

[0124] The Vickers hardness of at least a portion of the cylindrical portion 33b is preferably Hv200 or more lower than the Vickers hardness of the blade side portion 33a. That is, by subjecting the blade side portion 33a to the hard coating treatment, the Vickers hardness of the blade side portion 33a is made Hv200 or more higher than the Vickers hardness of at least a portion of the cylindrical portion 33b, and sufficient sliding resistance with respect to the blade groove 36 can be obtained.

[0125] In addition, the surface hardness of the narrowed portion 33c is lower than the surface hardness of the blade side portion 33a. In this way, by making the surface hardness of the narrowed portion 33c lower than the surface hardness of the blade side portion 33a, the machinability and the toughness of the narrowed portion 33c can be improved, and the sliding resistance with respect to the blade groove 36 can be obtained by making the surface hardness of the blade side portion 33a higher than the surface hardness of the narrowed portion 33c.

[0126] Further, the surface hardness of the narrowed portion 33c is preferably lower than the surface hardness of the cylindrical portion 33b. By making the surface hardness of the narrowed portion 33c lower than the surface hardness of the vane side portion 33a or the cylindrical portion 33b, the machinability and toughness of the narrowed portion 33c can be improved. In addition, the surface hardness of the circular arc surface 33e is preferably lower than the surface hardness of the notched portion 33d. By making the surface hardness of the circular arc surface 33e lower than the surface hardness of the notched portion 33d, the machinability and toughness of the circular arc surface 33e can be improved.

[0127] Figure 4 is a view showing a manufacturing process of a vane for a rotary compressor according to the embodiment.

[0128] Figure 4 (a) shows a base material of the vane 33, and the vane 33 uses an iron alloy in which iron (Fe) is a main component and chromium (Cr) is contained, or a steel material in which chromium (Cr), tungsten (W), vanadium (V), molybdenum (Mo), or the like is added to a high carbon steel material. Further, since the vane 33 uses a steel material in which tungsten (W) and vanadium (V) are not added, low cost can be achieved. In addition, the vane 33 can use stainless steel (for example, SUS440C).

[0129] Figure 4 (b) shows a state in which the base material of the vane 33 shown in (a) is subjected to hard coating treatment. Figure 4 (a) shows a state in which the base material of the vane 33 shown in (a) is subjected to hard coating treatment.

[0130] As shown in (c), the base material of the vane 33 subjected to hard coating treatment is fixed to the jig Y, and the cylindrical portion 33b and the narrowed portion 33c are machined by the cutting tool Z. Figure 4 As shown in (c), in order to form the cylindrical portion 33b in which the circular arc angle a exceeds 180°, finish machining needs to be performed in two or more times, and the machining accuracy at the connecting surface M of the machined surfaces decreases.

[0131] Figure 4 However, by dividing the circular arc surface 33e of the cylindrical portion 33b into a plurality of portions by the notched portion 33d, by making each of the circular arc surfaces 33e have a circular arc angle β of less than 180°, the machining accuracy of the circular arc surface 33e of the cylindrical portion 33b can be improved.

[0132] In particular, by forming the notched portion 33d at the connecting surface M, that is, the front end of the cylindrical portion 33b, machining can be performed by only two times of finish machining, that is, finish machining of the suction side circular arc surface 33el and finish machining of the discharge side circular arc surface 33e2.

[0133] In particular, by forming the notched portion 33d at the connecting surface M, that is, the front end of the cylindrical portion 33b, machining can be performed by only two times of finish machining, that is, finish machining of the suction side circular arc surface 33el and finish machining of the discharge side circular arc surface 33e2.

[0134] ​The working fluid and the refrigerant oil described in the present embodiment are in a two-phase separated state under temperature conditions of 25°C. Thus, particularly, even in a case where liquid compression operation cannot be avoided by using refrigerant oil having low phase solubility with the working fluid in the low rotation region of the rotary compressor 1, lubrication performance can be ensured, and a good sliding state can be maintained. Here, the low rotation region refers to a rotation speed region of 900 rpm or less, particularly 600 rpm or less, and further 360 rpm or less. In the low rotation region, liquid compression is easily generated, and by ensuring lubrication performance in the low rotation region where liquid compression is easily generated, operation in the low rotation region, i.e., low capacity operation, can be stably performed.

[0135] In addition, under temperature conditions of 0°C to 25°C, the proportion of the working fluid in the mixture in which the refrigerant oil maximally dissolves the working fluid is 1 wt% or more and less than 30 wt%. Thus, particularly, even in a case where liquid compression operation cannot be avoided by using refrigerant oil having low phase solubility with the working fluid in the low rotation region, lubrication performance can be ensured, and a good sliding state can be maintained.

[0136] In the present embodiment, the accumulator 14 is described as being included in the upstream of the suction pipe 12, but the accumulator 14 can be omitted. That is, even in a case where liquid compression operation cannot be avoided by using refrigerant oil having low phase solubility with the working fluid, lubrication performance of the refrigerant oil can be ensured, and a good sliding state can be maintained, so the accumulator 14 can not be provided.

[0137] In addition, the volume of the liquid storage portion 14f of the accumulator 14 can be set to be 2 times or less the suction volume formed in the cylinder 31. That is, even in a case where liquid compression operation cannot be avoided by using refrigerant oil having low phase solubility with the working fluid, lubrication performance can be ensured, and a good sliding state can be maintained, so the accumulator 14 can be made smaller.

[0138] In addition, in the present embodiment, the compression mechanism portion 30 is described as being composed of one cylinder 31 and one piston 32, but the compression mechanism portion 30 can be composed of two cylinders 31 and two pistons 32. From the viewpoint that the rotary compressor with two pistons is suitable for low speed operation, it is also preferable that each vane 33 act without leaving each piston 32.

[0139] In addition, as a device using the rotary compressor 1 suitable for low speed operation, for example, in an air conditioning device, an indoor air conditioner (a household air conditioner) is particularly suitable.

[0140] As described in the present embodiment, according to the compression mechanism portion 30 in which the vane 33 acts without leaving the piston 32, a highly efficient rotary compressor can be realized.

[0141] In particular, by setting the working fluid to R32 and the refrigerant oil to alkylbenzene oil, the solubility is low, the lubricating performance can be ensured, and a good sliding state can be maintained. In addition, the same applies to a working fluid containing at least R32.

[0142] In addition, by setting the working fluid to carbon dioxide and the refrigerant oil to polyalkylene glycol oil, the solubility is low, the lubricating performance can be ensured, and a good sliding state can be maintained. In addition, the same applies to a working fluid containing at least carbon dioxide.

[0143] In addition, by setting the working fluid to R290 and the refrigerant oil to polyalkylene glycol oil, the solubility is low, the lubricating performance can be ensured, and a good sliding state can be maintained. In addition, the same applies to a working fluid containing at least R290.

[0144] In addition, the kinematic viscosity of the refrigerant oil is preferably 35 mm / s or less, for example, in the case where the working fluid contains carbon dioxide or R290, it can also be a refrigerant oil having a kinematic viscosity exceeding 35 mm / s.

[0145] In addition, the rotary compressor in which the vane 33 operates without leaving the piston 32 can use R1234yf or HFO1123, a working fluid containing R1234yf, or a working fluid containing HFO1123. From the viewpoint of lubricating performance, in R1234yf or a working fluid containing R1234yf, it is preferable to set the refrigerant oil to alkylbenzene oil, and in HFO1123 or a working fluid containing HFO1123, it is preferable to set the refrigerant oil to ester oil or essential oil.

[0146] The device of the present 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 has high reliability.

[0147] Industrial availability

[0148] The device using the rotary compressor of the present application is useful as a hot water heating device, an air conditioning device, a water heater, a refrigerator, a display case, a cooler, a dehumidifier, or a refrigerator, etc.

Claims

1. A rotary compressor characterized by comprising: a motor portion and a compression mechanism portion provided in a closed container, the motor portion and the compression mechanism portion being connected by a shaft, the compression mechanism portion having a cylinder, a piston disposed in the cylinder, and a vane partitioning the cylinder, the shaft having an eccentric portion, a vane groove for disposing the vane being formed in the cylinder, the eccentric portion being disposed in the cylinder, the piston being fitted to the eccentric portion, a cylindrical groove having a circular arc angle of more than 180° being formed in the piston, a cylindrical portion disposed in the cylindrical groove being formed in an end portion of the vane, the vane being operated without leaving the piston, and a surface of the piston having a Vickers hardness of Hv400 or less.

2. The rotary compressor according to claim 1, characterized in that: the piston is made of gray cast iron material.

3. The rotary compressor according to claim 1 or 2, characterized in that: a side surface of the vane is surface-treated, and the side surface of the vane has a Vickers hardness of more than Hv1000.

4. The rotary compressor according to claim 3, characterized in that: the surface treatment is nitriding treatment or DLC treatment.

5. An apparatus characterized by comprising: the rotary compressor according to claim 1 or 2, and a condenser, a pressure-reducing device, and an evaporator connected in a ring shape by piping. ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​

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