JP7293024B2 - Rotary compressor and refrigeration cycle equipment - Google Patents

Description

An embodiment of the present invention relates to a rotary compressor and a refrigeration cycle apparatus including the rotary compressor.

Refrigerating cycle devices such as air conditioners are equipped with rotary compressors. A rotary compressor includes, as main elements, an electric motor section that rotates a rotating shaft, and a compression mechanism section that is connected to the electric motor section via the rotating shaft. The compression mechanism includes a cylinder that forms a cylinder chamber, and a roller that is fitted to the eccentric portion of the rotating shaft and rotates eccentrically within the cylinder chamber. The cylinder chamber is partitioned into a refrigerant suction chamber and a refrigerant compression chamber by vanes.

The vanes are arranged so that their tips are elastically abutted against the outer peripheral surface of the roller. When the rotary shaft is rotated by driving the electric motor, the roller is eccentrically rotated at the eccentric portion. While the rotating shaft rotates, the rollers and vanes slide against each other. Therefore, in order to rotate the rotating shaft with high precision and compress the refrigerant appropriately, it is necessary to slide the rollers and the vanes stably.

JP 2009-197793 A JP 2017-141802 A

In order to allow the rollers and vanes to slide stably over a long period of time, it is required to improve the wear resistance of these sliding portions. For example, when a rotary compressor is operated in a high differential pressure and high speed range, there is a risk that the sliding parts will wear more noticeably. Abrasion resistance is required.

An object of the present invention is to improve the wear resistance of the sliding portion between rollers and vanes, and to improve the rotational accuracy and compression performance of a rotary compressor, and a refrigerating machine equipped with the rotary compressor. To provide a cycle device.

According to an embodiment, the rotary compressor includes two cylinders forming a cylinder chamber, a rotating shaft having an eccentric portion arranged in the cylinder chamber, and an axis of the rotating shaft fitted in the eccentric portion in the cylinder chamber. It has a cylindrical roller that rotates eccentrically about a core, a vane that advances and retreats into a cylinder chamber with the eccentric rotation of the roller and divides the cylinder chamber into a suction chamber and a compression chamber, and an opening through which the rotating shaft passes. and a partition plate interposed between the two cylinders in the axial direction of the rotating shaft . The rollers are composed of a plurality of sub-rollers that are arranged substantially concentrically so as to overlap in the radial direction in two or more layers. Among the plurality of sub-rollers, the sub-roller arranged at the outermost periphery is formed of magnesium-added cast iron, has an area ratio of 5% or less of carbide precipitation on the sliding surface with the vane, and has a Rockwell hardness ( HRC) is 40 or more and 55 or less. The vane is formed by coating a diamond-like carbon film on its surface. Among the plurality of sub-rollers, the boundary between the inner peripheral surface of the sub-roller arranged on the outermost circumference and the outer peripheral surface of the sub-roller arranged inside one of the sub-rollers rotates partly in the circumferential direction with the opening of the partition plate. Do not overlap in the axial direction of the shaft.

BRIEF DESCRIPTION OF THE DRAWINGS It is a circuit diagram which shows roughly the structure of the refrigerating-cycle apparatus which concerns on 1st Embodiment. 1 is a cross-sectional view of a rotary compressor according to a first embodiment; FIG. FIG. 3 is a diagram showing a cross section of the compression mechanism of the rotary compressor in the arrow A2 portion shown in FIG. 2 in the direction of the arrow; FIG. 4 is a diagram showing the configuration of a roller according to a second embodiment, in which (a) is a cross-sectional view in a plane (horizontal plane) perpendicular to the axial direction of the rotating shaft, and (b) is parallel to the axial direction of the rotating shaft. 1 is a cross-sectional view in a horizontal plane (vertical plane); FIG.

[First Embodiment]
A first embodiment will be described below with reference to FIGS. 1 to 3. FIG.

FIG. 1 is a refrigerating cycle circuit diagram of an air conditioner 1 that is an example of a refrigerating cycle device according to this embodiment. The air conditioner 1 includes a rotary compressor 2, a four-way valve 3, an outdoor heat exchanger 4, an expansion device 5 and an indoor heat exchanger 6 as main elements.

As shown in FIG. 1 , the discharge side of the rotary compressor 2 is connected to the first port 3 a of the four-way valve 3 . A second port 3 b of the four-way valve 3 is connected to the outdoor heat exchanger 4 . The outdoor heat exchanger 4 is connected to the indoor heat exchanger 6 via the expansion device 5 . The indoor heat exchanger 6 is connected to the third port 3 c of the four-way valve 3 . A fourth port 3 d of the four-way valve 3 is connected to the suction side of the rotary compressor 2 via an accumulator 8 .

The refrigerant circulates through the circulation circuit 7 from the discharge side of the rotary compressor 2 to the suction side via the outdoor heat exchanger 4, the expansion device 5, the indoor heat exchanger 6, and the accumulator 8. As the refrigerant, a refrigerant containing no chlorine is preferable.

For example, when the air conditioner 1 operates in the cooling mode, the four-way valve 3 switches so that the first port 3a communicates with the second port 3b and the third port 3c communicates with the fourth port 3d. When the operation of the air conditioner 1 is started in the cooling mode, the high-temperature, high-pressure vapor-phase refrigerant compressed by the rotary compressor 2 is discharged to the circulation circuit 7 . The discharged gas-phase refrigerant is guided through the four-way valve 3 to the outdoor heat exchanger 4 functioning as a condenser (radiator).

The gas-phase refrigerant introduced to the outdoor heat exchanger 4 is condensed by heat exchange with the air, and changes into a high-pressure liquid-phase refrigerant. The high-pressure liquid-phase refrigerant is decompressed in the course of passing through the expansion device 5 and changes into a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to an indoor heat exchanger 6 that functions as an evaporator (heat absorber), and exchanges heat with air while passing through the indoor heat exchanger 6 .

As a result, the gas-liquid two-phase refrigerant absorbs heat from the air, evaporates, and changes into a low-temperature, low-pressure gas-phase refrigerant. The air passing through the indoor heat exchanger 6 is cooled by the latent heat of vaporization of the liquid-phase refrigerant, becomes cool air, and is sent to a place to be air-conditioned (cooled).

The low-temperature, low-pressure vapor-phase refrigerant that has passed through the indoor heat exchanger 6 is led to the accumulator 8 via the four-way valve 3 . If liquid-phase refrigerant that has not completely evaporated is mixed in the refrigerant, it is separated into a liquid-phase refrigerant and a gas-phase refrigerant here. The low-temperature, low-pressure vapor-phase refrigerant separated from the liquid-phase refrigerant is sucked into the rotary compressor 2 from the accumulator 8, and is again compressed by the rotary compressor 2 into a high-temperature, high-pressure vapor-phase refrigerant, which is sent to the circulation circuit 7. is discharged to

On the other hand, when the air conditioner 1 operates in the heating mode, the four-way valve 3 switches so that the first port 3a communicates with the third port 3c and the second port 3b communicates with the fourth port 3d. When the operation of the air conditioner 1 is started in the heating mode, the high-temperature, high-pressure gas-phase refrigerant discharged from the rotary compressor 2 is guided to the indoor heat exchanger 6 via the four-way valve 3, and Heat is exchanged with the air passing through the heat exchanger 6 . In this case, the indoor heat exchanger 6 functions as a condenser.

As a result, the vapor-phase refrigerant passing through the indoor heat exchanger 6 is condensed by exchanging heat with the air, and changes into a high-pressure liquid-phase refrigerant. The air passing through the indoor heat exchanger 6 is heated by heat exchange with the gas-phase refrigerant, becomes warm air, and is sent to a place to be air-conditioned (heated).

The high-temperature liquid-phase refrigerant that has passed through the indoor heat exchanger 6 is guided to the expansion device 5 and decompressed in the course of passing through the expansion device 5 to change into a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the outdoor heat exchanger 4 that functions as an evaporator, where it exchanges heat with the air to evaporate and change into a low-temperature, low-pressure gas-phase refrigerant. The low-temperature, low-pressure gas phase refrigerant that has passed through the outdoor heat exchanger 4 is sucked into the rotary compressor 2 via the four-way valve 3 and the accumulator 8, and is again converted into a high-temperature, high-pressure gas phase in the rotary compressor 2. The refrigerant is compressed and discharged to the circulation circuit 7 .

Next, a specific configuration of the rotary compressor 2 used in the air conditioner 1 will be described with reference to FIGS. 2 and 3. FIG. FIG. 2 is a cross-sectional view of the rotary compressor 2. As shown in FIG. As shown in FIG. 2, the rotary compressor 2 is a so-called vertical rotary compressor, and includes a sealed container 10, a compression mechanism section 11, and an electric motor section 12 as main elements.

The sealed container 10 has a cylindrical peripheral wall 10a and is erected along the vertical direction. A discharge pipe 10b is provided at the upper end of the sealed container 10 . The discharge pipe 10 b is connected to the first port 3 a of the four-way valve 3 via the circulation circuit 7 . Further, an oil reservoir 10c for storing lubricating oil I is provided in the lower portion of the sealed container 10. As shown in FIG.

As the lubricating oil I, for example, polyol ester oil, polyvinyl ether oil, polyalkylene glycol oil, mineral oil and the like can be applied. These lubricating oils I preferably do not contain extreme pressure additives. As an extreme pressure additive, for example, tricresyl phosphate can be applied.

The compression mechanism part 11 is housed in the lower part of the sealed container 10 so as to be submerged in the lubricating oil I. The compression mechanism section 11 has a twin cylinder structure, and includes a first cylinder 13, a second cylinder 14, a rotating shaft 15, a first roller 16, a second roller 17, a first vane 30a and a first cylinder. 2 vanes 30b are provided as main elements.

The first cylinder 13 is fixed to the inner peripheral surface of the peripheral wall 10 a of the closed container 10 . The second cylinder 14 is fixed to the bottom surface of the first cylinder 13 via a partition plate 18 .

A first bearing 20 is fixed above the first cylinder 13 . The first bearing 20 covers the inner diameter portion of the first cylinder 13 from above and protrudes upward from the first cylinder 13 . A space surrounded by the inner diameter portion of the first cylinder 13 , the partition plate 18 and the first bearing 20 constitutes a first cylinder chamber 21 . The partition plate 18 and the first bearing 20 correspond to closing members that respectively define one surface (lower surface and upper surface) of the rotary shaft 15 in the first cylinder chamber 21 in the axial direction.

A second bearing 22 is fixed below the second cylinder 14 . The second bearing 22 covers the inner diameter portion of the second cylinder 14 from below and protrudes downward from the second cylinder 14 . A space surrounded by the inner diameter portion of the second cylinder 14 , the partition plate 18 and the second bearing 22 constitutes a second cylinder chamber 23 . The partition plate 18 and the second bearing 22 correspond to closing members that respectively define one surface (upper surface and lower surface) of the rotating shaft 15 in the second cylinder chamber 23 in the axial direction. The first cylinder chamber 21 and the second cylinder chamber 23 are arranged coaxially with the central axis O1 of the sealed container 10 .

As shown in FIG. 2, the first cylinder chamber 21 and the second cylinder chamber 23 are connected to the accumulator 8 via suction pipes 25a, 25b which are part of the circulation circuit 7. As shown in FIG. The vapor-phase refrigerant separated from the liquid-phase refrigerant by the accumulator 8 is led to the first cylinder chamber 21 and the second cylinder chamber 23 through the suction pipes 25a and 25b.

The rotating shaft 15 has its axis located coaxially with the central axis O1 of the closed container 10 and passes through the first cylinder chamber 21 , the second cylinder chamber 23 and the partition plate 18 . The rotating shaft 15 has a first journal portion 27a, a second journal portion 27b and a pair of crankpin portions (eccentric portions) 28a and 28b. The first journal portion 27 a is rotatably supported by the first bearing 20 . The second journal portion 27b is rotatably supported by the second bearing 22. As shown in FIG.

Further, the rotating shaft 15 has a connecting portion 27c coaxially extending from the first journal portion 27a. The connecting portion 27 c penetrates the first bearing 20 and protrudes upward from the compression mechanism portion 11 . A rotor 33 of the electric motor portion 12, which will be described later, is fixed to the connecting portion 27c.

The eccentric portions 28a, 28b are located between the first journal portion 27a and the second journal portion 27b. The eccentric portions 28a and 28b have a phase difference of 180 degrees, for example, and have the same amount of eccentricity with respect to the central axis O1 of the sealed container 10. As shown in FIG. One eccentric portion (hereinafter referred to as first eccentric portion) 28 a is accommodated in the first cylinder chamber 21 . The other eccentric portion (hereinafter referred to as a second eccentric portion) 28b is accommodated in the second cylinder chamber 23. As shown in FIG.

FIG. 3 is a diagram showing a cross section of the compression mechanism portion 11 at the arrow A2 portion shown in FIG. 2 in the direction of the arrow. 3 shows the internal configuration of the first cylinder 13. As shown in FIG. The internal structure of the first cylinder 13 and the internal structure of the second cylinder 14 are substantially the same except for the portion that differs according to the phase difference between the first eccentric portion 28a and the second eccentric portion 28b. Therefore, the internal configuration of the second cylinder 14 conforms to the configuration shown in FIG.

As shown in FIGS. 2 and 3, the tubular first roller 16 is fitted to the outer peripheral surface 29a of the first eccentric portion 28a. A slight gap is provided between the inner peripheral surface 16a of the first roller 16 and the outer peripheral surface 29a of the first eccentric portion 28a to allow the rotation of the first roller 16 with respect to the first eccentric portion 28a. ing. As a result, the first roller 16 rotates eccentrically within the first cylinder chamber 21 when the rotary shaft 15 rotates, and a part of the outer peripheral surface 16b of the first roller 16 extends into the first cylinder chamber 21. slidably line contact with the inner peripheral surface 21a of the .

The cylindrical second roller 17 is fitted to the outer peripheral surface 29b of the second eccentric portion 28b. A slight gap is provided between the inner peripheral surface 17a of the second roller 17 and the outer peripheral surface 29b of the second eccentric portion 28b to allow rotation of the second roller 17 with respect to the second eccentric portion 28b. ing. As a result, the second roller 17 rotates eccentrically within the second cylinder chamber 23 when the rotary shaft 15 rotates, and a part of the outer peripheral surface 17b of the second roller 17 extends into the second cylinder chamber 23. slidably line contact with the inner peripheral surface 23a.

As shown in FIGS. 2 and 3, the first cylinder 13 is provided with a first vane 30a, and the second cylinder 14 is provided with a second vane 30b. Vane grooves 13a and 14a extending radially outward are formed in the inner peripheral portions of the cylinders 13 and 14, respectively. The first vane 30a is supported in the first vane groove 13a while being biased radially inward by biasing means 32a. Similarly, the second vane 30b is supported in the second vane groove 14a while being biased radially inward by biasing means 32b. Tip portions 31a and 31b of vanes 30a and 30b are slidably pressed against outer peripheral surfaces 16b and 17b of rollers 16 and 17, respectively. These vanes 30a and 30b cooperate with the rollers 16 and 17 to partition the cylinder chambers 21 and 23 into a suction chamber and a compression chamber, respectively. 23 and moves (advances and retreats) in a direction away from the cylinder chambers 21 and 23 . As the vanes 30a and 30b move forward and backward with respect to the cylinder chambers 21 and 23 in this manner, the volumes of the suction chambers and the compression chambers of the cylinder chambers 21 and 23 change, and the suction pipes 25a and 25b flow into the cylinder chambers 21 and 23. The sucked vapor phase refrigerant is compressed.

The high-temperature, high-pressure vapor-phase refrigerant compressed in the first cylinder chamber 21 and the second cylinder chamber 23 is discharged into the sealed container 10 via a discharge valve mechanism (not shown). The discharged gas-phase refrigerant rises inside the sealed container 10 . Furthermore, during the operation of the compression mechanism portion 11, the lubricating oil I stored in the oil reservoir portion 10c of the sealed container 10 is agitated. The agitated lubricating oil I becomes a mist and rises inside the sealed container 10 toward the discharge pipe 10b by being multiplied by the flow of the gas-phase refrigerant.

As shown in FIG. 2, the electric motor section 12 is accommodated in an intermediate portion along the central axis O1 of the sealed container 10 so as to be positioned between the compression mechanism section 11 and the discharge pipe 10b. The electric motor section 12 includes a so-called inner rotor type motor, and has a rotor 33 fixed to the rotating shaft 15 and a stator 34 fixed to the inner peripheral surface of the peripheral wall 10 a of the sealed container 10 .

A centrifugal oil separator 35 is incorporated in the upper end of the rotor 33 of the electric motor section 12 to separate the lubricating oil I contained in the gas-phase refrigerant rising inside the closed container 10 inside the closed container 10 . .

In the rotary compressor 2 having such a configuration, the cylinder structure of the compression mechanism portion 11, specifically, the first roller 16 and the second roller 17, the first vane 30a and the second vane 30b will be described in detail below. In this embodiment, the second roller 17 has the same structure as the first roller 16, and the second vane 30b has the same structure as the first vane 30a. Therefore, the configuration of the first roller 16 and the first vane 30a will be described below, and the description of the configuration of the second roller 17 and the second vane 30b will be omitted. In the second roller 17 and the second vane 30b, the same reference numerals are given to the structures having the same functions and actions as the first roller 16 and the first vane 30a.

In this embodiment, the first roller 16 is composed of a plurality of sub-rollers having different diameters. These sub-rollers are arranged substantially concentrically so as to overlap in the radial direction in two or more layers. 2 and 3 show an example of a first roller 16 having a double structure in which two sub-rollers 41 and 42 having different diameters are radially overlapped and arranged substantially concentrically. The first roller may have a multi-layer structure in which three or more sub-rollers are radially overlapped and arranged substantially concentrically.

Of the two sub-rollers 41 and 42, the inner sub-roller (hereinafter referred to as inner sub-roller) 41 has an inner diameter slightly larger than the outer peripheral surface 29a of the first eccentric portion 28a of the rotary shaft 15. It is said that The inner peripheral surface of the inner sub-roller 41 corresponds to the inner peripheral surface 16 a of the first roller 16 . Between the inner peripheral surface 16a of the inner sub-roller 41 and the outer peripheral surface 29a of the first eccentric portion 28a, a slight gap is provided to allow the rotation (rotation) of the inner sub-roller 41 with respect to the first eccentric portion 28a. there is Therefore, the rotation (rotation) speed of the inner sub-roller 41 is slower than the rotation speed of the rotating shaft 15 .

On the other hand, a sub-roller 42 located outside (hereinafter referred to as an outer sub-roller) has an outer diameter dimension that allows it to slide on the tip portion 31a of the first vane 30a. The inner diameter of the outer sub-roller 42 is slightly larger than the outer diameter of the inner sub-roller 41 . Therefore, a slight gap is formed between the outer peripheral surface 41a of the inner sub-roller 41 and the inner peripheral surface 42a of the outer sub-roller 42, and these sub-rollers 41 and 42 relatively rotate independently. In this case, the rotation (rotation) speed of the outer sub-roller 42 is slower than the rotation (rotation) speed of the inner sub-roller 41 .

In this embodiment, the outer sub-roller 42 is the outermost sub-roller of the two sub-rollers 41 and 42 , and its outer peripheral surface corresponds to the outer peripheral surface 16 b of the first roller 16 . Therefore, the sliding speed of the first roller 16 , specifically the outer sub-roller 42 , with respect to the tip portion 31 a of the first vane 30 a can be made lower than the rotational speed of the rotating shaft 15 .

As shown in FIGS. 2 and 3, the inner sub-roller 41 and the outer sub-roller 42 have different wall thicknesses (inner/outer diameter difference). As an example in this embodiment, the thickness of the inner sub-roller 41 is smaller than the thickness of the outer sub-roller 42 . In the present embodiment, the boundary (gap) S between the outer peripheral surface 41 a of the inner sub-roller 41 and the inner peripheral surface 42 a of the outer sub-roller 42 is partly spaced between the opening 18 a of the partition plate 18 and the rotating shaft 15 in the circumferential direction. Do not overlap axially. The opening 18a of the partition plate 18 is an opening for the rotary shaft 15 to pass through the partition plate 18. As shown in FIG. If a portion of the boundary portion S and the opening 18a do not overlap in the axial direction of the rotating shaft 15, the thickness of the inner sub-roller 41 may be greater than the thickness of the outer sub-roller 42. The wall thickness may be equivalent.

According to such a configuration, the boundary portion S is prevented from directly facing the opening portion 18a, so that the pressure inside the opening portion 18a is prevented from being directly applied to the boundary portion S. The pressure (P1) inside the opening 18a is substantially the same as the discharge pressure (P1), which is the pressure inside the sealed container 10. As shown in FIG. Therefore, the pressure of the boundary portion S becomes a pressure (P2) lower than the discharge pressure (P1) of the sealed container 10. As shown in FIG. That is, the pressure difference required to be sealed by the outer sub-roller 42 can be made as small as the pressure difference between the pressure (P2) of the boundary portion S and the suction pressure (P3) of the suction chamber. Therefore, the amount of high-pressure refrigerant leaking from the opening 18a to the suction chambers of the first cylinder chamber 21 and the second cylinder chamber 23 can be reduced. As a result, it is possible to suppress a decrease in the amount of gas-phase refrigerant sucked from the outside by the suction chamber, thereby suppressing a decrease in compression efficiency.

As described above, by forming the first roller 16 and the second roller 17 into a double structure, the vanes 30a, 30b are more likely to move than when these rollers 16, 17 are formed of a single cylindrical member. It is possible to reduce the sliding speed of the outer peripheral surfaces 16b, 17b with respect to the distal end portions 31a, 31b. As a result, wear of the tip portions 31a, 31b of the vanes 30a, 30b and the outer peripheral surfaces 16b, 17b of the rollers 16, 17 can be reduced.

In order to further reduce the wear of the tip portions 31a, 31b and the outer peripheral surfaces 16b, 17b, in this embodiment, the first vane 30a, the second vane 30b, and the outer sub-roller 42 are made of the following materials.

The first vane 30a and the second vane 30b are formed by using a high-speed tool steel (SKH material) as a base material and coating the surface thereof with a diamond-like carbon (DLC) film.
As the SKH material that is the base material, for example, tungsten-based SKH2 to SKH4 and molybdenum-based SKH50 to SKH59 are applicable.

Examples of diamond-like carbon include hydrogen-free DLC, hydrogen-containing DLC, and Si-containing DLC. In this embodiment, the DLC film is formed on the entire surfaces of the first vane 30a and the second vane 30b. However, the DLC film should be formed at least on the surfaces of the tip portions 31a and 31b of the vanes 30a and 30b, which are the sliding portions with the outer sub-roller . The film thickness of the DLC may be set according to the sliding pressure with the outer sub-roller 42 and the like.

It is preferable that the DLC film interposes an underlying layer between the SKH material and the SKH material, which is the base material, in order to increase the adhesion to the SKH material. For example, the underlayer contained a first layer consisting of a single layer of chromium from the surface side of the SKH material, a second layer consisting of a chromium-tungsten carbide alloy layer, and at least one of tungsten and tungsten carbide. and a third layer comprising a metal-containing amorphous carbon layer. The second layer has a concentration gradient of chromium and tungsten carbide, the chromium content is higher on the first layer side than the third layer side, and the tungsten carbide content is on the first layer side is preferably higher on the third layer side than Preferably, the third layer has a tungsten or tungsten carbide concentration gradient, and the tungsten or tungsten carbide content is higher on the second layer side than on the DLC film side.

The vanes 30a, 30b and the outer sub-roller 42 which slides are made of spheroidal graphite cast iron (FCD: Ferrum Casting Ductile). Spheroidal graphite cast iron is a material in which graphite crystallizes spherically and has excellent lubricity and high rigidity (Young's modulus). For example, the outer sub-roller 42 is made of magnesium (Mg)-added cast iron, and has a predetermined amount of precipitated carbide (area ratio) and Rockwell hardness (HRC) on the sliding surfaces of the vanes 30a and 30b with the DLC film. Specified within a range. As an example, spheroidal graphite cast iron contains Mg, C, Si, Mn, P, and S in predetermined weight percentages, and the balance is Fe. Further, as an example, the amount of precipitated carbide is 5% or less in terms of area ratio, and the range of HRC is 40 or more and 55 or less. The area ratio of the amount of precipitated carbides can be adjusted within a predetermined range according to the amount of P (phosphorus), which is a component of the spheroidal graphite cast iron. As a result, when the outer sub-roller 42 slides on the DLC film, the outer sub-roller 42 generates moderate friction and the surface pressure is reduced.

The material of the inner sub-roller 41 is not particularly limited, but preferably has a thermal expansion coefficient equal to or less than that of the outer sub-roller 42 . As a result, the gap (boundary portion S) between the inner sub-roller 41 and the outer sub-roller 42 is expanded, and leakage of the compressed gas can be suppressed. In this embodiment, as an example, the inner sub-roller 41 is made of spheroidal graphite cast iron that is substantially the same as the outer sub-roller 42 . By lowering the rigidity of the inner sub-roller 41 and the rigidity of the outer sub-roller 42, the sub-rollers 41 and 42 can be prevented from sliding and wearing.

In this manner, the outer sub-roller 42 is made of spheroidal graphite cast iron, and the first vane 30a and the second vane 30b are formed by coating the surface of the SKH material with a DLC film, thereby increasing the rigidity of the outer sub-roller 42. whirling can be suppressed. As a result, the inclination of the outer sub-roller 42 is suppressed, and it is possible to suppress the tip portions 31a and 31b of the vanes 30a and 30b from coming into contact with the DLC film. As a result, the outer sub-roller 42 and the vanes 30a, 30b can be stably slid over a long period of time, and the wear resistance of the sliding portions of both (the outer peripheral surfaces 16b, 17b and the tip portions 31a, 31b) can be improved. can improve.

In addition, since the first roller 16 and the second roller 17 have a double structure, even when the rotary compressor 2 is operated in a high differential pressure and high rotation range, these rollers 16 and 17 The sliding speed of the outer peripheral surfaces 16b and 17b with respect to the tips 31a and 31b of the vanes 30a and 30b can be reduced compared to the case where the vanes 30a and 30b are made of a single cylindrical member. As a result, the wear of the tip portions 31a, 31b and the outer peripheral surfaces 16b, 17b can be further reduced.

Therefore, it is possible to improve the reliability of the rotary compressor 2 by enhancing the rotational accuracy and compression performance. As a result, provision of the rotary compressor 2 can improve the reliability of the refrigeration cycle apparatus.

As described above, in this embodiment, both the first roller 16 and the second roller 17 have a double structure in which the two sub-rollers 41 and 42 overlap in the radial direction. In addition, these rollers may be a plurality of rollers (hereinafter referred to as subunits) stacked in the axial direction of the rotating shaft 15 . Hereinafter, an embodiment in which the roller is configured by laminating a plurality of subunits will be described as a second embodiment.

[Second embodiment]
FIG. 4 shows the configuration of the first roller 46 and the second roller 47 according to the second embodiment. 4A is a cross-sectional view in a plane (horizontal plane) perpendicular to the axial direction of the rotating shaft 15, and FIG. 4B is a cross-sectional view in a plane (vertical plane) parallel to the axial direction of the rotating shaft 15. is. The first roller 46 according to this embodiment is fitted to the outer peripheral surface 29a of the first eccentric portion 28a in the same manner as the first roller 16 according to the first embodiment. The second roller 47 is fitted to the outer peripheral surface 29b of the second eccentric portion 28b, like the second roller 17 according to the first embodiment. Therefore, the embodiment of the rotary compressor and the refrigeration cycle device to which the first roller 46 and the second roller 47 are applied is similar to the rotary compressor 2 according to the first embodiment except for these rollers 46 and 47. and the refrigeration cycle device (air conditioner 1).

As shown in FIG. 4, the first roller 46 and the second roller 47 each comprise three subunits 43a, 43b and 43c. These subunits 43a, 43b, and 43c are stacked in the axial direction of the rotary shaft 15 and arranged substantially concentrically. In this embodiment, as an example, the subunits 43a, 43b, and 43c have the same thickness in the axial direction, and the first roller 16 and the second roller 17 according to the first embodiment have the same axial thickness. It corresponds to the dimension obtained by substantially dividing the thickness in the direction into three equal parts. However, the thicknesses of these subunits 43a, 43b, and 43c in the axial direction may not be the same, and may be different from each other. Also, the number of laminated subunits is not limited to three, and may be two or four or more.

Each of the subunits 43a, 43b, 43c includes a plurality of sub-rollers with different diameters. FIG. 4 shows, as an example, subunits 43a, 43b, 43c having a double structure in which two sub-rollers 44, 45 having different diameters are radially overlapped and arranged substantially concentrically. Each of the subunits 43a, 43b, and 43c may have a multi-layer structure in which three or more sub-rollers are radially overlapped and arranged substantially concentrically.

Of the two sub-rollers 44 and 45, the inner sub-roller (hereinafter referred to as the inner sub-roller) 44 has the same configuration as the inner sub-roller 41 of the first embodiment except for the thickness in the axial direction of the rotating shaft 15. It is A sub-roller 45 located on the outer side (hereinafter referred to as an outer sub-roller) is configured similarly to the outer sub-roller 42 of the first embodiment, except for the thickness in the axial direction of the rotating shaft 15 .

The inner sub-roller 44 and the outer sub-roller 45 are made of spheroidal graphite cast iron (FCD), like the inner sub-roller 41 and the outer sub-roller 42 according to the first embodiment.

That is, in the present embodiment, the first roller 46 corresponds to a configuration in which the first roller 16 is divided into three parts in the axial direction of the rotating shaft 15, and the second roller 47 is the same as the second roller 17. Corresponds to a split configuration.

In this way, by configuring the first roller 46 and the second roller 47 by stacking the subunits 43a, 43b, and 43c in the axial direction of the rotating shaft 15, the inclination of the outer sub-roller 45 can be adjusted to each sub-unit. It can be suppressed for each unit 43a, 43b, 43c. Therefore, it is possible to more efficiently prevent the tip portions 31a and 31b of the first vane 30a and the second vane 30b from coming into contact with the DLC film. Moreover, since the sliding area of the rollers 46 and 47 with respect to the vanes 30a and 30b is divided and reduced, the surface pressure that the rollers 46 and 47 receive can be dispersed. These can further reduce wear of the rollers 46, 47 and the vanes 30a, 30b.

Although each embodiment of the present invention has been described above, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and modifications can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the scope of the invention described in the claims and equivalents thereof.

For example, in the above-described first and second embodiments, the rotary compressor 2 has the same volume of the first cylinder chamber 21 and the volume of the second cylinder chamber 23 . Alternatively, the rotary compressor may be of a different volume type in which each cylinder chamber has a different volume. Also, the rotary compressor may have one or more than three cylinders.

DESCRIPTION OF SYMBOLS 1... Refrigeration cycle apparatus (air conditioner), 2... Rotary compressor, 4... Outdoor heat exchanger, 5... Expansion device, 6... Indoor heat exchanger, 7... Circulation circuit, 8... Accumulator, 10... Closed container , 11... compression mechanism part, 12... electric motor part, 13... first cylinder, 13a... first vane groove, 14... second cylinder, 14a... second vane groove, 15... rotating shaft, 16, 46 1st roller 17, 47 2nd roller 18 Partition plate 20 First bearing 21 First cylinder chamber 22 Second bearing 23 Second cylinder chamber 28a... First eccentric part 28b... Second eccentric part 30a... First vane 30b... Second vane 31a, 31b... Tip part 41, 44... Inner sub-roller 42, 45... Outer sub-roller , 43a, 43b, 43c, subunits, I, lubricating oil, O1, central axis of closed container, and S, boundary.

Claims (5)

two cylinders forming a cylinder chamber;
a rotating shaft having an eccentric portion disposed within the cylinder chamber;
a cylindrical roller that is fitted to the eccentric portion and rotates eccentrically with respect to the axis of the rotating shaft in the cylinder chamber;
a vane that advances and retreats into the cylinder chamber with the eccentric rotation of the roller and divides the cylinder chamber into a suction chamber and a compression chamber;
a partition plate having an opening through which the rotating shaft penetrates and interposed between the two cylinders in the axial direction of the rotating shaft;
The roller is composed of a plurality of sub-rollers arranged substantially concentrically so as to overlap in the radial direction in two or more layers,
Among the plurality of sub-rollers, the sub-roller arranged at the outermost periphery is made of magnesium-added cast iron, has an area ratio of 5% or less of carbide precipitation on the sliding surface with the vane, and has a Rockwell Hardness (HRC) is 40 or more and 55 or less,
The vane is formed by coating a diamond-like carbon film on its surface ,
Of the plurality of sub-rollers, the boundary between the inner peripheral surface of the sub-roller arranged on the outermost circumference and the outer peripheral surface of the sub-roller arranged inside one of the sub-rollers is part of the partition plate in the circumferential direction. The opening does not overlap in the axial direction of the rotating shaft
Rotary compressor. The rotary compressor according to claim 1, wherein the base material of the vane is high speed tool steel. The rotary compressor according to claim 1 or 2, wherein a plurality of said rollers having a plurality of said sub-rollers are stacked in the axial direction of said rotating shaft. The rotary compressor according to any one of claims 1 to 3, wherein the roller is composed of two sub-rollers, and the two sub-rollers have different thicknesses in the radial direction. a rotary compressor according to any one of claims 1 to 4;
a condenser connected to the rotary compressor;
an expansion device connected to the condenser;
and an evaporator connected to the expansion device. A refrigeration cycle device.

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