Rotary compressor and apparatus

Abstract

A rotary compressor (1) and an apparatus using the same are provided. A compression mechanism section (30) has a cylinder (31), a piston (32), and a vane (33). A shaft (40) has an eccentric portion (42). A vane groove (36) in which the vane is arranged is formed on the cylinder. The eccentric portion is arranged in the cylinder. The piston is fitted to the eccentric portion. A cylindrical groove (32a) having a circular arc angle of more than 180° is formed on the piston. A cylindrical portion (33b) arranged in the cylindrical groove is formed on an end portion of the vane. The vane operates without leaving the piston. By having a vane side portion (33a) that slides with the vane groove (36) on the vane (33), and by making the surface hardness of at least a portion of the cylindrical portion (33b) lower than the surface hardness of the vane side portion (33a), the vane (33) can have sliding resistance with respect to the vane groove (36), and the processability and toughness of the cylindrical portion (33b) can be improved.

Description

TECHNICAL FIELD

[0001] The present application relates to a rotary compressor in which a vane does not move away from a piston, and an apparatus using the same. BACKGROUND

[0002] Patent Document 1 discloses a rotary compressor in which a vane does not move away from a piston by forming a cylindrical groove on a piston and forming a cylindrical portion on an end portion of the vane to be fitted in the cylindrical groove.

[0003] Further, a solidification treatment for improving the surface hardness by heat treatment or surface coating is applied to the vane, particularly the end portion of the vane (Patent Document 2).

[0004] PRIOR ART DOCUMENTS

[0005] PATENT DOCUMENTS

[0006] Patent Document 1: Japanese Patent Application Laid-Open No. 3-185291

[0007] Patent Document 2: Japanese Patent Application Laid-Open No. 7-145787 SUMMARY

[0008] PROBLEMS TO BE SOLVED BY THE INVENTION

[0009] It is technically and time consuming to process a vane, which becomes high hardness, with high precision, and particularly in a compressor in which the vane is fitted in the piston, it is not easy to process the cylindrical portion on the end portion of the vane with high precision leaving a high hardness layer.

[0010] Therefore, an object of the present application is to provide a rotary compressor in which the sliding resistance of a vane with respect to a vane groove is improved and the processability and toughness of a cylindrical portion are improved, and an apparatus using the same.

[0011] METHOD FOR SOLVING THE PROBLEMS

[0012] The rotary compressor 1 according to the first aspect of the present application has a motor portion 20 and a compression mechanism portion 30 in a closed container 10, the motor portion 20 and the compression mechanism portion 30 are connected by a shaft 40, the compression mechanism portion 30 has a cylinder 31, a piston 32 disposed in the cylinder 31, and a vane 33 that divides the cylinder 31, the shaft 40 has an eccentric portion 42, a vane groove 36 in which the vane 33 is disposed is formed on the cylinder 31, the eccentric portion 42 is disposed in the cylinder 31, the piston 32 is fitted to the eccentric portion 42, a cylindrical groove 32a having an angle of more than 180° is formed on the piston 32, a cylindrical portion 33b is formed on an end portion of the vane 33 and is disposed in the cylindrical groove 32a, the vane 33 operates without leaving the piston 32, and the rotary compressor 1 is characterized in that the vane 33 has a vane side surface portion 33a that slides with the vane groove 36, and the surface hardness of at least a portion of the cylindrical portion 33b is lower than the surface hardness of the vane side surface portion 33a.

[0013] The rotary compressor 1 according to the second aspect of the present application is based on the first aspect, and is characterized in that the Vickers hardness of at least the portion of the cylindrical portion 33b is lower than the Vickers hardness of the vane side surface portion 33a by more than Hv200.

[0014] The rotary compressor 1 according to the third aspect of the present application is based on the first or second aspect, and is characterized in that the vane side surface portion 33a is subjected to hard coating treatment.

[0015] The rotary compressor 1 according to the fourth aspect of the present application is based on the third aspect, and is characterized in that the hard coating treatment is nitriding treatment or DLC treatment.

[0016] The rotary compressor 1 according to the fifth aspect of the present application is based on the first or second aspect, and is characterized in that the vane 33 has a narrowed portion 33c that connects the vane side surface portion 33a and the cylindrical portion 33b, and the surface hardness of the narrowed portion 33c is lower than the surface hardness of the vane side surface portion 33a.

[0017] The apparatus according to the sixth aspect of the present application uses the rotary compressor 1 according to the first or second aspect, and is characterized in that the rotary compressor 1, a condenser 2, a pressure reducing device 3, and an evaporator 4 are connected in a ring shape by piping.

[0018] Effects of the Invention

[0019] According to the present application, by making the surface hardness of the vane side surface portion higher than the surface hardness of the cylindrical portion, it is possible to have resistance to sliding with respect to the vane groove, and by making the surface hardness of the cylindrical portion lower than the surface hardness of the vane side surface portion, it is possible to improve the machinability and toughness of the cylindrical portion. BRIEF DESCRIPTION OF DRAWINGS

[0020] Figure 1 is a sectional view of a rotary compressor showing an embodiment of the present application.

[0021] Figure 2 is Figure 1 the A-A line view shown.

[0022] Figure 3 is a view showing a piston and a vane for a rotary compressor according to the embodiment.

[0023] Figure 4 is a view showing a manufacturing process of a vane for a rotary compressor according to the embodiment.

[0024] BRIEF DESCRIPTION OF DRAWINGS

[0025] 1 rotary compressor

[0026] 2 condenser

[0027] 3 pressure reducing device

[0028] 4 evaporator

[0029] 10 closed container

[0030] 11 oil storage portion

[0031] 12 suction pipe

[0032] 13 discharge pipe

[0033] 14 accumulator

[0034] 14a outer cylinder

[0035] 14b refrigerant suction pipe

[0036] 14c separation plate

[0037] 14d outer cylinder inlet

[0038] 14e suction pipe inlet

[0039] 14f oil storage portion

[0040] 20 motor portion

[0041] 21 stator

[0042] 22 rotor

[0043] 30 compression mechanism portion

[0044] 31 cylinder

[0045] 32 piston

[0046] 32a cylindrical groove

[0047] 33 blade

[0048] 33a blade side portion

[0049] 33b cylindrical portion

[0050] 33c narrowed portion

[0051] 33d notch portion

[0052] 33e circular arc surface

[0053] 33e1 suction side circular arc surface

[0054] 33e2 discharge side circular arc surface

[0055] 34 compression chamber

[0056] 34a suction space

[0057] 34b compression space

[0058] 35 suction passage

[0059] 36 blade groove

[0060] 37 discharge hole

[0061] 40 shaft

[0062] 41 main shaft portion

[0063] 42 eccentric portion

[0064] 43 sub shaft portion

[0065] 46 oil supply passage in shaft

[0066] 47 communication passage

[0067] 51 upper bearing

[0068] 52 lower bearing

[0069] 53 upper cover

[0070] 54 sound deadening chamber

[0071] H height

[0072] M connecting surface

[0073] X extended imaginary surface

[0074] Y jig

[0075] Z cutting tool

[0076] α, β, γ circular arc angles DETAILED DESCRIPTION

[0077] The rotary compressor of the first embodiment of the present application has a vane side portion that slides with respect to the vane groove on the vane, and the surface hardness of at least a portion of the cylindrical portion is lower than the surface hardness of the vane side portion. According to the present embodiment, by making the surface hardness of the vane side portion higher than the surface hardness of at least a portion of the cylindrical portion, it is possible to have resistance to sliding with respect to the vane groove, and by making the surface hardness of at least a portion of the cylindrical portion lower than the surface hardness of the vane side portion, it is possible to improve the machinability and toughness of the cylindrical portion.

[0078] The second embodiment of the present application makes the Vickers hardness of at least a portion of the cylindrical portion lower than the Vickers hardness of the vane side portion by 200 Hv or more, on the basis of the rotary compressor of the first embodiment. According to the present embodiment, it is possible to have sufficient resistance to sliding with respect to the vane groove.

[0079] The third embodiment of the present application performs hard coating treatment on the vane side portion, on the basis of the rotary compressor of the first or second embodiment. According to the present embodiment, by the hard coating treatment, it is possible to have resistance to sliding.

[0080] The fourth embodiment of the present application makes the hard coating treatment be nitriding treatment or DLC treatment, on the basis of the rotary compressor of the third embodiment. According to the present embodiment, nitriding treatment or DLC treatment is suitable for the hard coating treatment.

[0081] The fifth embodiment of the present application has a narrowed portion that connects the vane side portion and the cylindrical portion on the vane, on the basis of the rotary compressor of the first or second embodiment, and the surface hardness of the narrowed portion is lower than the surface hardness of the vane side portion. According to the present embodiment, by making the surface hardness of the narrowed portion lower than the surface hardness of the vane side portion, it is possible to improve the machinability and toughness of the narrowed portion, and by making the surface hardness of the vane side portion higher than the surface hardness of the narrowed portion, it is possible to have resistance to sliding with respect to the vane groove.

[0082] The sixth embodiment of the present application is an apparatus that uses the rotary compressor of the first or second embodiment, in which the rotary compressor, the condenser, the pressure reducing device, and the evaporator are connected in a ring shape by piping. According to the present embodiment, it is possible to provide an apparatus with high reliability.

[0083]

EXAMPLE

[0084] Figure 1 is a cross-sectional view of a rotary compressor of an 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 present 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 coupled by a shaft 40.

[0086] The motor portion 20 is composed of a stator 21 fixed to an 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 disposed in the cylinder 31, and a vane 33 partitioning the cylinder 31 (see FIG. 2). Figure 2 ).

[0088] An upper bearing 51 is disposed on one side of the cylinder 31, and a lower bearing 52 is disposed 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 rotatably fitted to the eccentric portion 42 of the shaft 40 penetrating the cylinder 31.

[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. 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 hermetic container 10.

[0092] An oil reservoir portion 11 is formed in a bottom portion of the hermetic 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 hermetic container 10, and a discharge pipe 13 is connected to an upper surface of the hermetic 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 hermetic container 10 to the outside of the hermetic 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, the condenser 2, the pressure reducing device 3, and the evaporator 4 are connected in a ring shape by piping. The condenser 2 condenses the refrigerant discharged from the 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.

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

[0098] The reservoir 14 has an outer cylinder 14a, a refrigerant suction pipe 14b, and a separation plate 14c. The outer cylinder 14a has an outer cylinder inlet 14d at an upper portion thereof through which the refrigerant from the evaporator 4 is introduced. The refrigerant suction pipe 14b has a suction pipe inlet 14e at an inner portion of the outer cylinder 14a. The separation plate 14c is disposed between the outer cylinder inlet 14d and the suction pipe inlet 14e.

[0099] A liquid storage portion 14f is formed at a bottom portion inside the outer cylinder 14a. The liquid refrigerant is stored in the liquid storage portion 14f. The liquid refrigerant can be stored up to a height H of the suction pipe inlet 14e. Thus, the height H of the suction 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 a plurality of operating frequencies. In the inverter driving, a low rotation region in which the rotation speed of the motor portion 20 is reduced or a high rotation region in which the rotation speed of the motor portion 20 is increased is generated in order to optimize the operation 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 performing a revolution motion along the inner wall surface of the cylinder 31.

[0106] The compression chamber 34 is divided by the vane 33 into an intake space 34a communicating with the suction passage 35 and a compression space 34b communicating with the discharge hole 37. The intake volume formed in the cylinder 31 is the volume of the intake 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 intake 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 movement of the piston 32 is discharged from the discharge hole 37 into the muffling chamber 54 after being compressed by the compression chamber 34.

[0108] The refrigerant gas 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 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 reservoir 14.

[0109] Figure 3 is a view showing the piston and the vane of the rotary compressor of 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 a circular arc angle a exceeds 180° is formed on the outer peripheral surface of the piston 32. The cylindrical groove 32a extends from one end surface to the other end surface of the piston 32.

[0111] The vane 33 has a vane side surface portion 33a that slides with the vane groove 36, a cylindrical portion 33b that is disposed in the cylindrical groove 32a, and a narrowed portion 33c that connects the vane side surface portion 33a and the cylindrical portion 33b. The cylindrical portion 33b is formed at 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 that extends from one end surface to the other end surface of the cylindrical portion 33b is formed on 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 that is divided into at least two portions by the notch portion 33d is formed on 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 that is greater than 90° and less than 180°, and the notch portion 33d is set to a circular arc angle γ that is less than 45°. In addition, 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 that is less than 45°, it is possible to increase the contact area of the cylindrical groove 32a and the cylindrical portion 33b, and it is possible to reliably prevent refrigerant leakage.

[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 arc surface 33el and the discharge side arc surface 33e2 can be formed symmetrically through the notch portion 33d. In the present embodiment, the notch portion 33d is formed with a flat surface, but the notch portion 33d can also be formed with a curved surface as long as it is cut inward from the arc-shaped outer peripheral surface of the cylindrical portion 33b, and can also be formed with one flat surface.

[0117] It is preferable to arrange the two arc surfaces 33e formed so as to be closest to the extended imaginary surface X on the side surface of the vane side surface portion 33a. In this way, since the point on the side surface of the vane side surface portion 33a that is closest to the extended imaginary surface X in the cylindrical portion 33b is located on the arc surface 33e, it is possible to reliably prevent refrigerant leakage.

[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, it is easy to form the cylindrical groove 32a, and since the surface formed by the cylindrical portion 33b and the cylindrical groove 32a is resistant to wear, the wear resistance is also high.

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

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

[0121] The vane side surface portion 33a, that is, the side surface of the vane 33 is surface treated, and the side surface of the vane 33 is set to a hardness of Hv1000 or more. Therefore, it is possible to have sufficient sliding resistance with respect to the vane groove 36.

[0122] Nitriding treatment or DLC treatment is suitable for the surface treatment of the vane side surface portion 33a. By performing nitriding treatment or DLC treatment, it is possible to perform hard coating treatment on the vane side surface portion 33a.

[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. Further, at least a portion of the cylindrical portion 33b refers to the circular-arc surface 33e. The same applies in 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 sliding resistance with respect to the blade groove 36 is obtained, and the machinability and toughness of the cylindrical portion 33b can be improved 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.

[0124] The Vickers hardness of at least a portion of the cylindrical portion 33b is preferably lower than the Vickers hardness of the blade side portion 33a by Hv 200 or more. That is, by performing the hard coating treatment on the blade side portion 33a, the Vickers hardness of the blade side portion 33a is made higher than the Vickers hardness of at least a portion of the cylindrical portion 33b by Hv 200 or more, and sufficient sliding resistance with respect to the blade groove 36 is obtained.

[0125] Further, 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 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 blade side portion 33a or the cylindrical portion 33b, the machinability and toughness of the narrowed portion 33c can be improved. Further, 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 the manufacturing process of the blade for the rotary compressor of the embodiment.

[0128] Figure 4 (a) indicates the base material of the blade 33, and the blade 33 uses an iron alloy in which iron (Fe) is the 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 blade 33 uses a steel material in which tungsten (W) and vanadium (V) are not added, low cost can be achieved. Further, the blade 33 can use stainless steel (for example, SUS440C).

[0129] Figure 4 (b) indicates that Figure 4(a) The base material of the vane 33 shown is in a state where a hard coating treatment has been performed.

[0130] As Figure 4 (c) The base material of the vane 33, which has been subjected to a 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.

[0131] As Figure 4 (c) In order to form the cylindrical portion 33b where the circular arc angle α exceeds 180°, it is necessary to perform finish machining in two or more stages, and the machining accuracy at the connecting surface M of the machined surfaces decreases.

[0132] However, by dividing the circular arc surface 33e of the cylindrical portion 33b into a plurality of portions by the notch portion 33d, and by setting each of the circular arc surfaces 33e to a circular arc angle β of less than 180°, it is possible to improve the machining accuracy of the circular arc surface 33e of the cylindrical portion 33b.

[0133] In particular, by forming the notch portion 33d at the leading end of the cylindrical portion 33b, i.e., at the connecting surface M, it is possible to perform machining by finish machining only the suction-side circular arc surface 33el and the discharge-side circular arc surface 33e2.

[0134] The working fluid and the refrigerant oil described in the present embodiment as a refrigerant are in a two-phase separated state under temperature conditions of 25°C. Thus, in particular, even in the 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, it is possible to ensure lubrication performance, and it is possible to maintain a good sliding state. Here, the low rotation region refers to a rotation speed region of 900 rpm or less, in particular, 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, it is possible to stably perform operation in the low rotation region, i.e., low capacity operation.

[0135] In addition, under temperature conditions of 0°C to 25°C, the proportion of the working fluid in the mixture in which the working fluid is maximally dissolved in the refrigerant oil is 1 wt% or more and less than 30 wt%. Thus, in particular, even in the 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, it is possible to ensure lubrication performance, and it is possible to maintain a good sliding state.

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

[0137] Further, 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 the case where the liquid compression operation cannot be avoided by using the refrigerant oil having low compatibility with the working fluid, the lubricating property can be ensured, and a good sliding state can be maintained, so the accumulator 14 can be made small.

[0138] Further, 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 of two pistons is suitable for low-speed operation, it is also preferable that each vane 33 act without leaving each piston 32.

[0139] Further, as the 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 high-efficiency rotary compressor can be realized.

[0141] In particular, by setting the working fluid to R32 and the refrigerant oil to alkyl benzene oil, the compatibility is low, the lubricating property can be ensured, and a good sliding state can be maintained. Further, the same applies to the working fluid containing at least R32.

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

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

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

[0145] In addition, the rotary compressor in which the vane 33 does not move away from the piston 32 can use R1234yf or HFO1123, a working fluid containing R1234yf, or a working fluid containing HFO1123, and from the viewpoint of lubrication performance, in R1234yf or the working fluid containing R1234yf, refrigerant oil is preferably an alkylbenzene oil, and in HFO1123 or the working fluid containing HFO1123, refrigerant oil is preferably an ester oil or an 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 is highly reliable.

[0147] Industrial availability

[0148] The device of the present application using a rotary compressor is useful as a refrigeration cycle device such 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.

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, wherein the vane has a vane side portion that slides with the vane groove, and a surface hardness of at least a portion of the cylindrical portion is lower than a surface hardness of the vane side portion.

2. The rotary compressor according to claim 1, characterized in that: a Vickers hardness of at least the portion of the cylindrical portion is lower than a Vickers hardness of the vane side portion by Hv 200 or more.

3. The rotary compressor according to claim 1 or 2, characterized in that: the vane side portion is subjected to a hard coating treatment.

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

5. The rotary compressor according to claim 1 or 2, characterized in that: the vane has a narrowed portion connecting the vane side portion and the cylindrical portion, and a surface hardness of the narrowed portion is lower than the surface hardness of the vane side portion.

6. 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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