Rotary compressors and refrigeration cycle systems

Abstract

To provide a rotary compressor and a refrigeration cycle device that can suppress the deterioration of compression performance. [Solution] The rotary compressor of this embodiment comprises a cylinder, a rotor, normal vanes, hinged vanes, and a cylindrical component. The cylinder has a cylinder chamber. The rotor is positioned inside the cylinder chamber and has multiple slits formed on its outer circumference. The normal vanes and hinged vanes are positioned in the slits and move forward and backward relative to the cylinder chamber as the rotor rotates. The cylindrical component is in slidable contact with the inner wall of the cylinder. The hinged vanes have hinges formed on the ends that protrude relative to the cylinder chamber. A groove formed on the inner wall of the cylindrical component engages with the hinge of the hinged vane, and the hinged vane causes the cylindrical component to rotate integrally with the rotor.

Description

Technical Field

[0001] Embodiments of the present invention relate to a rotary compressor and a refrigeration cycle device.

Background Art

[0002] In a refrigeration cycle device, a rotary compressor is used to compress a refrigerant. A sliding vane type rotary compressor includes a cylinder, a rotor, and a vane. The cylinder has a cylinder chamber. The rotor is disposed inside the cylinder chamber and rotates around a rotation axis eccentric with respect to the cylinder chamber. The vane is disposed in a slit of the rotor, advances and retreats with respect to the cylinder chamber, and divides the cylinder chamber into small chambers. The refrigerant compressed in the small chamber is discharged from a discharge hole formed in the cylinder.

[0003] In a conventional vane type rotary compressor, compression is repeated while the inner wall surface of the cylinder and the tip of the vane always slide. Therefore, the sliding speed of the tip of the vane becomes large, and it is likely to be disadvantageous in terms of the PV (Pressure / Velocity) value, which is a sliding part reliability index. Further, in this vane type rotary compressor, when expanding the clearance volume, in order to suppress an increase in the surface pressure at the tip of the vane, the cylinder height may be increased without changing the eccentricity. In that case, an increase in the cylinder weight is inevitable. Further, in order to ensure the reliability of the sliding part, surface treatment of the inner wall surface of the cylinder is conceivable, but when the cylinder height is increased, the surface treatment cost increases.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] The problem that this invention aims to solve is to provide a rotary compressor and a refrigeration cycle device that can suppress the deterioration of compression performance. [Means for solving the problem]

[0006] The rotary compressor of this embodiment comprises a cylinder, a rotor, normal vanes, hinged vanes, and a cylindrical component. The cylinder has a cylinder chamber. The rotor is positioned inside the cylinder chamber and has multiple slits formed on its outer circumference. The normal vanes and hinged vanes are positioned in the slits and move forward and backward relative to the cylinder chamber as the rotor rotates. The cylindrical component is slidably in contact with the inner wall of the cylinder. The hinged vanes have hinges formed on the ends that protrude from the cylinder chamber. A groove formed on the inner wall of the cylindrical component engages with the hinge of the hinged vane, and the hinged vane causes the cylindrical component to rotate integrally with the rotor. [Brief explanation of the drawing]

[0007] [Figure 1] Circuit diagram of the refrigeration cycle device and cross-sectional view of the rotary compressor in the first embodiment. [Figure 2] Cross-sectional view of the compression mechanism along line II-II in Figure 1. [Figure 3] Figure 2 shows a cross-sectional view of the rotor after it has rotated by a predetermined angle. [Figure 4] A cross-sectional view of the rotor after it has rotated by a predetermined angle, as shown in Figure 3. [Figure 5] Perspective view of the cylindrical component and hinged vane in the first embodiment. [Figure 6] A plan view of the main part of the compression mechanism incorporating the cylindrical component and hinged vane in the first embodiment, as seen from the axial direction. [Figure 7] A perspective view of the first bearing in the first embodiment. [Figure 8] A perspective view of the second bearing in the first embodiment. [Figure 9] A plan view of the compression mechanism in the first embodiment, viewed from the axial direction. [Figure 10]Cross-sectional view of the compression mechanism along line XX in Figure 9. [Figure 11] A perspective view of the cylindrical component in the second embodiment. [Figure 12] A plan view of the main part of the compression mechanism incorporating the cylindrical component in the second embodiment, viewed from the axial direction. [Figure 13] A perspective view of the compression mechanism in the second embodiment. [Figure 14] A perspective view of a modified example of the compression mechanism in the second embodiment. [Modes for carrying out the invention]

[0008] (First Embodiment) The rotary compressor and refrigeration cycle device of the first embodiment will be described below with reference to Figures 1 to 10. Figure 1 includes a circuit diagram of the refrigeration cycle device 1 in this embodiment. The refrigeration cycle device 1 includes a rotary compressor 10, a four-way valve 3, a first heat exchanger 4, an expansion device 5, a second heat exchanger 6, and a refrigerant flow path 8 for circulating refrigerant (fluid) to these. The refrigerant circulates through the refrigeration cycle device 1 while undergoing phase changes.

[0009] The rotary compressor 10 compresses the low-pressure gaseous refrigerant taken inside into a high-temperature, high-pressure gaseous refrigerant. An accumulator (gas-liquid separator) 2b is located upstream of the rotary compressor 10. The accumulator 2b separates the gaseous and liquid two-phase refrigerant and supplies the gaseous refrigerant to the rotary compressor 10.

[0010] The four-way valve 3 reverses the direction of refrigerant flow in the refrigerant flow path 8 of the first heat exchanger 4, expansion device 5, and second heat exchanger 6. When the four-way valve 3 is in the state shown in Figure 1, the refrigerant discharged from the rotary compressor 10 flows in the order of first heat exchanger 4, expansion device 5, and second heat exchanger 6. At this time, the first heat exchanger 4 functions as a condenser (heat sink), and the second heat exchanger 6 functions as an evaporator (heat absorber).

[0011] When the four-way valve 3 switches from the state shown in FIG. 1, the refrigerant discharged from the rotary compressor 10 flows through the second heat exchanger 6, the expansion device 5, and the first heat exchanger 4 in this order. At this time, the second heat exchanger 6 functions as a condenser (radiator), and the first heat exchanger 4 functions as an evaporator (heat absorber).

[0012] The condenser dissipates heat from the high-temperature and high-pressure gaseous refrigerant discharged from the rotary compressor 10 to convert the high-temperature and high-pressure gaseous refrigerant into a high-pressure liquid refrigerant.

[0013] The expansion device 5 reduces the pressure of the high-pressure liquid refrigerant sent from the condenser to convert the high-pressure liquid refrigerant into a low-temperature and low-pressure gas-liquid two-phase refrigerant. For example, the expansion device 5 is an expansion valve.

[0014] The evaporator converts the gas-liquid two-phase refrigerant sent from the expansion device 5 into a low-pressure gaseous refrigerant. In the evaporator, when the low-pressure gas-liquid two-phase refrigerant vaporizes, it absorbs the heat of vaporization from the surroundings, thereby cooling the surroundings. The low-pressure gaseous refrigerant that has passed through the evaporator is taken into the interior of the above-described rotary compressor 10 via the accumulator 2b.

[0015] Thus, in the refrigeration cycle device 1, the refrigerant, which is the working fluid, circulates while undergoing a phase change between gas and liquid. The refrigerant dissipates heat during the process of changing from gas to liquid and absorbs heat during the process of changing from liquid to gas. The refrigeration cycle device 1 performs heating, cooling, defrosting, etc. by utilizing the heat dissipation or heat absorption of the refrigerant.

[0016] FIG. 1 includes a cross-sectional view of the rotary compressor 10 in the embodiment. FIGS. 2 to 4 are cross-sectional views of the compression mechanism portion 20 taken along line II-II of FIG. 1. In the present application, the Z direction, R direction, and θ direction in the cylindrical coordinate system are defined as follows. The Z direction is the axial direction of the rotor 16. The +Z direction is the direction from the compression mechanism 20 toward the motor 14. For example, the Z direction is the vertical direction, and the +Z direction is vertically upward. The R direction is the radial direction of the rotor 16. The +R direction is the radially outward direction. The θ direction is the circumferential direction of the rotor 16. The +θ direction (downstream) is the rotational direction of the right-hand screw that advances in the -Z direction. Note that the opposite directions of the +Z, +R, and +θ directions are the -Z, -R, and -θ directions (upstream), respectively.

[0017] The rotary compressor 10 is a sliding vane (rotary vane) type rotary compressor. As shown in Figure 1, the rotary compressor 10 has a case 11, an electric motor unit 14, a shaft 15, and a compression mechanism unit 20.

[0018] The case 11 is formed in a cylindrical shape with both ends closed and sealed. The case 11 houses the motor unit 14, the shaft 15, and the compression mechanism unit 20. Inside the case 11, in the -Z direction, is lubricating oil 12 for lubricating the compression mechanism unit 20. Inside the case 11, in the +Z direction, is the gaseous refrigerant compressed by the compression mechanism unit 20. The gaseous refrigerant and lubricating oil inside the case 11 are under high pressure. The gaseous refrigerant is supplied to the four-way valve 3 from the discharge port 13 in the +Z direction of the case 11 through the refrigerant flow path 8.

[0019] The motor unit 14 is located inside the case 11 in the +Z direction. The motor unit 14 has a stator 14a and a rotor 14b. The stator 14a is fixed to the inner circumferential surface of the case 11. The rotor 14b is located in the -R direction relative to the stator 14a.

[0020] The shaft 15 is arranged coaxially with the case 11. The rotor 14b of the motor unit 14 is fixed to the shaft 15 in the +Z direction. The rotor 16 of the compression mechanism unit 20 is fixed to the shaft 15 in the -Z direction. The motor unit 14 rotates the rotor 16 via the shaft 15. The shaft 15 and rotor 16 are separate components, but they may be integrated.

[0021] The compression mechanism 20 is located inside the case 11 in the -Z direction. The compression mechanism 20 includes a cylinder 21, a rotor 16, normal vanes 17 and hinged vanes 41 (see Figure 2), a cylindrical component 43, a first bearing (main bearing) 30, a second bearing (sub-bearing) 35, and a muffler 33.

[0022] The cylinder 21 has a cylindrical inner wall surface and is arranged coaxially with the case 11. The cylinder 21 is fixed to the inner circumferential surface of the case 11. As shown in Figure 2, the cylinder 21 has a cylinder chamber (compression chamber) 22. The cylinder chamber 22 is formed inside a through hole that penetrates the cylinder 21 in the Z direction. The central axis of the cylinder chamber 22 is eccentric from the central axis of the cylinder 21.

[0023] The rotor 16 is formed in a cylindrical shape. The rotor 16 is positioned inside the cylinder chamber 22. The space between the outer surface of the rotor 16 and the inner wall surface of the cylinder 21 functions as the actual cylinder chamber 22. The rotor 16 is positioned coaxially with the shaft 15. The axis of rotation of the rotor 16 coincides with the central axis of the cylinder 21 and is eccentric from the central axis of the cylinder chamber 22.

[0024] The distance between the outer surface of the rotor 16 and the inner wall surface of the cylinder 21 in the R direction (hereinafter simply referred to as the distance between the rotor and cylinder 21) changes along the θ direction. The distance between the rotor and cylinder 22 is maximized in the direction of eccentricity of the central axis of the cylinder chamber 22 with respect to the central axis of the cylinder 21 (down-left direction in Figure 2). The position where the distance between the rotor and cylinder 22 is maximized in the θ direction is called the bottom dead center BE. On the other hand, the distance between the rotor and cylinder 22 is minimized in the opposite direction of eccentricity of the central axis of the cylinder chamber 22 (up-right direction in Figure 2). The position where the distance between the rotor and cylinder 22 is minimized in the θ direction is called the top dead center (minimum distance position) TE.

[0025] In the example shown in Figure 2, there is only one top dead center (TDC) TE in the θ direction. In other words, when the rotor 16 completes one rotation from the TDC TE, the distance between the rotor and TDC simply increases as the rotor 16 passes the bottom dead center (BE), and then the distance between the rotor and TDC simply decreases as the rotor 16 returns to its original TDC TE. There may be multiple TDCs TE in the θ direction.

[0026] As shown in Figure 2, cylinder 21 has a refrigerant intake port (intake passage) 25 and a discharge port (discharge port) 26. The intake port 25 penetrates cylinder 21 in the R direction. The intake port 25 introduces gaseous refrigerant supplied from accumulator 2b (see Figure 1) into the cylinder chamber 22.

[0027] The discharge section 26 discharges the gaseous refrigerant compressed in the cylinder chamber 22 to the outside of the cylinder chamber 22. The discharge section 26 has a discharge hole that penetrates the closing portion 32 of the first bearing 30 in the Z direction. In the plan view of Figure 2, the discharge hole of the discharge section 26 is located in a position that coincides with the downstream end of the first small chamber 23a. In the plan view of Figure 2, the discharge hole of the discharge section 26 is located in a position that coincides with the muffler 33. When the gaseous refrigerant in the first chamber 23a is compressed to a pressure exceeding the specified pressure, the valve 45 of the discharge section 26 opens, and the compressed gaseous refrigerant in the first chamber 23a is discharged into the muffler chamber 34.

[0028] In the example shown in Figure 2, the rotor 16 rotates in the +θ direction (counterclockwise). In this application, the upstream side (-θ direction) of the rotor 16's rotation direction is sometimes simply referred to as the "upstream side," and the downstream side (+θ direction) of the rotor 16's rotation direction is sometimes simply referred to as the "downstream side." The suction port 25 is located downstream of the top dead center TE of the cylinder chamber 22. The discharge section 26 is located upstream of the top dead center TE of the cylinder chamber 22.

[0029] The vanes 17 are typically formed in a flat shape from a metallic material. The vanes 17 are positioned in one of a plurality of slits 18 formed in the rotor 16. The slits 18 penetrate the rotor 16 in the Z direction. The slits 18 extend, for example, along the R direction. The +R direction end of the slit 18 opens onto the outer circumferential surface of the rotor 16. A back pressure chamber 19 is formed at the -R direction end of the slit 18. High-pressure lubricating oil 12 (see Figure 1) enters the back pressure chamber 19. The pressure of the lubricating oil 12 in the back pressure chamber 19 acts on the vanes 17. In addition, centrifugal force acts on the vanes 17 as the rotor 16 rotates. The vanes 17 are pressed against the inner wall surface of the cylinder 21 by the pressure of the lubricating oil 12 in the back pressure chamber 19 and the centrifugal force. The vanes 17 move back and forth relative to the cylinder chamber 22 and cylindrical component 43 as the rotor 16 rotates.

[0030] Figure 5 is a perspective view of the cylindrical component 43 and the hinged vane 41 in the first embodiment. As shown in Figures 2 and 5, the hinged vane 41 differs from the ordinary vane 17 in that a hinge 42 is formed on the end that protrudes toward the cylinder chamber 22. The hinge 42 is formed in an axial shape (cylindrical shape) along the axial direction of the cylinder 21 and has an outer surface covering more than half of the circumference. The hinged vane 41, like the ordinary vane 17, is formed in a flat shape from a metallic material and is positioned in one of the multiple slits 18 formed in the rotor 16. A groove 44 is formed in the inner wall of the cylindrical part 43 for engaging the hinge 42 of the hinged vane 41. The groove 44 is formed to extend along the Z direction.

[0031] Figure 6 is a plan view of the main part of the compression mechanism 20, which incorporates the cylindrical component 43 and the hinged vane 41 in the first embodiment, as seen from the axial direction. As shown in Figure 6, the cylindrical component 43 is formed in a cylindrical shape along the inner wall surface of the cylinder 21 and is positioned coaxially with the cylinder 21. The cylindrical component 43 is provided so that its outer circumferential surface can slide against the inner wall surface of the cylinder 21. The cylindrical component 43 is installed inside the cylinder 21 with the hinge 42 of the hinged vane 41 engaged with the groove 44, and the hinged vane 41 is assembled to swing around the axis of the hinge 42. The cylindrical component 43 and the hinged vane 41 are able to rotate integrally in synchronization with the rotor 16.

[0032] In this embodiment, of the multiple vanes 17, 41, one vane is a hinged vane 41 having a hinge 42, while the other vanes are ordinary vanes 17 whose tips slide against the inner wall surface of the cylindrical part 43. By having only one vane engage with the groove 44 of the cylindrical part 43 at its end, and having the other vanes have a general structure in which their tips slide against the inner wall surface of the cylindrical part 43, cost increases can be suppressed, and eccentric rotation of the rotor 16 relative to the cylindrical part 43 can be easily achieved.

[0033] As shown in Figure 2, multiple vanes 17, 41 are arranged at equal angular intervals in the θ direction. The multiple vanes 17, 41 divide the cylinder chamber 22 into multiple small chambers (working chambers) 23 in the θ direction. In Figure 2, the small chamber 23 facing the discharge section 26 is designated as the first small chamber 23a, and the small chamber 23 adjacent to the upstream side of the first small chamber 23a is designated as the second small chamber 23b. The second small chamber 23b faces the suction hole 25.

[0034] Next, the operation of the compression mechanism 20 will be explained with reference to Figures 2 to 4. As shown in Figure 2, the small chamber 23 moves in the +θ direction as the rotor 16 rotates. When the small chamber 23 (downstream of the first small chamber 23a in Figure 2) moves from top dead center TE to bottom dead center BE, the volume of the small chamber 23 increases. The small chamber 23, which communicates with the suction port 25, draws in gaseous refrigerant from the suction port 25 as its volume increases (see Figures 3 and 4).

[0035] As the small chamber 23 (upstream of the first small chamber 23a in Figure 2) moves from bottom dead center BE to top dead center TE, the volume of the small chamber 23 decreases. As the volume of the small chamber 23 decreases, it compresses the gaseous refrigerant. When the gaseous refrigerant is compressed to a pressure above the specified pressure, the valve 45 of the discharge section 26 opens, and the high-pressure gaseous refrigerant is discharged from the discharge section 26 (see Figures 3 and 4).

[0036] For each rotation of the rotor 16, the gaseous refrigerant is drawn in and discharged a predetermined number of times. The predetermined number of times corresponds to the number of vanes 17 and 41. In the example in Figure 2, there is normally one vane 17 and one hinged vane 41, but there may be two or more normal vanes 17 and hinged vanes 41. In Figure 2, the vane located at the upstream end of the first chamber 23a is a normal vane 17, and the vane located at the downstream end of the first chamber 23a is a hinged vane 41.

[0037] In the sliding vane type rotary compressor 10, the rotor 16 rotates coaxially with the shaft 15. This rotary compressor 10 is low-cost and low-vibration. It can also suppress noise caused by vibration. In this rotary compressor 10, the cylinder chamber 22 is divided into multiple small chambers 23 by multiple vanes 17,41. The volumetric flow rate per section is reduced, and suction and discharge pulsations are reduced. In this rotary compressor 10, the multiple vanes 17,41 are arranged on the rotor 16 and not on the cylinder 21. As a result, the inner diameter of the cylinder chamber 22 is increased, the exhaust volume is increased, and the compression performance of the rotary compressor 10 is improved.

[0038] As shown in Figure 1, a first bearing (main bearing) 30 is positioned in the +Z direction of the cylinder 21. The first bearing 30 has a bearing portion 31 and a closing portion 32. The bearing portion 31 of the first bearing 30 rotatably supports the shaft 15 of the cylinder 21 in the +Z direction. The closing portion 32 of the first bearing 30 closes the opening of the cylinder chamber 22 in the +Z direction. Furthermore, as shown in the perspective view of Figure 7, a first recessed portion 38 is provided on the surface of the closing portion 32 of the first bearing 30 that faces the cylinder 21.

[0039] A second bearing (sub-bearing) 35 is positioned in the -Z direction of the cylinder 21. The second bearing 35 has a bearing portion 36 and a closing portion 37. The bearing portion 36 of the second bearing 35 rotatably supports the shaft 15 of the cylinder 21 in the -Z direction. The closing portion 37 of the second bearing 35 closes the opening of the cylinder chamber 22 in the -Z direction. Furthermore, as shown in the perspective view of Figure 8, a second recessed portion 39 is provided on the surface of the closing portion 37 of the second bearing 35 that faces the cylinder 21.

[0040] A muffler 33 is positioned in the +Z direction of the closed portion 32 of the first bearing 30. A muffler chamber 34 is formed between the muffler 33 and the first bearing 30. The muffler chamber 34 contains the high-pressure gaseous refrigerant discharged from the discharge portion 26 of the cylinder 21. The high-pressure gaseous refrigerant is discharged into the case 11 through the opening between the bearing portion 31 of the first bearing 30 and the muffler 33.

[0041] Referring to Figures 9 and 10, the operation of introducing gaseous refrigerant into the compression mechanism 20 will be described. Figure 9 is a plan view of the compression mechanism 20 as seen from the +Z direction. Figure 10 is a cross-sectional view of the shaft 15 and the compression mechanism 20 along line XX in Figure 9.

[0042] As shown in Figure 9, a discharge section 26 is provided on the surface of the first bearing 30. As shown in Figures 1 and 10, low-pressure gaseous refrigerant that has passed through the evaporator of the second heat exchanger 6 is introduced into the suction port 25 via the accumulator 2b. The cylinder 21 has a communication hole 25a that is located in the -R direction of the suction port 25 and penetrates the cylinder 21 in the Z direction. The openings at both ends of the communication hole 25a in the Z direction face the first recessed section 38 and the second recessed section 39, respectively.

[0043] The first recessed portion 38 and the second recessed portion 39 are provided with extensions 38a and 39a that extend diagonally in the -R and -θ directions in the plan view of Figure 9. Each extension 38a and 39a extends to a position that overlaps with the cylinder chamber 22. The gaseous refrigerant introduced from the accumulator 2b into the suction port 25 is divided into the first recessed portion 38 and the second recessed portion 39 located above and below the communication hole 25a in the Z direction, and flows into the interior of the cylinder chamber 22.

[0044] In this embodiment, the rotary compressor 10 and refrigeration cycle device 1 incorporate hinged vanes 41 and cylindrical parts 43 into the inner diameter of the cylinder 21. As a result, the hinged vanes 41 cause the cylindrical parts 43 to rotate integrally with the shaft 15 in synchronization. This allows the rotary compressor 10 and refrigeration cycle device 1 to keep the sliding speed of the tip of the other normal vane 17 low.

[0045] Furthermore, although the outer surface of the cylindrical part 43 slides against the inner wall surface of the cylinder, this sliding occurs between a concave and a convex surface, and because the radius R can be larger compared to the tip of a normal vane 17, it is advantageous in terms of Hertzian surface pressure. Therefore, the rotary compressor 10 and refrigeration cycle device 1 can suppress the deterioration of compression performance and provide a compressor with high overall sliding part reliability. In addition, even when surface treatment is applied to the sliding part, it is applied to the compact and lightweight cylindrical part 43 rather than the inner wall surface of the cylinder 21. As a result, sliding part reliability can be obtained at a low cost.

[0046] Furthermore, the refrigeration cycle device 1 of this embodiment includes a rotary compressor 10, one of a first heat exchanger 4 and a second heat exchanger 6 that functions as a radiator, an expansion device 5, and the other of the first heat exchanger 4 and the second heat exchanger 6 that functions as a heat absorber. The radiator is connected to the rotary compressor 10. The expansion device 5 is connected to the radiator. The heat absorber is connected to the expansion device 5. In the rotary compressor 10, the decrease in the compression performance of the refrigerant is suppressed. Therefore, according to this embodiment, a high-performance refrigeration cycle device can be provided by having a rotary compressor 10.

[0047] (Second Embodiment) The rotary compressor and refrigeration cycle device of the second embodiment will be described below with reference to Figures 11 and 12. Figure 11 is a perspective view of the cylindrical component 51 in this embodiment. Figure 12 is a plan view of the compression mechanism 50 incorporating the cylindrical component 51 in this embodiment, viewed from the +Z direction.

[0048] As shown in Figure 11, a groove 44 is formed in the inner wall of the cylindrical part 51 for engaging the hinge 42 of the hinged vane 41. Furthermore, an outer peripheral recess 52 is formed on the outer circumference of the cylindrical part 51 to reduce the contact area with the inner wall surface of the cylinder 21. The outer peripheral recess 52 forms a displacement surface that offsets the outer peripheral surface of the cylindrical part 51 inward by a specified amount.

[0049] As shown in Figure 12, the cylindrical component 51 is provided so that the outer surface of the protruding portion other than the outer recessed portion 52 can slide against the inner wall surface of the cylinder 21. The cylindrical component 51 is installed inside the cylinder 21 with the hinge 42 of the hinged vane 41 engaged with the groove 44, and the hinged vane 41 is assembled to swing around the axis of the hinge 42. The cylindrical component 51 and the hinged vane 41 can rotate integrally in synchronization with the rotor 16.

[0050] Figure 13 is a perspective view of the compression mechanism 50 of this embodiment with the first bearing 30 removed. Figure 14 is a perspective view showing a modified version of the compression mechanism relative to Figure 13. As shown in Figure 13, the cylinder 21 of the compression mechanism 50 is equipped with two vanes 17, 41. On the other hand, as shown in Figure 14, the cylinder 21 of the compression mechanism 50 can also be equipped with three vanes 17, 41 at approximately equal intervals in the θ direction of the rotor 16. Note that the number of vanes is not limited to two or three, but may be four or more.

[0051] The rotary compressor and refrigeration cycle device equipped with the cylindrical component 51 according to this embodiment can obtain the same effects as in the first embodiment. Furthermore, in this embodiment, the outer circumference of the cylindrical component 51 facing the inner wall surface of the cylinder 21 is formed with a contact surface (outer circumference surface) that contacts the inner wall surface of the cylinder 21 and an outer circumference recessed portion 52 having a displacement surface spaced apart from the inner wall surface of the cylinder 21. Therefore, according to this embodiment, sliding loss can be effectively suppressed by reducing the sliding area between the cylindrical component 51 and the cylinder 21, and a more efficient vane-type rotary compressor can be provided.

[0052] Furthermore, the surface of the cylindrical part 51 can be subjected to a surface treatment of DLC (Diamond-Like Carbon) coating and / or molybdenum disulfide shot treatment.

[0053] To improve the reliability and performance of sliding parts, surface treatments such as DLC or molybdenum disulfide shot, which offer high hardness, low friction, and low aggressiveness, can be considered. However, if surface treatment is applied to the cylinder's inner diameter, it will be necessary to deliver the finished product to a surface treatment company, which could lead to increased transportation costs. Furthermore, depending on the displacement volume, surface treatment may become difficult due to increased cylinder height and component weight, which could also lead to increased costs.

[0054] In contrast, in the rotary compressor and refrigeration cycle device of this embodiment, surface treatment is performed on the cylindrical component 51. This eliminates the need to deliver the cylinder 21 after finishing to a surface treatment company, thereby reducing transportation costs. Furthermore, according to this embodiment, by performing surface treatment on the cylindrical component 51, which is more compact and lighter than the components of the cylinder 21, improvements in performance and reliability can be obtained at a lower cost, making it possible to provide a compressor that is low cost, high performance, and highly reliable.

[0055] While several embodiments of the present invention have been described, these embodiments are presented as examples only and are not intended to limit the scope of the invention. These embodiments can be carried out in a variety of other forms, and various omissions, combinations, substitutions, and modifications are possible without departing from the spirit of the invention. These embodiments and their variations are included in the scope and spirit of the invention, as well as in the claims and their equivalents. [Explanation of symbols]

[0056] 1...Refrigeration cycle unit, 4...First heat exchanger (radiator, heat absorber), 5...Expansion device, 6...Second heat exchanger (heat absorber, heat absorber), 10...Rotary compressor, 16...Rotor, 17...Normal vane, 18...Slit, 20, 50...Compression mechanism, 21...Cylinder, 22...Cylinder chamber, 23...Small chamber, 41...Hinged vane, 42...Hinge, 43, 51...Cylindrical part, 44...Groove, 52...Outer circumference recess (recess)

Claims

1. A cylinder having a cylinder chamber, A rotor is disposed inside the cylinder chamber and has multiple slits formed on its outer circumference, The slit is arranged and consists of a normal vane and a hinged vane that move forward and backward relative to the cylinder chamber as the rotor rotates, The cylinder comprises a cylindrical part that slidably contacts the inner wall of the cylinder, The hinged vane has a hinge formed at the end that protrudes from the cylinder chamber. A rotary compressor in which a groove formed in the inner wall of the cylindrical component engages with the hinge of the hinged vane, and the cylindrical component rotates integrally with the rotor by the hinged vane.

2. The rotary compressor according to claim 1, wherein a recess is formed on the outer circumference of the cylindrical component to reduce the contact area between the outer circumference of the cylindrical component and the inner wall of the cylinder.

3. The rotary compressor according to claim 1 or 2, wherein the surface of the cylindrical component is subjected to a surface treatment of DLC coating and / or molybdenum disulfide shot treatment.

4. The rotary compressor according to claim 1 or 2, comprising one hinged vane and two conventional vanes.

5. A rotary compressor according to claim 1 or 2, A heat sink connected to the rotary compressor, An expansion device connected to the heat sink, A heat absorber connected to the expansion device, A refrigeration cycle device equipped with the following features.

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