阅读说明：本技术 制冷剂压缩机和使用了其的设备 (Refrigerant compressor and apparatus using the same ) 是由 小林正则 石田贵规 于 2019-11-05 设计创作，主要内容包括：本发明提供一种制冷剂压缩机,包括：积存有冷冻机油的密闭容器；收纳于密闭容器,由从外部供给的电力驱动的电动构件；和压缩构件,其被收纳于密闭容器且粘附有冷冻机油,由电动构件驱动,来压缩从外部供给的制冷剂气体。在冷冻机油中以溶解状态包含被调节为至少在运转时不析出的浓度的油膜缺失调节剂。(The present invention provides a refrigerant compressor, comprising: a closed container in which refrigerating machine oil is stored; an electric member housed in the sealed container and driven by electric power supplied from the outside; and a compression member which is accommodated in the closed container, to which the refrigerating machine oil adheres, and which is driven by the electric member to compress the refrigerant gas supplied from the outside. An oil film loss control agent is dissolved in a refrigerator oil and is adjusted to a concentration at least not to be precipitated during operation.)

1. A refrigerant compressor, comprising:

a closed container in which refrigerating machine oil is stored;

an electrically driven member housed in the sealed container and driven by electric power supplied from the outside; and

a compression member which is accommodated in the closed casing, to which the refrigerating machine oil adheres, and which is driven by the electric member to compress a refrigerant gas supplied from outside,

the oil film loss control agent is dissolved in the refrigerating machine oil and is adjusted to a concentration at least not to be precipitated during operation.

2. The refrigerant compressor as set forth in claim 1, wherein:

the oil film loss modulator comprises fullerene.

3. The refrigerant compressor as set forth in claim 1, wherein:

the oil film loss modulator comprises an organic compound having polarity.

4. A refrigerant compressor according to any one of claims 1 to 3, wherein:

the compression member has at least one pair of sliding parts sliding against each other,

the sliding surface of at least one of the pair of sliding members is made of a non-ferrous material.

5. The refrigerant compressor as set forth in claim 4, wherein:

the sliding surface of the other of the pair of sliding members is made of a ferrous material.

6. The refrigerant compressor according to claim 4 or 5, wherein:

the non-ferrous material includes at least any one of an aluminum alloy, a magnesium alloy, and a resin material.

7. A refrigerant compressor according to any one of claims 1 to 3, wherein:

the compression member has at least one pair of sliding parts sliding against each other,

each sliding surface of the pair of sliding members is made of an iron-based material.

8. The refrigerant compressor according to any one of claims 1 to 7, wherein:

the refrigerator oil contains the oil film loss control agent in an amount of 0.0001 to 0.5 wt%.

9. The refrigerant compressor according to any one of claims 1 to 8, wherein:

the viscosity of the refrigerating machine oil at 40 ℃ is set to 100mm²A value in a range of not more than s.

10. The refrigerant compressor as set forth in claim 9, wherein:

the viscosity of the refrigerator oil at 40 ℃ was set to 4.9mm²A value in a range of not more than s.

11. The refrigerant compressor according to any one of claims 1 to 10, wherein:

the viscosity of the refrigerating machine oil at 120 ℃ is set to 10.0mm²A value in a range of not more than s.

12. The refrigerant compressor according to any one of claims 1 to 11, wherein:

the refrigerant gas comprises natural refrigerant.

13. A refrigerant compressor as set forth in claim 12, wherein:

the natural refrigerant is at least one of R600a, R290, and R744, or a mixed refrigerant containing two or more of them.

14. The refrigerant compressor according to any one of claims 1 to 11, wherein:

the refrigerant gas comprises an HFC-based refrigerant.

15. A refrigerant compressor as set forth in claim 14, wherein:

the HFC-type refrigerant is at least one of R134a, 152a, R407c, R404A, R410A and R32, or a mixed refrigerant containing two or more of them.

16. The refrigerant compressor according to any one of claims 1 to 11, wherein:

the refrigerant gas is an HFO-type refrigerant or a mixed refrigerant containing the same.

17. A refrigerant compressor as set forth in claim 16, wherein:

the HFO-based refrigerant has a molecular structure including a double bond and two carbon atoms.

18. The refrigerant compressor according to any one of claims 1 to 17, wherein:

the refrigerator oil contains at least one of mineral oil, ester oil, alkylbenzene oil, polyvinyl ether, and polyalkylene glycol.

19. The refrigerant compressor according to any one of claims 1 to 18, wherein:

the electric component is driven in a variable frequency manner according to a plurality of operating frequencies.

20. An apparatus, characterized by:

the refrigerant compressor according to any one of claims 1 to 19, a radiator for radiating heat from the refrigerant, a pressure reducing device for reducing the pressure of the refrigerant, and a heat absorber for absorbing heat from the refrigerant are annularly connected by pipes.

Technical Field

The present invention relates to a refrigerant compressor used in an air conditioner (air conditioner), a refrigeration device, a washer-dryer, a water heater, and the like, and an apparatus using the same.

Background

In recent years, from the viewpoint of global environmental protection, the efficiency of refrigerant compressors has been increased to reduce the amount of fossil fuel used. For example, as disclosed in patent document 1, a refrigerant compressor has been developed in which an annular oil supply groove is provided in an outer peripheral portion of a piston of the refrigerant compressor, thereby reducing leakage loss of refrigerant from a compression chamber.

Fig. 6 is a schematic cross-sectional view of a conventional refrigerant compressor disclosed in patent document 1. Fig. 7 is a front view of a part of the refrigerant compressor of fig. 6 as viewed from arrow a. Fig. 8 is a sectional view of a main portion of a piston and its periphery of the refrigerant compressor of fig. 6.

As shown in fig. 6 to 8, the refrigerant compressor has a structure in which, for example, a compression element 6 and an electric element 5 are housed in a sealed container 1. The compression element 6 includes a main shaft portion 9 and an eccentric shaft portion 10 both extending in the vertical direction, and includes a crankshaft 8 supported by a shaft support portion 18, a piston 19 connected to the eccentric shaft portion 10, and a cylinder 15 formed with a cylinder 16. A cylindrical compression chamber 17 into which a piston 19 is inserted is formed in the cylinder 16. The electromotive element 5 includes a rotor 4 having a permanent magnet (not shown) embedded therein and press-fitted to and fixed to the main shaft portion 9, and a stator 3 having a winding. A refrigerating machine oil 7 is stored in a lower portion of the closed casing 1.

An oil supply structure 8a is provided on the crankshaft 8. The oil supply structure 8a has: an inclined pump 11 including a passage having one end opened in the refrigerating machine oil 7 and extending obliquely in the vertical direction in the main shaft portion 9, a viscous pump 12 including a circumferential groove formed in the outer surface of the main shaft portion 9 and connected to the other end of the inclined pump 11, and a vertical hole portion 13 and a horizontal hole portion 14 formed in the eccentric shaft portion 10. The vertical hole 13 and the horizontal hole 14 open into the internal space 2 of the sealed container 1 above the crankshaft 8.

The piston 19 is connected to the eccentric shaft portion 10 by a connecting member 20 and is inserted into the cylinder 16 so as to be slidable in a reciprocating manner. Two annular oil supply grooves 21 are formed in the outer peripheral portion of the piston 19 over the entire periphery of the piston 19. When the piston 19 is at the top dead center (for example, a position of an arrow B in fig. 8 where an upper end surface 19a of the piston 19 on the opposite side of the eccentric shaft portion 10 and one end of the cylinder 15 on the opposite side of the eccentric shaft portion 10 overlap when viewed in the radial direction of the cylinder 16), the oil supply groove 21 overlaps with the inner circumferential surface of the cylinder 15 when viewed in the radial direction of the cylinder 15. When the piston 19 is at the bottom dead center (for example, a position of an arrow C in fig. 8 where the upper end surface 19a of the piston 19 and a longitudinal middle portion of the cylinder 15 overlap when viewed in the radial direction of the cylinder 15), the oil supply groove 21 communicates with the internal space 2.

When the refrigerant compressor is driven, the crankshaft 8 rotates together with the rotor 4 of the electric component 5 by electric power supplied from the outside. The eccentric motion of the eccentric shaft portion 10 is transmitted to the piston 19 via the connecting member 20, whereby the piston 19 reciprocates between the top dead center and the bottom dead center in the compression chamber 17. The piston 19 compresses the refrigerant gas supplied into the closed casing 1 from an external cooling system (not shown) in the compression chamber 17. By repeating this compression operation, the refrigerant is sequentially sent from the refrigerant compressor to the cooling system.

The refrigerating machine oil 7 in the sealed container 1 is sucked upward by the inclined pump 11 by the centrifugal force of the rotation of the crankshaft 8, and is supplied to each sliding portion via the viscous pump 12. The refrigerator oil 7 is scattered into the internal space 2 through the vertical hole 13 and the horizontal hole 14. As shown in fig. 7 and 8, in this case, the refrigerating machine oil 7 is scattered from the vertical hole portion 13 and the horizontal hole portion 14 toward the piston 19 along the release path D formed in advance. The refrigerating machine oil 7 adheres to the circumferential surface of the piston 19 and the end surface of the cylinder 15 on the eccentric shaft portion 10 side, and thereby forms an oil reservoir 7a by surface tension or the like. The oil reservoir 7a is formed around the entire circumference of the annular oil supply groove 21. An oil film is formed between the piston 19 and the cylinder 16 by the refrigerating machine oil 7 in the oil reservoir 7a stored in the oil supply groove 21, and the sealing property of the gap (hereinafter, both are simply referred to as "sealing property") is ensured to reduce the leakage loss of the refrigerant.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2003-65236

Disclosure of Invention

Problems to be solved by the invention

Recently, for further improvement in efficiency of the refrigerant compressor, for example, reduction in viscosity of the refrigerating machine oil and low-speed operation transition of the refrigerant compressor by inverter driving are desired. However, this may make it difficult to form an oil film, or may make it difficult to maintain an oil film because, for example, the edge of the oil supply groove becomes a starting point for cutting the oil film (hereinafter, these problems are simply referred to as oil film missing). When the oil film loss occurs, there is a problem that the cooling capacity of the refrigerant compressor is reduced and the efficiency is reduced.

Accordingly, an object of the present invention is to provide a refrigerant compressor and a device using the same, which can prevent a reduction in sealing performance due to a lack of an oil film between a piston and a cylinder even when a low-speed operation is performed using a low-viscosity refrigerating machine oil, thereby preventing a reduction in cooling capacity and efficiency.

Means for solving the problems

In order to solve the above problems, an aspect of the present invention provides a refrigerant compressor, comprising: the method comprises the following steps: a closed container in which refrigerating machine oil is stored; an electric member housed in the closed container and driven by electric power supplied from the outside; and a compression member that is accommodated in the closed container, to which the refrigerating machine oil adheres, and that is driven by the electric member to compress refrigerant gas supplied from the outside, wherein an oil film lack adjusting agent adjusted to a concentration at least not to be precipitated during operation is contained in the refrigerating machine oil in a dissolved state.

According to the above configuration, the oil-film-loss control agent is contained in a dissolved state in the refrigerating machine oil stored in the closed casing, and therefore the oil film of the refrigerating machine oil can be easily maintained on the surface of the compression member. Thus, even when low-speed operation is performed using low-viscosity refrigerator oil, an oil film can be stably formed and maintained in, for example, a sliding gap between a piston and a cylinder of a compression element.

Further, since the oil film loss control agent adjusted to a concentration at least not to be precipitated during operation is contained in the refrigerator oil in a dissolved state, for example, the sliding surfaces of the piston and the cylinder are not scratched by the precipitates of the oil film loss control agent. Therefore, the sealability between the piston and the cylinder can be prevented from being lowered due to the absence of an oil film, and the cooling capability and efficiency can be prevented from being lowered.

In one aspect, the present invention provides a refrigeration apparatus including a refrigerant circuit in which the refrigerant compressor, a radiator for radiating heat from a refrigerant, a pressure reducing device for reducing pressure of the refrigerant, and a heat absorber for absorbing heat from the refrigerant are connected in a ring shape by pipes.

According to the above configuration, it is possible to provide a refrigeration apparatus including the refrigerant compressor, which can prevent a decrease in sealability between the piston and the cylinder due to oil film loss and can prevent a decrease in cooling capacity and efficiency even when a low-speed operation is performed using a low-viscosity refrigerator oil in the refrigerant compressor.

Effects of the invention

According to the present invention, even when low-speed operation is performed using low-viscosity refrigerator oil, it is possible to prevent a reduction in sealing performance due to a lack of an oil film between a piston and a cylinder, and therefore it is possible to provide a refrigerant compressor capable of preventing a reduction in cooling capacity and efficiency, and a refrigeration apparatus using the same.

Drawings

Fig. 1 is a schematic cross-sectional view of a reciprocating (reciprocating) refrigerant compressor according to embodiment 1.

Fig. 2 is a sectional view of a main portion of a piston and its periphery of the refrigerant compressor of fig. 1.

Fig. 3 is a schematic view of fullerenes used in the refrigerant compressor of fig. 1.

Fig. 4(a) is a graph comparing COP of the refrigerant compressors of the examples and comparative examples. (b) Is a comparison of the input of the refrigerant compressors of the examples and comparative examples. (c) Is a comparison graph of the refrigeration capacities of the refrigerant compressors of the examples and comparative examples.

Fig. 5 is a schematic view of the refrigeration apparatus of embodiment 2.

Fig. 6 is a schematic cross-sectional view of a conventional refrigerant compressor.

Fig. 7 is a front view of a portion of the refrigerant compressor of fig. 6 as viewed from arrow a.

Fig. 8 is a sectional view of a main portion of a piston and its periphery of the refrigerant compressor of fig. 6.

Detailed Description

Hereinafter, embodiments will be described with reference to the drawings.

(embodiment 1)

[ refrigerant compressor ]

Fig. 1 is a schematic cross-sectional view of a reciprocating (reciprocating) refrigerant compressor 100 according to embodiment 1. The refrigerant compressor 100 shown in fig. 1 is included in an air conditioner, a refrigeration apparatus, or the like. Refrigerant compressor 100 includes a closed casing 101, an electric component 105, and a compression component 106.

The closed casing 101 is filled with a refrigerant gas. As an example, the refrigerant gas is a natural refrigerant, an HFC (hydrofluorocarbon) refrigerant, an HFO (hydrofluoroolefin) refrigerant, or a mixed refrigerant containing the same.

Examples of the natural refrigerant include at least one of R600a, R290, and R744, or a mixed refrigerant containing two or more kinds thereof. The refrigerant of the present embodiment is R600a, which is a hydrocarbon refrigerant typified by a natural refrigerant having a low global warming potential. The HFC-based refrigerant includes, for example, at least one of R134a, 152a, R407c, R404A, R410A, and R32, or a mixed refrigerant containing two or more kinds.

As HFO-based refrigerant, there can be mentioned: at least one of 1,1,2 trifluoroethylene (R1123), trans-1, 2, difluoroethylene (R1132(E)), cis-1, 2 difluoroethylene (R1132(Z)), 1 difluoroethylene (R1132a), 2,3,3, 3-tetrafluoro-1-propene (HFO-1234yf), or a mixed refrigerant containing two or more of these refrigerants is used. For example, R1234yf is preferable as the HFO-based refrigerant. HFO-based refrigerants have a molecular structure containing a double bond and two carbon atoms.

In addition, the refrigerator oil 107 is stored in the closed casing 101. The refrigerator oil 107 contains at least one of mineral oil, ester oil, alkylbenzene oil, polyvinyl ether, and polyalkylene glycol. The refrigerator oil 107 according to the present embodiment includes a paraffin-based mineral oil having high compatibility with R600a as a base oil. As will be described later, the refrigerating machine oil 107 contains the oil film lack regulator 180 in a dissolved state, which is adjusted to a concentration at least not to be precipitated during operation.

In addition, in the case where the refrigerant compressor 100 of the present embodiment is used for an air conditioner, for example, the 1 st viscosity characteristic is that the viscosity of the refrigerator oil at 40 ℃ is set to 100mm²A value in a range of not more than s.

The refrigerating machine oil 107 of the present embodiment is a refrigerantWhen the compressor 100 is used for a refrigeration device, for example, the viscosity at 40 ℃ is set to 4.9mm as the 2 nd viscosity characteristic²A value in a range of not more than s. In the same manner, the viscosity of the refrigerator oil 107 at 120 ℃ was set to 10.0mm as the 3 rd viscosity characteristic²(more preferably 5.0 mm) or less²Less than s). When the refrigerant compressor 100 is used for a refrigeration apparatus, for example, the refrigerator oil 107 may have at least one of the 2 nd and 3 rd viscosity characteristics. For example, the refrigerating machine oil 107 may have a 3 rd viscosity characteristic without having a 2 nd viscosity characteristic.

The abovementioned viscosity at 40 ℃ corresponds here to the viscosity according to ISO 3448: the kinematic viscosity described in the ISO viscosity classification of 1975, and the viscosity grade of the refrigerator oil 107 can be represented by the ISO viscosity grade number (VG) of the classification.

The electric element 105 is housed in the sealed container 101 and is driven by electric power supplied from the outside. The electromotive element 105 has a stator 103 and a rotor 104. The rotor 104 has a winding and is fixed to a crankshaft 108 described later. The stator 103 is disposed to enclose a permanent magnet (not shown) therein and surround the outer periphery of the rotor 104. The electric component 105 is driven at a variable frequency by a plurality of operating frequencies including, for example, an operating frequency lower than 20 r/sec.

Compression element 106 is housed in hermetic container 101, is adhered to refrigerating machine oil 107, and is driven by electric element 105 to compress refrigerant gas supplied from the outside. Specifically, compression element 106 includes crankshaft 108, cylinder 115, coupling member 120, and piston 119.

Crankshaft 108 is made of cast iron, for example. The crankshaft 108 is disposed to extend in the vertical direction. The crankshaft 108 has a main shaft portion 109 and an eccentric shaft portion 110 arranged in a longitudinal direction. The main shaft portion 109 and the eccentric shaft portion 110 each extend in the vertical direction. The rotor 104 is press-fitted and fixed to the main shaft 109. Main shaft portion 109 is axially supported by main bearing 118. For example, the eccentric shaft 110 is disposed above the main shaft 109. The eccentric shaft portion 110 is disposed eccentrically with respect to the main shaft portion 109.

An oil supply structure 108a is provided in the crankshaft 108. The oil supply structure 108a includes: a tilt pump 111 including a passage having one end opened in the refrigerating machine oil 107 and extending obliquely in the vertical direction in the main shaft 109, a viscous pump 112 including a circumferential groove formed in the outer surface of the main shaft 109 and connected to the other end of the tilt pump 111, and a vertical hole 113 and a horizontal hole 114 formed in the eccentric shaft 110. Vertical hole 113 and horizontal hole 114 open into internal space 102 of sealed container 101 at the upper portion of crankshaft 108.

The cylinder 115 is made of cast iron, for example. A substantially cylindrical cylinder 116 is formed inside the cylinder block 115. The cylinder 116 extends in the horizontal direction, and a piston 119 is inserted to be slidable in a reciprocating manner. The inner space between piston 119 and the cylinder head in cylinder 116 becomes compression chamber 117. The cylinder block 115 has a main bearing 118. Eccentric shaft 110 and piston 119 are coupled by coupling member (connecting rod) 120.

A plurality of (here, two) annular oil supply grooves 121 are formed in the outer peripheral portion of piston 119 over the entire periphery of piston 119. The oil supply groove 121 overlaps the inner circumferential surface of the cylinder 115 as viewed in the radial direction of the cylinder 115 at the top dead center of the piston 119. Further, the oil supply groove 121 is at the bottom dead center of the piston 119, at least a portion thereof communicates with the internal space 102 outside the cylinder 115, and the remaining portion is located inside the cylinder 115.

Here, the compression member 106 has at least one pair of sliding members that slide with each other, and the sliding surface of at least one of the pair of sliding members is made of a nonferrous material. The non-ferrous material includes at least any one of an aluminum alloy, a magnesium alloy, and a resin material. The compression member 106 of the present embodiment has a plurality of pairs of sliding members. The sliding members constituting the pair include a piston 119, a cylinder 116, an eccentric shaft 110, and a connecting member 120. Each sliding member may be made of a material different from that of the sliding surface in a portion other than the sliding surface.

When refrigerant compressor 100 is driven, electric power such as commercial power supplied from the outside is supplied to electric element 105 via an external inverter drive circuit (not shown). Thereby, the electric component 105 is driven at a variable frequency according to a plurality of operating frequencies.

By rotating the crankshaft 108 with the rotor 104 of the electric component 105, the eccentric shaft 110 performs eccentric motion. Coupling member 120 reciprocates piston 119 between a top dead center and a bottom dead center in compression chamber 117 of cylinder 115. Thereby, the refrigerant gas introduced into hermetic container 101 from the cooling system (not shown) is sucked into compression chamber 117 and compressed. By repeating this compression operation, the refrigerant is compressed and sequentially sent from the refrigerant compressor 100 to the cooling system.

On the other hand, the refrigerating machine oil 107 in the closed casing 101 is sucked upward by the inclined pump 111 by the centrifugal force of the rotation of the crankshaft 108, and is supplied to each sliding portion via the viscous pump 112. Thereby, the respective sliding portions are lubricated by the refrigerator oil 107. Further, the refrigerator oil 107 is scattered into the internal space 102 through the vertical hole portion 113 and the horizontal hole portion 114.

As shown in fig. 2, in this case, in particular, the refrigerating machine oil 107 is scattered from the vertical hole portion 113 and the horizontal hole portion 114 to the internal space 102 along the release path M, N formed in advance. As a result, the scattered refrigerating machine oil 107 adheres to the circumferential surface of the piston 119 and the end surface of the cylinder 115 on the eccentric shaft portion 110 side, and forms an oil reservoir 107a by surface tension or the like.

The oil reservoir 107a is formed by filling an annular oil supply groove 121 around its entire circumference by capillary action. The refrigerating machine oil 107 in the oil reservoir 107a stored in the annular oil supply groove 121 forms an oil film, and maintains the sealing property between the piston 119 and the cylinder 116, thereby reducing the leakage loss of the refrigerant.

Here, in the refrigerant compressor 100, the oil film loss control agent 180 is included in the refrigerator oil 107 stored in the closed casing 101 in a dissolved state, and therefore the oil film of the refrigerator oil 107 can be easily maintained on the surface of the sliding portion of the compression element 106 or the like. Thus, even when low-speed operation is performed using the low-viscosity refrigerating machine oil 107, an oil film can be stably formed and maintained in, for example, a sliding gap between the piston 119 and the cylinder 116 of the compression member 106.

Further, since the oil-loss control agent 180 adjusted to a concentration at least not to be precipitated during operation is included in the refrigerating machine oil 107 in a dissolved state, for example, the sliding surfaces of the piston 119 and the cylinder 116 are not scratched by the precipitates of the oil-loss control agent 180. Therefore, the sealability between piston 119 and cylinder 116 can be prevented from being lowered due to the absence of an oil film, and the cooling capability and efficiency can be prevented from being lowered.

That is, by configuring the refrigerant compressor 100 by using the refrigerating machine oil 107 to which the oil film lack adjusting agent 180 is added while accommodating the electric element 105 and the compression element 106 that drives the electric element 105 and compresses the refrigerant, it is possible to prevent the oil film lack between the piston 119 and the cylinder 116 and maintain the sealing property. This can reduce leakage loss of the refrigerant from the compression chamber 117, and thus can realize the high-efficiency refrigerant compressor 100. Hereinafter, the oil film loss control agent 180 will be described in detail.

[ oil film loss modifier ]

The oil film loss control agent 180 easily forms an oil film of the refrigerating machine oil 107 on the surface of the sliding portion of the compression member 106, and prevents the oil film loss, thereby maintaining the oil film. The oil film loss control agent 180 is dissolved in the refrigerator oil 107 and does not precipitate under normal operating conditions of the refrigerant compressor 100. This prevents the surface of the sliding portion of the compression member 106 from being scratched by the deposit of the oil film deficiency adjusting agent 180 and causing a flaw.

The oil film loss modulator 180 is soluble in organic solvents. For example, the oil film loss control agent 180 includes fullerene 181. Here, the oil film loss control agent 180 is composed of only fullerene 181.

Fig. 3 is a schematic view of fullerene 181 used in refrigerant compressor 100 of fig. 1. The fullerene 181 is bonded to form a spherical network structure with a plurality of carbon atoms. Fullerene 181 is a third carbon allotrope following diamond and graphite, from which single clusters (molecules) can be separated.

Due to its structural characteristics, fullerene 181 is soluble in organic solvents such as benzene and toluene, although it is a carbon allotrope. Thereby, the fullerene 181 is well dissolved in the refrigerator oil 107. Further, it is found that the oil film loss control agent 180 contains the fullerene 181, thereby improving the extension of the refrigerator oil 107 and preventing the oil film loss even when the viscosity of the refrigerator oil 107 is reduced, thereby easily maintaining the oil film. As will be described later, the upper limit of the amount of fullerene 181 added to refrigerating machine oil 107 is limited, thereby preventing precipitation of fullerene 181 in refrigerating machine oil 107.

For example, the average particle size of a single cluster of the fullerene 181 is set to a value in the range of 100pm or more and 10nm or less (here, about 1 nm). The cross-sectional shape of the fullerene 181 is a fine particle having a substantially circular shape. The average particle diameter as used herein means a value derived from the einstein stokes law equation by detecting scattered light of particles in brownian motion by a dynamic light scattering method, determining a diffusion coefficient, and calculating the diffusion coefficient.

The fullerene 181 of the present embodiment is a mixed fullerene of a mixture of C60, C70, and a higher-order fullerene. Fig. 3 shows the structure of C60. As shown in fig. 3, the cluster of C60 is constructed by bonding 60 carbon atoms 181a to form a truncated octahedron composed of 12 five-membered rings 181b and 20 six-membered rings 181C. C60 is believed to have a particularly high molecular bearing effect. C70 is composed of 70 carbon atoms 181a, and is considered to have a molecular bearing effect similar to that of C60.

The mixed fullerene may include other fullerenes than those described above. A single cluster of fullerenes 181 may also contain less than 60 carbon atoms. The oil film loss control agent 180 may include a plurality of types of fullerenes 181 having different carbon atoms and contained in a single cluster, a plurality of types of fullerenes 181 having different average particle diameters, and the like. In addition, the oil film loss control agent 180 may contain only one kind of fullerene 181.

As a method for producing the fullerene 181, a known method can be appropriately selected. As an example, carbon black (soot) containing fullerene 181 is obtained by synthesizing a hydrocarbon feedstock in a predetermined combustion process. By filtering the coal with an organic solvent, a solution in which fullerene 181 containing C60, C70, and higher-order fullerenes (each referred to as a mixed fullerene) is dissolved can be separated from the residue. This solution is purified to obtain a mixed fullerene or separate individual fullerenes.

[ confirmation test 1]

A confirmation test for confirming the solubility of fullerene 181 in paraffin-based mineral oil was performed in the following procedure. At room temperature (25 ℃), a mixed fullerene composed of C60, C70, and higher-order fullerenes (C76, C82, etc.) whose diameter is set to a value in the range of 100pm or more and 10nm or less is prepared as fullerene 181. The oil film loss control agent 180 is composed of only the fullerene 181. A plurality of samples of the refrigerator oil 107 were prepared by adding an appropriate amount of fullerene 181 to paraffin-based mineral oil and sufficiently stirring the mixture. Then, each sample was left for a certain period of time to confirm the presence or absence of precipitation and precipitation of fullerene 181.

As a result, when the refrigerator oil 107 contained the fullerene 181 in the range of 0.5 wt% or less, the precipitation and deposition of the fullerene 181 were not observed in any of the samples. On the other hand, when the refrigerator oil 107 contains the fullerene 181 in a range exceeding 0.5 wt%, it was confirmed that precipitation and precipitation of the fullerene 181 occurred. This confirmed that the paraffin-based mineral oil used in this test can dissolve the fullerene 181 in a predetermined range.

Next, the same test as described above was performed by taking into consideration the conditions of the temperature-pressure range assumed in the refrigerant-refrigerator oil coexisting atmosphere in the refrigerant compressor 100. As a result, it was confirmed that when the refrigerator oil 107 contains the fullerene 181 in an amount exceeding 0.05 wt%, the fullerene 181 is precipitated and precipitated.

From the above test results, it is understood that the saturated dissolution amount of the fullerene 181 in the paraffin-based mineral oil is a value in the case where the refrigerator oil 107 contains 0.5 wt% of the fullerene 181 at room temperature (25 ℃). In other words, the saturated dissolution amount is the maximum amount of the fullerene 181 to be added, which satisfies the dissolution phenomenon that all the fullerenes 181 to be added are dispersed in the paraffin-based mineral oil to form a homogeneous system.

It is also understood that when a temperature-pressure range assumed under a refrigerant-refrigerator oil coexisting atmosphere in the refrigerant compressor 100 is considered, the refrigerator oil 107 preferably contains the fullerene 181 in an amount of 0.05 wt% or less.

Further, according to another test result, it is found that, when the refrigerator oil 107 contains the fullerene 181 in an amount of less than 0.0001 wt% at room temperature (25 ℃), the effect of adding the fullerene 181 is considerably low.

The amount of fullerene 181 in refrigerating machine oil 107 is preferably set as appropriate according to the type and state of the oil components of the refrigerant and refrigerating machine oil 107 used in refrigerant compressor 100, the temperature and internal pressure value of refrigerant compressor 100, and the like. For example, the refrigerating machine oil 107 preferably contains the fullerene 181 in a range of 0.0001 wt% to 0.5 wt%, and more preferably contains the fullerene 181 in a range of 0.001 wt% to 0.05 wt%.

Next, performance evaluation tests were performed on the refrigerant compressors of examples and comparative examples 1 and 2 in which various refrigeration oils having different specifications were sealed. FIG. 4(a) is a graph comparing Coefficient of Performance (COP) of the refrigerant compressors of examples and comparative examples 1 and 2. The coefficient of performance is a coefficient used as a target (index) of the energy consumption rate of a freezing and refrigerating apparatus or the like, that is, a value obtained by dividing the cooling capacity (W) by the applied input (W). Fig. 4(b) is a comparison diagram of the input of the refrigerant compressors of the embodiment and comparative examples 1 and 2. Fig. 4(c) is a diagram comparing the refrigeration capacities of the refrigerant compressors of the embodiment and comparative examples 1 and 2. Fig. 4 shows the evaluation results of the example and comparative examples 1 and 2 by the relative ratio when the evaluation result of comparative example 1 is 100.

In recent years, in order to achieve high efficiency, a refrigerant compressor 100 has been made to have a lower viscosity than that of the prior art (specifically, a viscosity at 40 ℃ C. is 4.9mm²(s or less). Thus, in the examples, the viscosity at 40 ℃ is 3.0mm²The fullerene 181 was dissolved in paraffin mineral oil as an oil film loss control agent 180, and the refrigerator oil 107 was prepared so as to contain the fullerene 181 in an amount of 0.001 wt%.

In comparative example 1, a viscosity of 4.9mm at 40 ℃ alone was used²A refrigerant oil comprising paraffin mineral oil. In comparative example 2, only 3.0mm having a viscosity at 40 ℃ lower than that of comparative example 1 was used²A refrigerant oil comprising paraffin mineral oil. That is, the refrigerator oils of comparative examples 1 and 2 were not added with fullerene 181.

As shown in FIGS. 4(a) to (b), the performance coefficients of the examples were higher than those of comparative examples 1 and 2. It is also seen that the example has a lower input than comparative examples 1 and 2. It is also understood that the example has a higher refrigerating capacity than comparative example 2 and the same refrigerating capacity as comparative example 1.

On the other hand, it is understood that comparative example 2 has a lower coefficient of performance than comparative example 1 and a significantly lower cooling capacity than comparative example 1. The refrigerating machine oil of comparative example 2 has a lower viscosity than that of comparative example 1, and can reduce the friction loss in the fluid lubrication region such as the sliding surface in the compression element, and therefore can reduce the input significantly.

Specifically, in the refrigerant compressor, normally, the annular oil supply groove 121 formed in the piston 119 holds the oil film of the refrigerating machine oil 107 by capillary action, thereby exhibiting sealing performance between the piston 119 and the cylinder 116 and suppressing leakage of the refrigerant gas from the gap.

Here, the refrigerating machine oil is reduced in viscosity (specifically, the viscosity is reduced to 4.9 mm)²Not more than s), the molecular motion of the oil component contained in the refrigerator oil becomes large by, for example, lowering the molecular weight, and the oil component is easily volatilized even under the same temperature conditions. Further, by lowering the viscosity of the refrigerating machine oil, the adsorption force of the refrigerating machine oil to the sliding surface of the compression member or the like may be reduced.

Thus, in comparative example 2, it is considered that the sealing property is lowered, and the refrigerant is likely to leak from between piston 119 and cylinder 116 in the process of suction and compression of the refrigerant during the reciprocation of piston 119, and the cooling capacity is remarkably lowered.

In contrast, in the examples, although a viscosity of 3.0mm at 40 ℃ was used²The refrigerating machine oil 107 having a low viscosity/s also suppresses the decrease in the refrigerating capacity. From the results, it is understood that the oil film loss control agent 180 dissolved in the refrigerator oil 107 can stably maintain good sealing properties even in the refrigerator oil 107 having a low viscosity.

Further, the reason why the fullerene 181 contained in the oil film loss control agent 180 exerts its effect is not clearly elucidated, but it is proposed that the fullerene has a radical trap effect derived from high electron compatibility due to structural symmetry. Therefore, in the refrigerator oil 107 containing the fullerene 181, for example, it is considered that the fullerene 181 acts on intermolecular attraction of the oil component, and the molecular motion of the oil component is inactivated, thereby suppressing the volatilization of the oil component.

In addition, it was confirmed in the confirmation test 1 that the refrigerator oil 107 used therein had a viscosity of 3.0mm at 40 ℃²Paraffin mineral oil/s, but even when used, has a viscosity of 2.2mm at 40 DEG C²The same effect can be obtained with paraffin mineral oil/s. From this confirmation result, it is considered that the viscosity of the refrigerator oil 107 at 40 ℃ is preferably at least 2.2mm²More than s.

[ confirmation test 2]

Next, a durability test of an actual machine using the refrigerant compressor was performed. In this test, a refrigerant compressor having a coupling member 120 whose sliding surface is made of an aluminum alloy and an eccentric shaft portion 110 whose sliding surface is made of an iron-based material was used. Example 1 of oil film loss control agent 180 containing fullerene 181 at a concentration of 50ppm and example 2 of oil film loss control agent 180 containing fullerene 181 at a concentration of 100ppm were prepared. In addition, a comparative example of an oil film loss adjusting agent containing no fullerene was prepared. In examples 1 and 2 and comparative example, the refrigerating machine oil used was a refrigerating machine oil having a viscosity of 2.2mm at 40 ℃²Paraffin mineral oil/s.

Each refrigerant compressor in which the refrigerating machine oil containing the oil film lack regulator is sealed is similarly operated in a predetermined high-temperature high-load intermittent operation mode in which the operation and the stop of the operation are repeated in a short time. This accelerates wear of the sliding surfaces of the eccentric shaft 110 and the coupling member 120. After the test, the refrigerant compressor was disassembled, and the abrasion of the coupling member 120 was confirmed.

As a result, assuming that the abrasion loss of the coupling member 120 of the comparative example is 100, the abrasion loss of the coupling member 120 of examples 1 and 2 is a value in a range of 46.1 to 72.4. It was thus confirmed that, in examples 1 and 2, the amount of wear of the connecting member 120 was significantly reduced compared to the comparative example, even though the connecting member 120 whose sliding surface was made of an aluminum alloy was used. From these results, it is considered that according to the refrigerant compressor 100 of the present embodiment, even when a non-ferrous material other than an aluminum alloy or an aluminum alloy is used for the sliding surface of the sliding member, the amount of wear of the sliding member can be appropriately reduced.

In recent years, in refrigerant compressors, low viscosity oil has been used as refrigerating machine oil for high efficiency, but this may increase wear of sliding surfaces of sliding members included in compression members of the refrigerant compressors. Therefore, the wear is suppressed by using an extreme pressure additive such as a phosphorus-based additive. However, even when such an additive is used, it is difficult to obtain a sufficient wear-inhibiting effect when the sliding surface of at least one of the pair of sliding members is made of a non-ferrous material.

In contrast, according to the refrigerant compressor 100 of the present embodiment, even when the low-viscosity refrigerator oil 107 is used, the amount of wear of the sliding surfaces of the pair of sliding members can be appropriately reduced as described above, and the refrigerant compressor 100 can be driven with high efficiency. Further, from the results of examples 1 and 2, it is found that in order to obtain such excellent effects, it is preferable that the viscosity of the refrigerator oil 107 at 40 ℃ is at least 2.2mm²More than s.

Further, it has been confirmed through another experiment conducted by the inventors that even in the case where the sliding surface of one of the pair of sliding members included in the compression member of the refrigerant compressor is made of a non-ferrous material and the sliding surface of the other is made of a ferrous material, the same excellent effects as described above are achieved. Further, it was confirmed that, in the case where the sliding surfaces of the pair of sliding members included in the compression member of the refrigerant compressor are made of an iron-based material, the amount of wear of the sliding surfaces is small as compared with the case where the sliding surfaces are made of a non-iron-based material, and the refrigerant compressor 100 can be driven with high efficiency.

From the above test results, according to the refrigerant compressor 100 of the present embodiment, even when the low-viscosity refrigerator oil 107 is used, the sealing performance between the piston 119 and the cylinder 116 is maintained, and the leakage loss of the refrigerant in the compression chamber 117 can be reduced. Further, the wear of the sliding parts of the compression element 106 of the refrigerant compressor 100 is reduced, and the refrigerant compressor 100 can be driven stably. Therefore, high performance of the refrigerant compressor 100 can be achieved.

Further, the oil film loss control agent 180 contains fullerene 181, and thereby formation of an oil film between piston 119 and cylinder 116 can be promoted. This prevents the sealability between piston 119 and cylinder 116 from being reduced by the loss of the oil film, and reduces the leakage loss of the refrigerant from compression chamber 117. Therefore, high performance of the refrigerant compressor 100 can be achieved.

In addition, as described above, fullerene 181 has high electronic compatibility due to structural symmetry, and for example, in the case of C60, 6 electrons can be trapped by one cluster. Therefore, radicals that are a factor of oxidation of the refrigerator oil 107 and the refrigerant are removed from the fullerene 181, and an effect of suppressing deterioration of the refrigerator oil 107 and the refrigerant can be expected. In addition, fullerene 181 is not consumed by chemical reactions. This can ensure the reliability of the refrigerant compressor 100 for a long period of time.

Therefore, for example, when the refrigerant compressor 100 is included in a stationary refrigeration apparatus disposed indoors or the like, the refrigeration apparatus can be stably driven while suppressing the generation of vibration and noise for several years. As an environment in which the stationary type refrigeration apparatus is used, for example, an environment in which the refrigeration apparatus is continuously driven without being maintained for a long period of time is assumed. Even in this case, since fullerene 181 contained in refrigerating machine oil 107 does not disappear, the refrigerating apparatus can be stably driven. As described above, the refrigerant compressor 100 is preferably used particularly in a stationary refrigeration apparatus.

Since the fullerene 181 has a spherical or elliptical shape, the fullerene 181 contained in the refrigerator oil 107 rolls when the opposing sliding surfaces move relative to each other, thereby exhibiting a molecular bearing effect due to rolling friction. This reduces the friction coefficient of the sliding portion, and thus can achieve a favorable input reduction. Therefore, for example, the torque at the time of starting the refrigerant compressor 100 can be reduced, and the startability of the refrigerant compressor 100 can be greatly improved.

Further, since the fullerene 181 is uniformly dispersed and dissolved in the refrigerating machine oil 107, the state in which the fullerene 181 is uniformly dispersed in the refrigerating machine oil 107 can be maintained even when the refrigerant compressor 100 is shifted from the operating state to the stopped state. As a result, when the refrigerant compressor 100 is restarted, metal contact on the surface of the sliding portion of the compression member 106 and the like can be alleviated, and the refrigerant compressor 100 can maintain good durability for a long period of time.

Further, since oil film loss control agent 180 contains an organic compound having polarity, formation of an oil film between piston 119 and cylinder 116 can be promoted. Therefore, it is possible to prevent the deterioration of the sealing property between piston 119 and cylinder 116 due to the disappearance of the oil film when refrigerating machine oil 107 having low viscosity is used during low-speed rotation. Therefore, the leakage loss of the refrigerant from the compression chamber 117 can be further reduced, and the refrigerant compressor 100 can be further improved in performance.

The refrigerator oil 107 used in the refrigerant compressor 100 contains the oil film loss control agent 180 in an amount of 0.0001 to 0.5 wt%. This can facilitate oil film formation when the refrigerant compressor 100 is used for a refrigeration device, for example. Further, by adding the oil film loss adjusting agent 180 in an excessive amount, precipitation of the oil film loss adjusting agent 180 is prevented, and clogging of the narrow tube existing in the compression member 106 and generation of a flaw on the sliding surface can be prevented.

Further, the viscosity of the refrigerating machine oil 107 used in the refrigerant compressor 100 at 40 ℃ is set to 100mm²A value in a range of not more than s. Thus, for example, when the refrigerant compressor 100 is used for an air conditioner application, even if the refrigerant compressor 100 is driven in a relatively high temperature state in an installation environment of the air conditioner, it is possible to reduce leakage loss of the refrigerant, reduce viscous loss of the refrigerant compressor 100, and reduce input of the refrigerant compressor 100.

The viscosity of the refrigerating machine oil 107 used in the refrigerant compressor 100 at 40 ℃ is setIs set to be 4.9mm²A value in a range of not more than s. Thus, for example, when the refrigerant compressor 100 is used for a refrigeration apparatus, the leakage loss of the refrigerant can be reduced, the viscosity loss of the refrigerant compressor 100 can be reduced, and the input of the refrigerant compressor 100 can be reduced.

Further, the viscosity of the refrigerating machine oil 107 used in the refrigerant compressor 100 at 120 ℃ was set to 10.0mm²A value in a range of not more than s. Thus, for example, when the refrigerant compressor 100 is used for a refrigeration apparatus, even if the refrigerant compressor 100 is driven in a relatively high temperature state in an installation environment of the refrigeration apparatus, it is possible to reduce leakage loss of the refrigerant, reduce viscous loss of the refrigerant compressor 100, and reduce input of the refrigerant compressor 100.

In addition, in the present embodiment, since the viscosity of the refrigerator oil 107 is kept low in the temperature range of 40 ℃ to 120 ℃, the viscosity loss of the refrigerant compressor 100 can be stably reduced in a wide temperature range. Therefore, for example, even in an application in an environment that is likely to be in a high temperature state and an application in which a temperature change in the environment is severe, a reduction in the input of the refrigerant compressor 100 is achieved while suppressing a leakage loss of the refrigerant.

Even if at least one of R600a, R290, and R744, or a natural refrigerant including two or more mixed refrigerants is used as the refrigerant, and at least one of mineral oil, ester oil, alkylbenzene oil, polyvinyl ether, and polyalkylene glycol is used as the refrigerator oil 107, the same effect as the present embodiment can be obtained, and the use of a refrigerant having a small greenhouse effect can contribute to suppression of global warming.

Even when at least one of R134a, 152a, R407c, R404A, R410A, and R32 is used as the refrigerant or an HFC-based refrigerant containing a mixed refrigerant of two or more kinds is used as the refrigerating machine oil 107, the same effects as described above can be achieved, and the refrigerant compressor 100 having high reliability and high efficiency can be achieved.

Even when an HFO-based refrigerant such as R1234yf or a mixed refrigerant containing the same is used as the refrigerant, and at least one of mineral oil, ester oil, alkylbenzene oil, polyvinyl ether, and polyalkylene glycol is used as the refrigerator oil 107, the same effects as described above can be achieved.

In this case, if the refrigerator oil 107 contains the fullerene 181, the fullerene 181 can be inactivated by trapping an acidic substance (for example, hydrofluoric acid) generated when the refrigerant is decomposed by sliding heat or the like. This can reduce the increase in the total acid value in the oil component of the refrigerator oil 107, and can reduce the attack of acidic substances on the surface of the sliding portion of the compression member 106. Therefore, the refrigerant compressor 100 having high reliability and high efficiency can be realized. In addition, the use of a refrigerant that is nonflammable and has little greenhouse effect can contribute to suppression of global warming.

Further, by performing the variable frequency driving of the electric element 105 in accordance with the plurality of operating frequencies, it is possible to prevent abnormal wear and maintain high reliability at any time during harsh high-speed operation such that the load acting on the sliding portions increases due to an increase in the number of revolutions and a decrease in the viscosity of the refrigerating machine oil due to heat generation in the sliding portions during low-speed operation in which the amount of oil supplied to the respective sliding portions decreases. Further, energy saving can be achieved by optimizing the operation of the refrigerant compressor 100 by inverter control.

The refrigerator oil 107 of the present embodiment contains paraffin-based mineral oil, but the fullerene 181 is favorably dissolved even when it contains at least one of other mineral oil or ester oil, alkylbenzene oil, polyvinyl ether, and polyalkylene glycol. For example, fullerene 181 is soluble in a solvent containing a compound having a carbonyl group (C ═ O group) or an ether group (R — O — R 'group) (where R and R' are organic groups), and it was confirmed in experiments that the amount of fullerene 181 saturated and dissolved in refrigerator oil 107 containing ester oil was the same as that of paraffin mineral oil.

In the present embodiment, the oil film loss adjusting agent 180 including the fullerene 181 is exemplified, but the oil film loss adjusting agent 180 may be constituted only by the fullerene 181, or may include a component other than the fullerene 181.

Here, the oil film loss control agent 180 according to the modified example includes an organic compound having polarity. As the component, for example, an organic polymer having polarity can be cited as the organic compound. Specifically, examples of the material include Polymethacrylate (PMA) material, Olefin Copolymer (OCP) material, and Polyisobutylene (PIB) material. Even when the oil film loss control agent 180 of the above modification is used, the same effects as described above can be expected.

In the present embodiment, although the effect of preventing performance degradation when the refrigerant compressor 100 is operated at a low speed (for example, at an operating frequency of 17Hz) is described, the same effect can be obtained even in the case of operation at a speed at a commercial frequency rotation speed and in the case of high-speed operation at a higher rotation speed.

That is, since the refrigerant compressor 100 of the present embodiment is driven by the inverter at a plurality of operating frequencies, the amount of oil supplied to each sliding portion is reduced during low-speed operation, but high performance can be maintained by the action of the oil film deficiency adjusting agent 180. Further, at the time of high-speed rotation, the load acting on the sliding portion increases, and the viscosity of the refrigerating machine oil decreases due to heat generation of the sliding portion, but abnormal wear is prevented by the action of the oil film loss control agent 180, and high reliability can be maintained. Further, energy saving can be achieved by optimizing the operation of the refrigerant compressor 171 by inverter control.

The refrigerant compressor is not limited to a reciprocating type (reciprocating type), and may be of another type, for example, a rotary type or a rolling type. Hereinafter, other embodiments will be described centering on differences from embodiment 1.

(embodiment 2)

Fig. 5 is a schematic diagram of a refrigeration apparatus 270 of embodiment 2. The basic configuration of the refrigeration apparatus 270 will be described below. As shown in fig. 5, the refrigeration apparatus 270 is an example of a device using the refrigerant compressor 100. The refrigeration unit 270 may also include a refrigerator. The refrigeration device 270 includes a main body 275, a partition wall 278, and a refrigerant circuit 271.

The main body 275 has a heat-insulating box body having an opening communicating with the inside and a door for opening and closing the opening of the box body. The main body 275 has a storage space 276 for storing articles and a machine room 277 in which a refrigerant circuit 271 for cooling the storage space 276 is disposed. The storage space 276 and the machine chamber 277 are separated by a partition wall 278. A fan (not shown) is disposed in the storage space 276. In fig. 5, a part of the case is cut out to show the inside of the main body 275.

The refrigerant circuit 271 includes a refrigerant compressor 100, a radiator 272, a pressure reducing device 273, and a heat absorber 274. Refrigerant compressor 100, radiator 272, pressure reducer 273, and heat absorber 274 are connected in an annular shape by pipes.

The heat sink 272 dissipates heat from the refrigerant. The pressure reducer 273 reduces the pressure of the refrigerant. The heat absorber 274 absorbs heat from the refrigerant. The heat absorber 274 is disposed in the storage space 276 and generates cooling heat. As indicated by arrows in fig. 5, the cooling heat of the heat absorber 274 is circulated in the storage space 276 by a fan. Thereby, the air in the storage space 276 is stirred to cool the storage space 276.

According to refrigerating apparatus 270 having the above configuration, even when low-speed operation is performed using low-viscosity refrigerator oil 107, refrigerating performance and efficiency can be prevented from being deteriorated while preventing sealability between piston 119 and cylinder 116 from being deteriorated due to oil film shortage by including refrigerant compressor 100 described above.

That is, since the refrigeration apparatus 270 includes the refrigerant circuit 271 and the refrigerant circuit 271 connects the refrigerant compressor 100, the radiator 272, the pressure reducing device 273, and the heat absorber 274 in a ring shape by pipes, it is possible to reduce power consumption and save energy by the refrigerant compressor 100 having improved volumetric efficiency.

The present invention is not limited to the embodiments, and modifications, additions, and deletions can be made to the structure without departing from the spirit and scope of the invention. The embodiments may be arbitrarily combined with each other, and for example, a part of the structure in one embodiment may be applied to another embodiment. The scope of the present invention is defined by the claims, and all changes that come within the meaning and range of equivalency of the claims are intended to be embraced therein. The equipment using the refrigerant compressor 100 is not limited to an air conditioner or a refrigerator, and may be, for example, a dry cleaner or a water heater.

Industrial applicability of the invention

As described above, the present invention has an excellent effect of providing a refrigerant compressor capable of preventing a reduction in cooling capacity and efficiency by preventing a reduction in sealing performance due to a lack of an oil film between a piston and a cylinder even when low-speed operation is performed using a low-viscosity refrigerator oil, and a refrigeration apparatus using the same. Therefore, the present invention is useful when applied to a wide range of refrigerant compressors and refrigeration systems using the same, which can exhibit the above-described effects.

Description of the reference numerals

100 refrigerant compressor

105 electric component

106 compression member

107 refrigerator oil

180 oil film loss regulator

181 Fullerene

270 refrigerating plant

271 refrigerant circuit

272 heat sink

273 pressure relief device

274 heat sink.