Rotary compressor and apparatus

Abstract

The utility model provides a rotary compressor (1) and equipment using the rotary compressor (1), a compression mechanism part (30) is provided with a cylinder (31), a piston (32) configured in the cylinder (31) and blades (33) dividing the interior of the cylinder (31), a shaft (40) is provided with an eccentric part (42), a blade groove (36) configured with the blades (33) is formed on the cylinder (31), the eccentric part (42) is configured in the cylinder (31), the piston (32) is embedded with the eccentric part (42), and the blade groove (36) is embedded with the eccentric part (42). The vane (33) operates without leaving the piston (32), and by bringing the refrigerator oil and the working fluid into a two-phase separated state under a temperature condition of 25 DEG C, lubrication performance can be ensured and a good sliding state can be maintained even if liquid compression operation cannot be avoided.

Description

TECHNICAL FIELD

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

[0002] Patent document 1 discloses a rotary compressor in which a vane does not leave a piston by forming a cylindrical groove on the piston and a cylindrical portion on the end of the vane.

[0003] Patent document 2 discloses a rocking-type rotary compressor that uses a non-miscible oil having a region in which the proportion of oil components does not miscible in the range of -40°C to 31°C.

[0004] PRIOR ART DOCUMENTS

[0005] PATENT DOCUMENT

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

[0007] Patent document 2: Japanese Patent Application Publication No. 2008-101523 SUMMARY

[0008] PROBLEMS TO BE SOLVED BY THE INVENTION

[0009] In the case where liquid refrigerant is sucked in and compressed, the closed container is filled with liquid refrigerant, and the refrigerant oil is made low-viscosity by dissolving a large amount of liquid refrigerant in the refrigerant oil.

[0010] In the rotary compressor described in patent document 1, the piston and the vane are not separated, so when liquid refrigerant is sucked into the compression chamber, liquid compression is performed. Liquid compression exerts a greater load on the compressor than gas compression.

[0011] Thus, the viscosity of the refrigerant oil is reduced and the load is increased due to liquid compression at the same time, so the sliding state of the compressor deteriorates.

[0012] In addition, if the non-miscible oil described in patent document 2 is discharged from the compressor, it is difficult to return to the compressor, and it is easy to cause a shortage of refrigerant oil in the compressor.

[0013] Therefore, the purpose of the present utility model is to provide a rotary compressor and a device using the rotary compressor, which can ensure lubrication performance and maintain a good sliding state even in the case where liquid compression operation cannot be avoided.

[0014] METHOD FOR SOLVING THE PROBLEMS

[0015] The utility model discloses a first aspect provides a kind of rotary compressor 1, motor portion 20 and compression mechanism portion 30 are in closed container 10, the oil storage portion 11 of storing refrigeration oil is formed in the bottom in the closed container 10, suction pipe 12 in the closed container 10 has the working fluid being guided to the compression mechanism portion 30, and discharge pipe 13 is guided to the closed container 10 outside by the working fluid compressed by the compression mechanism portion 30, the working fluid compressed by the compression mechanism portion 30 is guided to the closed container 10 outside from the discharge pipe 13 after being discharged to the 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 blade 33 separating the cylinder 31, the shaft 40 has eccentric portion 42, the blade slot 36 of the blade 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 blade 33 does not act from the piston 32, the rotary compressor 1 is characterized in that, under the temperature condition of 25 DEG C, the refrigeration oil and the working fluid are two-phase separation state.

[0016] The rotary compressor 1 of the second aspect of the utility model is characterized in that, on the basis of the first aspect, a cylindrical groove 32a with an arc angle α exceeding 180° is formed on the piston 32, and a cylindrical portion 33b is formed at the end of the blade 33 and arranged in the cylindrical groove 32a.

[0017] The rotary compressor 1 of the third aspect of the utility model is characterized in that, on the basis of the first aspect, under the temperature condition of 0 DEG C to 25 DEG C, the proportion of the working fluid in the mixture of the working fluid maximally dissolved in the refrigeration oil is less than 30 wt%.

[0018] The rotary compressor 1 of the fourth aspect of the utility model is characterized in that, on the basis of the first aspect, the accumulator 14 is not provided upstream of the suction pipe 12.

[0019] The rotary compressor 1 of the fifth aspect of the utility model is characterized in that, on the basis of the first aspect, the accumulator 14 is provided upstream of the suction pipe 12, and the volume of the liquid storage portion 14f of the accumulator 14 is set to be less than twice the suction volume formed in the cylinder 31.

[0020] The rotary compressor 1 of the sixth aspect of the utility model is characterized in that, on the basis of any one of the first to fifth aspects, the working fluid is set to be R32, and the refrigeration oil is set to be alkyl benzene oil.

[0021] The rotary compressor 1 of the seventh aspect of the present application is characterized in that, based on any one of the first to fifth aspects, the working fluid is set to carbon dioxide and the refrigerant oil is set to polyalkylene glycol oil.

[0022] The rotary compressor 1 of the eighth aspect of the present application is characterized in that, based on any one of the first to fifth aspects, the working fluid is set to R290 and the refrigerant oil is set to polyalkylene glycol oil.

[0023] The ninth aspect of the present application provides an apparatus using the rotary compressor 1 of any one of the first to fifth aspects, and is characterized in that the rotary compressor 1, the condenser 2, the pressure reducing device 3, and the evaporator 4 are connected in a ring shape by piping.

[0024] Effect of the Invention

[0025] According to the present application, in particular, even in a case where liquid compression operation cannot be avoided by using refrigerant oil having low compatibility with the working fluid in the low rotation region, lubrication performance can be ensured and a good sliding state can be maintained. BRIEF DESCRIPTION OF DRAWINGS

[0026] Figure 1 is a cross-sectional view of a rotary compressor according to an embodiment of the present application.

[0027] Figure 2 is Figure 1 the A-A line view shown.

[0028] Figure 3 is a view showing a piston and a vane for a rotary compressor according to the same embodiment.

[0029] Figure 4 is a view showing a manufacturing process of a vane for a rotary compressor according to the same embodiment.

[0030] REFERENCE NUMERALS

[0031] 1 Rotary compressor

[0032] 2 Condenser

[0033] 3 Pressure reducing device

[0034] 4 Evaporator

[0035] 10 Hermetic container

[0036] 11 Oil storage portion

[0037] 12 Suction pipe

[0038] 13 Discharge pipe

[0039] 14 accumulator

[0040] 14a outer cylinder

[0041] 14b refrigerant suction pipe

[0042] 14c separation plate

[0043] 14d outer cylinder inlet

[0044] 14e suction pipe inlet

[0045] 14f liquid storage portion

[0046] 20 motor portion

[0047] 21 stator

[0048] 22 rotor

[0049] 30 compression mechanism portion

[0050] 31 cylinder

[0051] 32 piston

[0052] 32a cylindrical groove

[0053] 33 vane

[0054] 33a vane side portion

[0055] 33b cylindrical portion

[0056] 33c narrowed portion

[0057] 33d notch portion

[0058] 33e circular arc surface

[0059] 33e1 suction side circular arc surface

[0060] 33e2 discharge side circular arc surface

[0061] 34 compression chamber

[0062] 34a suction space

[0063] 34b compression space

[0064] 35 suction passage

[0065] 36 vane groove

[0066] 37 discharge hole

[0067] 40 shaft

[0068] 41 main shaft portion

[0069] 42 eccentric portion

[0070] 43 sub-shaft portion

[0071] 46 oil supply passage

[0072] 47 communication passage

[0073] 51 upper bearing

[0074] 52 lower bearing

[0075] 53 upper cover

[0076] 54 sound deadening chamber

[0077] H height

[0078] M connecting surface

[0079] X extended imaginary surface

[0080] Y jig

[0081] Z cutting tool

[0082] α, β, γ circular arc angle DETAILED DESCRIPTION

[0083] In the rotary compressor of the first embodiment of the present application, the refrigerant oil and the working fluid are in a two-phase separated state under a temperature condition of 25°C. According to the present embodiment, in particular, 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.

[0084] The second embodiment of the present application forms a cylindrical groove having a circular arc angle exceeding 180° on a piston, and forms a cylindrical portion disposed in the cylindrical groove at an end portion of a vane, on the basis of the rotary compressor of the first embodiment. According to the present embodiment, since the cylindrical portion and the cylindrical groove form a surface that receives, wear resistance is high.

[0085] The third embodiment of the present application forms a cylindrical groove having a circular arc angle exceeding 180° on a piston, and forms a cylindrical portion disposed in the cylindrical groove at an end portion of a vane, on the basis of the rotary compressor of the first embodiment. According to the present embodiment, since the cylindrical portion and the cylindrical groove form a surface that receives, wear resistance is high.

[0086] The fourth embodiment of the present application is a rotary compressor which does not have an accumulator upstream of the suction pipe, based on the rotary compressor of the first embodiment. According to the fourth embodiment, even if liquid compression operation cannot be avoided, lubrication performance can be ensured, and a good sliding state can be maintained, so the accumulator can be made small.

[0087] The fifth embodiment of the present application is a rotary compressor which has an accumulator upstream of the suction pipe, based on the rotary compressor of the first embodiment. The volume of the liquid storage portion of the accumulator is set to be 2 times or less the suction volume formed in the cylinder. According to the fifth embodiment, even if liquid compression operation cannot be avoided, lubrication performance can be ensured, and a good sliding state can be maintained, so the accumulator can be made small.

[0088] The sixth embodiment of the present application is a rotary compressor in which the working fluid is R32 and the refrigerant oil is alkyl benzene oil, based on the rotary compressor of the first to fifth embodiments. According to the sixth embodiment, the solubility is low, lubrication performance can be ensured, and a good sliding state can be maintained.

[0089] The seventh embodiment of the present application is a rotary compressor in which the working fluid is carbon dioxide and the refrigerant oil is polyalkylene glycol oil, based on the rotary compressor of the first to fifth embodiments. According to the seventh embodiment, the solubility is low, lubrication performance can be ensured, and a good sliding state can be maintained.

[0090] The eighth embodiment of the present application is a rotary compressor in which the working fluid is R290 and the refrigerant oil is polyalkylene glycol oil, based on the rotary compressor of the first to fifth embodiments. According to the eighth embodiment, the solubility is low, lubrication performance can be ensured, and a good sliding state can be maintained.

[0091] The ninth embodiment of the present application provides an apparatus which uses the rotary compressor of the first to fifth embodiments, 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 ninth embodiment, an apparatus with high reliability can be provided.

[0092]

Embodiment

[0093] Figure 1 is a cross-sectional view of a rotary compressor according to an embodiment of the present application, Figure 2 is Figure 1 the A-A line view shown in FIG. 1.

[0094] 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 connected by a shaft 40.

[0095] The motor portion 20 is composed of a stator 21 fixed to the inner surface of the sealed container 10 and a rotor 22 rotating within the stator 21.

[0096] The compression mechanism portion 30 has a cylinder 31, a piston 32 disposed within the cylinder 31, and a vane 33 partitioning the inside of the cylinder 31 (see Figure 2 ).

[0097] 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.

[0098] 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.

[0099] The upper bearing 51 is fixed to the sealed container 10. The piston 32 is rotatably fitted to the eccentric portion 42 of the shaft 40 which penetrates the inside of the cylinder 31.

[0100] An upper cover 53 is provided on the 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 sealed container 10.

[0101] An oil reservoir portion 11 is formed in the 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 the inside of the shaft 40 in the axial direction. A communication passage 47 for supplying refrigerant oil to the sliding surface of the compression mechanism portion 30 is formed in the inside of the eccentric portion 42.

[0102] The refrigerant oil in the oil reservoir portion 11 is introduced into the inner shaft oil supply passage 46 from the 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 surface of the compression mechanism portion 30 from the communication passage 47.

[0103] An intake pipe 12 is connected to the side surface of the sealed container 10, and a discharge pipe 13 is connected to the 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.

[0104] A surge tank 14 is provided on the upstream side of the intake pipe 12.

[0105] 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.

[0106] The refrigerant evaporated by the evaporator 4 is returned to the accumulator 14.

[0107] The accumulator 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 through which the refrigerant from the evaporator 4 is introduced at an upper portion thereof. 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.

[0108] A liquid storage portion 14f is formed at an inner bottom portion of 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.

[0109] 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.

[0110] 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.

[0111] The suction pipe 12 is connected to a suction passage 35 of the compression mechanism portion 30.

[0112] The suction passage 35 is connected to the compression chamber 34.

[0113] The piston 32 performs a revolution motion by the rotation of the shaft 40.

[0114] 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.

[0115] The compression chamber 34 is divided by the vane 33 into a suction space 34a communicating with the suction passage 35 and a compression space 34b communicating 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.

[0116] The gaseous refrigerant passing through the suction passage 35 from the suction pipe 12 and being 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.

[0117] The refrigerant gas discharged into the sound deadening 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 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.

[0118] Figure 3 Fig. 2 is a view showing a piston and a vane of 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.

[0119] A cylindrical groove 32a having a circular arc angle α of more than 180° is formed in an 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.

[0120] The vane 33 has a vane side surface portion 33a which slides with the vane groove 36, a cylindrical portion 33b which is disposed 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 an end portion of the vane 33.

[0121] By engaging the cylindrical portion 33b with the cylindrical groove 32a, the vane 33 operates without departing from the piston 32.

[0122] A notch portion 33d which extends from one end surface to the other end surface of the cylindrical portion 33b is formed in the cylindrical portion 33b. The cylindrical portion 33b divides a 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 an outer peripheral surface of the cylindrical portion 33b.

[0123] 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°. In addition, the circular arc angle β is preferably 110° or more and 150° or less.

[0124] By setting the notch portion 33d to the circular arc angle γ which 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.

[0125] 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.

[0126] 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.

[0127] 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.

[0128] 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.

[0129] 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.

[0130] 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.

[0131] 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.

[0132] 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 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 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.

[0133] 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.

[0134] 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.

[0135] 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.

[0136] Figure 4 is a view showing a manufacturing process of a blade for a rotary compressor according to the embodiment.

[0137] Figure 4 (a) shows a base material of the blade 33, and the blade 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 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).

[0138] Figure 4 (b) shows that the blade 33 is subjected to a hard coating treatment. Figure 4(a) The base material of the vane 33 shown is in a state where a hard coating treatment has been performed.

[0139] 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.

[0140] 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.

[0141] 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.

[0142] 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.

[0143] The working fluid and the refrigerant oil, which are described in the present embodiment, are in a two-phase separated state under temperature conditions of 25°C. Thus, in particular, even in a case where liquid compression operation cannot be avoided by using refrigerant oil having low phase solubility with respect to 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.

[0144] 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 a case where liquid compression operation cannot be avoided by using refrigerant oil having low phase solubility with respect to 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.

[0145] 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.

[0146] 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.

[0147] 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.

[0148] 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.

[0149] 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.

[0150] 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.

[0151] 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.

[0152] 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.

[0153] 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.

[0154] 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.

[0155] 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.

[0156] Industrial availability

[0157] The device using the rotary compressor of the present application 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; an oil storage portion for storing refrigerant oil formed in a bottom portion of the closed container; a suction pipe for guiding a working fluid to the compression mechanism portion and a discharge pipe for guiding the working fluid compressed by the compression mechanism portion to the outside of the closed container, provided in the closed container; the working fluid compressed by the compression mechanism portion being guided to the outside of the closed container from the discharge pipe after being discharged into the 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 for 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; the vane being operated without leaving the piston; and the refrigerant oil and the working fluid being in a two-phase separated state at a temperature of 25°C.

2. The rotary compressor according to claim 1, characterized by comprising: a cylindrical groove having a circular arc angle of more than 180° being formed in the piston; and a cylindrical portion formed in an end portion of the vane for being disposed in the cylindrical groove.

3. The rotary compressor according to claim 1, characterized in that, in a mixture of the working fluid and the refrigerant oil, the proportion of the working fluid is less than 30 wt% at a temperature of 0°C to 25°C.

4. The rotary compressor according to claim 1, characterized by comprising: no accumulator upstream of the suction pipe.

5. The rotary compressor according to claim 1, characterized by comprising: an accumulator upstream of the suction pipe; and a volume of a liquid storage portion of the accumulator being less than twice a suction volume formed in the cylinder.

6. The rotary compressor according to any one of claims 1 to 5, characterized in that the working fluid is R32 and the refrigerant oil is an alkylbenzene oil.

7. The rotary compressor according to any one of claims 1 to 5, characterized in that the working fluid is carbon dioxide and the refrigerant oil is a polyalkylene glycol oil.

8. The rotary compressor according to any one of claims 1 to 5, characterized in that the working fluid is R290 and the refrigerant oil is a polyalkylene glycol oil.

9. An apparatus characterized by comprising: the rotary compressor according to any one of claims 1 to 5; and a condenser, a pressure reducing device, and an evaporator connected in a ring shape by piping. ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​

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