Rotary compressor, equipment and indoor air conditioner

Abstract

A rotary compressor (1) includes a compression mechanism portion (30) having a cylinder (31), a piston (32), and a vane (33), a shaft (40) having an eccentric portion (42) disposed in the cylinder, a groove being formed in the cylinder, the piston being fitted to the eccentric portion, and a cylindrical groove (32a) having an arc angle (alpha) exceeding 180 degrees being formed in the piston. A cylindrical portion (33b) disposed in the cylindrical groove is formed at an end portion of the blade, the blade (33) operates without leaving the piston, a cutout portion (33d) is formed in the cylindrical portion from one end surface to the other end surface of the cylindrical portion, an arc surface (33e) of the cylindrical portion is divided into a plurality of portions by the cutout portion, each arc surface is set to have an arc angle [beta] of less than 180 DEG, and the arc angle [beta] is greater than 180 DEG. The cutout section (33d) has an arc angle [gamma] of less than 45 DEG, and the machining accuracy of the arc surface of the cylindrical section can be improved.

Description

[0001] This case is a divisional application of the patent application filed on January 24, 2025, with application number 202510116972.5, entitled "Rotary Compressor and Device". Technical Field

[0002] The present invention relates to a rotary compressor in which the blades move without leaving the piston and to an apparatus using the rotary compressor. Background Technology

[0003] Patent document 1 discloses a rotary compressor that allows the blades to move without leaving the piston by forming a cylindrical groove on the piston and forming a cylindrical portion disposed in the cylindrical groove at the end of the blade.

[0004] Patent document 2 discloses a compressor in which the cylindrical side of the blade is D-cut to improve the machinability of the blade side.

[0005] Existing technical documents

[0006] Patent documents

[0007] Patent Document 1: Japanese Patent Application Publication No. 3-185291

[0008] Patent Document 2: Japanese Patent Application Publication No. 2012-237317 Summary of the Invention

[0009] The problem that the invention aims to solve

[0010] The blade tip is fitted into a groove in the piston. The cylindrical part of the blade and the piston groove slide in the circumferential direction, so the piston groove and the cylindrical part of the blade need to be precision machined.

[0011] If the cylindrical portion of the blade has an arc angle exceeding 180°, it requires finishing the cylindrical portion of the blade in two or more stages. The seams on the machined surfaces become a cause of reduced precision in the cylindrical portion.

[0012] Therefore, the object of the present invention is to provide a rotary compressor capable of improving the machining accuracy of the arc surface of a cylindrical part and an apparatus using the rotary compressor.

[0013] Methods for solving problems

[0014] The first aspect of the present invention provides a rotary compressor 1, which has an electric motor section 20 and a compression mechanism section 30 within a sealed container 10. The electric motor section 20 and the compression mechanism section 30 are connected by a shaft 40. The compression mechanism section 30 has a cylinder 31, a piston 32 disposed within the cylinder 31, and blades 33 that divide the cylinder 31. The shaft 40 has an eccentric portion 42, and grooves for arranging the blades 33 are formed on the cylinder 31. The eccentric portion 42 is disposed within the cylinder 31, and the piston 32 is fitted with the eccentric portion 42. An arc angle α is formed on the piston 32. A cylindrical groove 32a exceeding 180° is formed at the end of the blade, and a cylindrical portion 33b is formed in the cylindrical groove 32a. The blade 33 moves without leaving the piston 32. The rotary compressor 1 is characterized in that a notch 33d is formed on the cylindrical portion 33b from one end face to the other end face. The notch 33d divides the arc surface 33e of the cylindrical portion 33b into a plurality of segments. Each arc surface 33e is set to an arc angle β of less than 180°, and the notch 33d is set to an arc angle γ of less than 45°.

[0015] The rotary compressor 1 of the second aspect of the present invention is based on the first aspect, characterized in that the notch 33d is formed at the front end of the blade 33.

[0016] The rotary compressor 1 of the third aspect of the present invention is based on the first or second aspect, characterized in that at least two arcuate surfaces 33e are formed on the outer peripheral surface of the cylindrical portion 33b, and the two arcuate surfaces 33e are positioned as close as possible to the extended imaginary surface X of the side surface of the blade 33.

[0017] A fourth aspect of the present invention provides an apparatus that uses the rotary compressor 1 described in the first or second aspect, characterized in that the rotary compressor 1, condenser 2, pressure reducing device 3 and evaporator 4 are connected in a ring shape by piping.

[0018] Invention Effects

[0019] According to the present invention, by dividing the arc surface of the cylindrical part into multiple parts using a notch from one end face to the other end face and setting each arc surface to an arc angle of less than 180°, the machining accuracy of the arc surface of the cylindrical part can be improved. By setting the notch to an arc angle of less than 45°, the contact area between the cylindrical groove and the cylindrical part can be increased, and reliably preventing refrigerant leakage can be prevented. Attached Figure Description

[0020] Figure 1 This is a cross-sectional view of a rotary compressor according to an embodiment of the present invention.

[0021] Figure 2 yes Figure 1 The view shown is along the AA line.

[0022] Figure 3 This is a diagram showing the piston and blades of a rotary compressor according to the same embodiment.

[0023] Figure 4 This is a diagram illustrating the manufacturing process of the blades for a rotary compressor according to the same embodiment.

[0024] Explanation of reference numerals in the attached figures

[0025] 1. Rotary compressor

[0026] 2. Condenser

[0027] 3. Pressure reducing device

[0028] 4. Evaporator

[0029] 10. Sealed containers

[0030] 11 Oil Storage Section

[0031] 12. Inhalation tube

[0032] 13 Discharge pipe

[0033] 14 reservoir

[0034] 14a outer cylinder

[0035] 14b Refrigerant suction pipe

[0036] 14c Separation Plate

[0037] 14d outer cylinder entrance

[0038] 14e Inhalation tube inlet

[0039] 14f Liquid Storage Section

[0040] 20 Electric Motor Section

[0041] 21 Stator

[0042] 22 Rotors

[0043] 30 Compression Mechanism Department

[0044] 31 cylinders

[0045] 32 Pistons

[0046] 32a Cylindrical groove

[0047] 33 blades

[0048] 33a Blade side surface

[0049] 33b Cylindrical portion

[0050] 33c narrowing section

[0051] 33d notch

[0052] 33e Arc surface

[0053] 33e1 Suction side arc surface

[0054] 33e2 Exhaust side arc surface

[0055] 34 Compression Chamber

[0056] 34a Inhalation space

[0057] 34b Compressed space

[0058] 35. Inhalation route

[0059] 36 blade grooves

[0060] 37 Discharge port

[0061] 40 axis

[0062] 41 Spindle section

[0063] 42 Eccentric part

[0064] 43 Sub-shaft section

[0065] 46. ​​Internal oil supply passage

[0066] 47 Connecting Paths

[0067] 51 Upper Bearing

[0068] 52 Lower Bearing

[0069] 53 Upper Cover

[0070] 54 Silencer

[0071] H height

[0072] M connected surfaces

[0073] X Extended Imaginary Surface

[0074] Y-clamp

[0075] Z-cutting tools

[0076] α, β, γ are arc angles. Detailed Implementation

[0077] The rotary compressor of the first embodiment of the present invention has a notch formed on the cylindrical portion, extending from one end face of the cylindrical portion to the other end face. The notch divides the arc surface of the cylindrical portion into multiple segments, each arc surface having an arc angle of less than 180°, and the notch having an arc angle of less than 45°. To form a cylindrical portion with an arc angle exceeding 180°, finishing is required in two or more stages, reducing the machining accuracy at the connecting surfaces. However, according to this embodiment, by dividing the arc surface of the cylindrical portion into multiple segments using the notch extending from one end face to the other end face and setting each arc surface to an arc angle of less than 180°, the machining accuracy of the arc surface of the cylindrical portion can be improved. By setting the notch to an arc angle of less than 45°, the contact area between the cylindrical groove and the cylindrical portion can be increased, reliably preventing refrigerant leakage.

[0078] The second embodiment of the present invention, based on the rotary compressor of the first embodiment, forms a notch at the leading edge of the blade. According to this embodiment, it is not easy to apply a load to the leading edge of the blade, and the suction-side arcuate surface and the discharge-side arcuate surface can be symmetrically formed by the notch.

[0079] The third embodiment of the present invention, based on the rotary compressor of the first or second embodiment, forms at least two arcuate surfaces on the outer peripheral surface of the cylindrical portion, separated by a notch, and positions the two formed arcuate surfaces as close as possible to the extended imaginary surface X of the side surface of the blade. According to this embodiment, refrigerant leakage can be reliably prevented.

[0080] The device according to the fourth embodiment of the present invention uses a rotary compressor of the first or second embodiment, wherein the rotary compressor, condenser, pressure reducing device, and evaporator are connected in a ring shape by piping. According to this embodiment, a highly reliable device can be provided.

[0081]

Example

[0082] Figure 1 This is a cross-sectional view showing a rotary compressor according to an embodiment of the present invention. Figure 2 yes Figure 1 The view shown is along the AA line.

[0083] The rotary compressor 1 of this embodiment includes an electric motor section 20 and a compression mechanism section 30 within a sealed container 10. The electric motor section 20 and the compression mechanism section 30 are connected by a shaft 40.

[0084] The motor unit 20 consists of a stator 21 fixed to the inner surface of the sealed container 10 and a rotor 22 rotating within the stator 21.

[0085] The compression mechanism 30 includes a cylinder 31, a piston 32 disposed within the cylinder 31, and vanes 33 that divide the cylinder 31 (see reference). Figure 2).

[0086] An upper bearing 51 is disposed on one side of cylinder 31, and a lower bearing 52 is disposed on the other side of cylinder 31.

[0087] The shaft 40 is composed of a main shaft portion 41 for mounting the rotor 22 and supported by an upper bearing 51, an eccentric portion 42 for mounting the piston 32, and a secondary shaft portion 43 supported by a lower bearing 52.

[0088] The upper bearing 51 is fixed to the sealed container 10. The piston 32 is freely engaged with the eccentric part 42 of the shaft 40 inside the through cylinder 31.

[0089] An upper cover 53 is provided on the upper part of the upper bearing 51. A silencing chamber 54 is formed between the upper bearing 51 and the upper cover 53. High-pressure refrigerant gas compressed by the compression mechanism 30 is discharged into the silencing chamber 54. The high-pressure refrigerant gas discharged into the silencing chamber 54 is then discharged into the sealed container 10.

[0090] An oil reservoir 11 is formed at the bottom of the sealed container 10. The oil reservoir 11 stores refrigeration oil. An internal oil supply passage 46 is formed axially inside the shaft 40. A connecting passage 47 for supplying refrigeration oil to the sliding surface of the compression mechanism 30 is formed inside the eccentric portion 42.

[0091] The refrigeration oil in the oil reservoir 11 is introduced from the lower end of the shaft 40 into the internal oil supply passage 46. A portion of the refrigeration oil introduced into the internal oil supply passage 46 is supplied to the sliding surface of the compression mechanism section 30 through the connecting passage 47.

[0092] A suction pipe 12 is connected to the side of the sealed container 10, and a discharge pipe 13 is connected to the upper surface of the sealed container 10. The suction pipe 12 guides the refrigerant to the compression mechanism 30. The discharge pipe 13 guides the refrigerant compressed by the compression mechanism 30 and discharged into the sealed container 10 to the outside of the sealed container 10.

[0093] An accumulator 14 is provided on the upstream side of the suction pipe 12.

[0094] In the rotary compressor 1 of this embodiment, the condenser 2, the pressure reducing device 3, and the evaporator 4 are connected in a ring shape via 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 whose pressure has been reduced by the pressure reducing device 3.

[0095] The refrigerant evaporated by evaporator 4 returns to accumulator 14.

[0096] The accumulator 14 has an outer cylinder 14a, a refrigerant suction pipe 14b, and a separator plate 14c. An outer cylinder inlet 14d for introducing refrigerant from the evaporator 4 is located at the upper part of the outer cylinder 14a. The refrigerant suction pipe 14b has a suction pipe inlet 14e inside the outer cylinder 14a. The separator plate 14c is disposed between the outer cylinder inlet 14d and the suction pipe inlet 14e.

[0097] A liquid storage section 14f is formed at the inner bottom of the outer cylinder 14a. Liquid refrigerant is stored in the liquid storage section 14f. The liquid refrigerant can be stored up to a height H of the suction pipe inlet 14e. Therefore, the volume of the liquid storage section 14f is up to the height H of the suction pipe inlet 14e.

[0098] Furthermore, 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 it can also be driven by inverter at multiple operating frequencies. In inverter drive, in order to optimize the operation control of the rotary compressor 1, a low rotational region with reduced speed of motor 20 or a high rotational region with increased speed of motor 20 is generated.

[0099] Figure 2 The compression chamber 34 shown is formed between the upper bearing 51 and the lower bearing 52 and between the inner circumferential surface of the cylinder 31 and the outer circumferential surface of the piston 32.

[0100] The suction pipe 12 is connected to the suction passage 35 of the compression mechanism 30.

[0101] The inhalation passage 35 is connected to the compression chamber 34.

[0102] The piston 32 revolves due to the rotation of shaft 40.

[0103] The blade 33 reciprocates in the blade groove 36 via the piston 32, which revolves along the inner wall of the cylinder 31.

[0104] The compression chamber 34 is divided by the blades 33 into an intake space 34a that communicates with the intake passage 35 and a compression space 34b that communicates with the discharge port 37. The intake volume formed in the cylinder 31 is the volume of the intake space 34a when the intake passage 35 is blocked by the piston 32, and the volume when the intake space 34a becomes the maximum space.

[0105] The gaseous refrigerant, drawn from the intake pipe 12 through the intake passage 35 and into the compression chamber 34 by the revolution of the piston 32, is compressed by the compression chamber 34 and then discharged from the discharge port 37 into the silencer chamber 54.

[0106] The refrigerant gas discharged into the silencing chamber 54 is discharged into the sealed container 10 and then discharged out of the sealed container 10 through the discharge pipe 13. The high-pressure refrigerant gas discharged out of the sealed container 10 becomes low-pressure refrigerant gas through the condenser 2, the pressure reducing device 3 and the evaporator 4, and then returns to the compression mechanism 30 through the accumulator 14.

[0107] Figure 3 This is a diagram showing the piston and blades of a rotary compressor according to the same embodiment. Figure 3 (a) is a three-dimensional view with the piston and blades separated. Figure 3 (b) is a top view with the piston and blades separated. Figure 3 (c) is a three-dimensional view of the leaf from different directions.

[0108] A cylindrical groove 32a with an arc angle α exceeding 180° is formed on the outer peripheral surface of the piston 32. The cylindrical groove 32a extends from one end face of the piston 32 to the other end face.

[0109] The blade 33 has a blade side surface portion 33a that slides with the blade groove 36, a cylindrical portion 33b disposed in the cylindrical groove 32a, and a narrowing portion 33c connecting the blade side surface portion 33a and the cylindrical portion 33b. The cylindrical portion 33b is formed at the end of the blade 33.

[0110] By engaging the cylindrical portion 33b with the cylindrical groove 32a, the blade 33 moves without leaving the piston 32.

[0111] A notch 33d is formed on the cylindrical portion 33b, extending from one end face of the cylindrical portion 33b to the other end face. The cylindrical portion 33b is divided into multiple arc surfaces 33e by the notch 33d. Thus, at least two arc surfaces 33e are formed on the outer peripheral surface of the cylindrical portion 33b by the notch 33d.

[0112] Each arc surface 33e is set with an arc angle β greater than 90° and less than 180°, and the notch 33d is set with an arc angle γ less than 45°. In addition, the arc angle β is preferably 110° or more and 150° or less.

[0113] By setting the notch 33d to an arc angle γ of less than 45°, the contact area between the cylindrical groove 32a and the cylindrical part 33b can be increased, thus reliably preventing refrigerant leakage.

[0114] In this embodiment, the notch 33d is formed at the leading edge of the blade 33. That is, the notch 33d is formed at the leading edge of the cylindrical portion 33b. This makes it easier to apply load to the leading edge of the blade. By forming the notch 33d at the leading edge of the blade, the intake-side arcuate surface 33e1 and the discharge-side arcuate surface 33e2 can be symmetrically formed through the notch 33d. Furthermore, in this embodiment, the notch 33d is formed with a flat surface. However, the notch 33d can also be formed with a curved surface, or even with a flat surface, as long as it is cut in such a way that it is closer to the inner side of the arcuate outer peripheral surface of the cylindrical portion 33b.

[0115] Preferably, the two formed arc surfaces 33e are positioned as close as possible to the extended imaginary surface X of the side surface of the blade side surface portion 33a. This ensures that refrigerant leakage is reliably prevented because the point in the cylindrical portion 33b closest to the extended imaginary surface X of the side surface of the blade side surface portion 33a is located on the arc surface 33e.

[0116] The Vickers hardness of the piston 32 surface is set to below Hv400. Since the piston 32 itself uses a low-hardness component, it is easy to form a cylindrical groove 32a. Due to the surface contact between the cylindrical portion 33b and the cylindrical groove 32a, the wear resistance is also high.

[0117] The Vickers hardness of the piston 32 surface is preferably set in the range of Hv80 to Hv400, and more preferably in the range of Hv180 to Hv250.

[0118] The piston 32 is preferably made of gray cast iron, which facilitates the formation of cylindrical grooves 32a. Furthermore, the piston 32 can be formed from sintered material. When sintered material is used for the piston 32, the Vickers hardness is preferably set to Hv400 or lower.

[0119] The side surface of the blade 33a, i.e., the side surface of the blade 33, is surface-treated to achieve a Vickers hardness exceeding Hv1000. Therefore, it exhibits sufficient resistance to slippage relative to the blade groove 36.

[0120] Nitriding or DLC treatment is suitable for the surface treatment of the blade side surface 33a. By performing nitriding or DLC treatment, a hard coating treatment can be applied to the blade side surface 33a.

[0121] At least a portion of the cylindrical portion 33b has a surface hardness lower than that of the blade side surface portion 33a. Furthermore, at least a portion of the cylindrical portion 33b refers to the arcuate surface 33e. The same applies in the following description. Thus, by making the surface hardness of at least a portion of the cylindrical portion 33b lower than that of the blade side surface portion 33a, it exhibits better resistance to sliding relative to the blade groove 36. Furthermore, by making the surface hardness of at least a portion of the cylindrical portion 33b lower than that of the blade side surface portion 33a, the machinability and toughness of the cylindrical portion 33b can be improved.

[0122] The Vickers hardness of at least a portion of the cylindrical portion 33b is preferably Hv200 or more lower than that of the blade side portion 33a. That is, by applying a hard coating to the blade side portion 33a, the Vickers hardness of the blade side portion 33a is made to be Hv200 or more higher than that of at least a portion of the cylindrical portion 33b, thus providing sufficient resistance to slippage relative to the blade groove 36.

[0123] Furthermore, the surface hardness of the narrowing portion 33c is lower than that of the blade side surface portion 33a. In this way, by making the surface hardness of the narrowing portion 33c lower than that of the blade side surface portion 33a, the machinability and toughness of the narrowing portion 33c can be improved, and by making the surface hardness of the blade side surface portion 33a higher than that of the narrowing portion 33c, it can have anti-slip properties relative to the blade groove 36.

[0124] Furthermore, the surface hardness of the narrowed portion 33c is preferably lower than that of the cylindrical portion 33b. By making the surface hardness of the narrowed portion 33c lower than that of the blade side surface portion 33a or the cylindrical portion 33b, the machinability and toughness of the narrowed portion 33c can be improved. Additionally, the surface hardness of the arcuate surface 33e is preferably lower than that of the notch portion 33d. By making the surface hardness of the arcuate surface 33e lower than that of the notch portion 33d, the machinability and toughness of the arcuate surface 33e can be improved.

[0125] Figure 4 This is a diagram illustrating the manufacturing process of the blades for a rotary compressor according to the same embodiment.

[0126] Figure 4 (a) indicates the base material of blade 33. Blade 33 is made of an iron alloy with iron (Fe) as the main component and containing chromium (Cr), or steel with added metallic materials such as chromium (Cr), tungsten (W), vanadium (V), and molybdenum (Mo) to high-carbon steel. Furthermore, since blade 33 uses steel without added tungsten (W) and vanadium (V), low cost can be achieved. Additionally, blade 33 can be made of stainless steel (e.g., SUS440C).

[0127] Figure 4 (b) indicates that... Figure 4(a) shows the state in which the substrate of blade 33 has undergone hard coating treatment.

[0128] like Figure 4 As shown in (c), the substrate of the blade 33, which has undergone hard coating treatment, is fixed on the fixture Y, and the cylindrical part 33b and the narrowed part 33c are processed by the cutting tool Z.

[0129] like Figure 4 As shown in (c), in order to form a cylindrical part 33b with an arc angle α exceeding 180°, it is necessary to perform finishing in more than two stages, which reduces the machining accuracy at the connecting surface M of the machined surface.

[0130] However, by dividing the cylindrical part 33b into multiple arc surfaces 33e through the notch 33d, and by setting each arc surface 33e to an arc angle β of less than 180°, the machining accuracy of the arc surfaces 33e of the cylindrical part 33b can be improved.

[0131] In particular, by forming a notch 33d at the front end of the connecting surface M, i.e. the cylindrical portion 33b, the machining can be performed by only two finishing processes: finishing the intake side arc surface 33e1 and finishing the discharge side arc surface 33e2.

[0132] In this embodiment, the working fluid and refrigeration oil, described as the refrigerant, are in a two-phase separated state at a temperature of 25°C. This ensures lubrication performance and maintains a good sliding condition, even when liquid compression operation cannot be avoided by using refrigeration oil with low miscibility with the working fluid in the low-rotation range of the rotary compressor 1. Here, the low-rotation range refers to a rotational speed range of 900 rpm or less, particularly 600 rpm or less, and further, 360 rpm or less. Liquid compression is easily generated in the low-rotation range; by ensuring lubrication performance in this region, stable operation within the low-rotation range, i.e., low-capacity operation, is possible.

[0133] Furthermore, under temperature conditions of 0°C to 25°C, the proportion of the working fluid in the mixture of the refrigeration oil containing the working fluid to the maximum extent is 1 wt% or more and less than 30 wt%. In this way, in particular, even when liquid compression operation cannot be avoided by using refrigeration oil with low compressibility with the working fluid in the low rotation range, lubrication performance can be ensured and good sliding condition can be maintained.

[0134] In this embodiment, an accumulator 14 is described as being included upstream of the suction pipe 12, but the accumulator 14 can be omitted. That is, even if liquid compression operation cannot be avoided by using refrigeration oil with low compatibility with the working fluid, the lubricating performance of the refrigeration oil can be ensured and a good sliding state can be maintained, so the accumulator 14 can be omitted.

[0135] Furthermore, the volume of the reservoir 14f of the accumulator 14 can be set to less than twice the suction volume formed in the cylinder 31. That is, even if liquid compression operation cannot be avoided by using refrigeration oil with low compatibility 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.

[0136] Furthermore, in this embodiment, a compression mechanism 30 consisting of one cylinder 31 and one piston 32 has been described, but it is also possible for a compression mechanism 30 consisting of two cylinders 31 and two pistons 32. Considering that such a rotary compressor with two pistons is suitable for low-speed operation, it is also preferable that each blade 33 operates without leaving its respective piston 32.

[0137] In addition, as a device that uses a rotary compressor 1 suitable for low-speed operation, it is particularly suitable for indoor air conditioners (household air conditioners) in air conditioning systems.

[0138] As described in this embodiment, a highly efficient rotary compressor can be achieved by using a compression mechanism 30 in which the blades 33 operate without leaving the piston 32.

[0139] In particular, by setting the working fluid to R32 and the refrigeration oil to alkylbenzene oil, low compatibility ensures lubrication performance and maintains good sliding conditions. Furthermore, the same applies to working fluids containing at least R32.

[0140] Furthermore, by using carbon dioxide as the working fluid and polyalkylene glycol oil as the refrigeration oil, low compatibility ensures lubrication performance and maintains good sliding conditions. The same applies to working fluids that contain at least carbon dioxide.

[0141] Furthermore, by setting the working fluid to R290 and the refrigeration oil to polyalkylene glycol oil, low compatibility ensures lubrication performance and maintains good sliding conditions. The same applies to working fluids containing at least R290.

[0142] In addition, the kinematic viscosity of the refrigeration oil is preferably below 35 mm / s. For example, if the working fluid contains carbon dioxide or R290, the refrigeration oil may also have a kinematic viscosity exceeding 35 mm / s.

[0143] In addition, the rotary compressor in which the blades 33 move without leaving the piston 32 can use R1234yf or HFO1123, working fluid containing R1234yf, or working fluid containing HFO1123. From the perspective of lubrication performance, in R1234yf or working fluid containing R1234yf, it is preferable to use alkylbenzene oil, and in HFO1123 or working fluid containing HFO1123, it is preferable to use ester oil or fragrance oil.

[0144] The equipment in this embodiment, which connects the rotary compressor 1, condenser 2, pressure reducing device 3, and evaporator 4 in a ring through piping, has high reliability.

[0145] Industrial availability

[0146] The device using a rotary compressor of the present invention is useful as a refrigeration cycle device such as a hot water heating device, an air conditioning device, a water heater, a cold storage, a display cabinet, a cooler, a dehumidifier, or a freezer.

Claims

1. A rotary compressor, characterized in that: The sealed container houses the electric motor and the compression mechanism. The electric motor and the compression mechanism are connected by a shaft. The compression mechanism includes a cylinder, a piston disposed within the cylinder, and blades that divide the cylinder. The shaft has an eccentric portion. Blade grooves for arranging the blades are formed on the cylinder. The eccentric portion is disposed inside the cylinder. The piston engages with the eccentric portion. A cylindrical groove with an arc angle exceeding 180° is formed on the piston. A cylindrical portion disposed in the cylindrical groove is formed at the end of the blade. The blades move without leaving the piston, wherein A notch is formed on the cylindrical portion, extending from one end face to the other. The cylindrical portion is divided into multiple arc surfaces by the notch. Each of the aforementioned arc surfaces is made with an arc angle of less than 180°. The notch is made into a rounded angle of less than 45°. The piston is made of a low-hardness material that gives the surface of the piston a Vickers hardness of less than Hv400. The notch is formed at the leading edge of the blade.

2. The rotary compressor as described in claim 1, characterized in that: At least two arcuate surfaces are formed on the outer circumferential surface of the cylindrical portion. The two formed arc surfaces are positioned at the position closest to the extended imaginary surface X.

3. A device, characterized in that: Using the rotary compressor as described in claim 1 or 2, The rotary compressor, condenser, pressure reducing device, and evaporator are connected in a ring via piping.

4. An indoor air conditioner, characterized in that: Using the rotary compressor as described in claim 1 or 2, The rotary compressor, condenser, pressure reducing device, and evaporator are connected in a ring via piping.

Images