Rotary compressor and refrigeration cycle device

Abstract

To provide a rotary compressor and a refrigeration cycle device that can restrain a decrease in reliability.SOLUTION: A rotary compressor according to an embodiment comprises a case internally housing a compression mechanism part and a lubricating oil storage part. The compression mechanism part comprises a cylinder, and an injection mechanism. The injection mechanism injects a refrigerant introduced from the outside of the case, into a cylinder chamber. The injection mechanism comprises a guide part, and a mobile body. The guide part establishes communication between the cylinder chamber and the lubricating oil storage part. The mobile body is arranged inside the guide part, and can move along a first direction in which the guide part extends. The injection mechanism injects the refrigerant into the cylinder chamber in association with movement of the mobile body.SELECTED DRAWING: Figure 3

Description

Technical Field

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

Background Art

[0002] In a refrigeration cycle apparatus, a rotary compressor that compresses a gaseous refrigerant is used. As the rotary compressor operates, the sliding portion wears out and the reliability decreases. There is a need for a rotary compressor that can suppress a decrease in reliability.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] The problem to be solved by the present invention is to provide a rotary compressor and a refrigeration cycle apparatus that can suppress a decrease in reliability.

Means for Solving the Problems

[0005] The rotary compressor according to the embodiment has a case that houses a shaft, a compression mechanism portion, and a lubricating oil reservoir portion therein. The compression mechanism portion includes an eccentric portion, a cylinder, a roller, a closing member, and an injection mechanism. The eccentric portion is provided on the shaft. The cylinder has a cylinder chamber in which the eccentric portion is disposed, and discharges the gaseous refrigerant compressed inside the cylinder chamber to the inside of the case. The roller is cylindrical, fitted onto the eccentric portion, and eccentrically rotates inside the cylinder chamber. The closing member closes the end portion of the cylinder chamber in the axial direction of the shaft. The injection mechanism injects the refrigerant introduced from the outside of the case into the cylinder chamber. The injection mechanism includes a pipe, a guide portion, an opening portion, and a moving body. The pipe introduces the refrigerant from the outside of the case. The guide portion is formed on the cylinder and communicates the cylinder chamber with the lubricating oil reservoir portion. The opening portion communicates with the pipe and opens into the guide portion. The moving body is disposed inside the guide portion and is movable along a first direction in which the guide portion extends. The tip of the moving body in a first inner direction, which is the cylinder chamber side in the first direction, abuts against the outer peripheral surface of the roller. The tip of the moving body in a first outer direction, which is the direction opposite to the first inner direction, is exposed to the lubricating oil reservoir portion. The injection mechanism injects the refrigerant into the cylinder chamber as the moving body moves. The moving body has a recess on its outer surface. The recess can communicate the opening and the cylinder chamber as the moving body moves. The opening is blocked by the moving body except when it is exposed in the recess. The moving body is a plate. The shape of the cross-section orthogonal to the first direction of the plate is rectangular with the axial direction as the longitudinal direction and the second direction orthogonal to the axial direction and the first direction as the short direction. The guide portion is formed on the end face of the cylinder on the side of the closing member and is a guide groove blocked by the closing member. The opening is formed in the closing member and opens into the guide groove. The recess is formed on the end face of the plate on the side of the closing member and penetrates in the second direction.

Brief Description of the Drawings

[0006]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Mode for Carrying Out the Invention

[0007] Hereinafter, the rotary compressor and the refrigeration cycle device of the embodiment will be described with reference to the drawings. FIG. 1 is a schematic configuration diagram of a refrigeration cycle device including a cross-sectional view of a rotary compressor according to the first embodiment.

[0008] The refrigeration cycle device 1 will be briefly described. The refrigeration cycle device 1 includes a rotary compressor 2, a radiator (for example, a condenser) 3 connected to the rotary compressor 2, an expansion device (for example, an expansion valve) 4 connected to the radiator 3, and a heat absorber (for example, an evaporator) 5 connected between the expansion device 4 and the rotary compressor 2. The refrigeration cycle device 1 contains a refrigerant such as carbon dioxide (CO2). The refrigerant circulates through the refrigerant flow path 8 of the refrigeration cycle device 1 while undergoing a phase change.

[0009] The rotary compressor 2 is a so-called rotary compressor. The rotary compressor 2 compresses the low-pressure gaseous refrigerant (fluid) taken into it to a high-temperature and high-pressure gaseous refrigerant. The specific configuration of the rotary compressor 2 will be described later.

[0010] The radiator 3 dissipates heat from the high-temperature and high-pressure gaseous refrigerant supplied from the rotary compressor 2 to convert the high-temperature and high-pressure gaseous refrigerant into a high-pressure liquid refrigerant. The expansion device 4 reduces the pressure of the high-pressure liquid refrigerant sent from the radiator 3 to convert the high-pressure liquid refrigerant into a low-temperature and low-pressure liquid refrigerant. The absorber 5 vaporizes the low-temperature and low-pressure liquid refrigerant fed from the expansion device 4 into a low-pressure gaseous refrigerant. In the absorber 5, when the low-pressure liquid 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 absorber 5 is taken into the interior of the above-described rotary compressor 2.

[0011] As described above, in the refrigeration cycle device 1 of the present embodiment, the refrigerant, which is the working fluid, circulates through the refrigerant flow path 8 while undergoing a phase change between the gaseous refrigerant and the liquid refrigerant. The refrigerant releases heat during the process of changing from the gaseous refrigerant to the liquid refrigerant, and absorbs heat during the process of changing from the liquid refrigerant to the gaseous refrigerant. Heating, cooling, etc. are performed by utilizing these heat releases and absorptions.

[0012] The rotary compressor 2 will be described. In the present application, the Z direction (axial direction) is the axial direction of the central axis of the shaft 13. The +Z direction is the direction from the compression mechanism portion 20 toward the electric motor portion 15, and the -Z direction is the opposite side of the +Z direction. For example, the Z direction is the vertical direction, and the +Z direction is vertically upward.

[0013] The rotary compressor 2 includes an accumulator 6 and a compressor main body 10. The accumulator 6 separates the refrigerant fed from the absorber 5 into a gaseous refrigerant and a liquid refrigerant. The gaseous refrigerant is taken into the compressor main body 10 through the suction pipe.

[0014] The compressor main body 10 includes a case 11, a shaft 13, an electric motor portion 15, a lubricating oil storage portion 14, a plurality of compression mechanism portions 20, and an injection mechanism 30. The case 11 is formed in a cylindrical shape with both ends closed. The case 11 houses the shaft 13, the electric motor portion 15, the lubricating oil storage portion 14, and the plurality of compression mechanism portions 20. The case 11 has a supply portion 12 at the upper end portion. The supply portion 12 supplies the gaseous refrigerant inside the case 11 to the radiator 3.

[0015] The shaft 13 is arranged along the central axis of the compressor main body 10. The shaft 13 has a plurality of eccentric portions 21. The electric motor unit 15 is arranged in the +Z direction of the shaft 13. The electric motor unit 15 has a stator 15a and a rotor 15b. The stator 15a is fixed to the inner peripheral surface of the case 11. The rotor 15b is fixed to the outer peripheral surface of the shaft 13. The electric motor unit 15 rotationally drives the shaft 13.

[0016] The lubricating oil storage part 14 is inside the case 11 and in the area outside the plurality of compression mechanism parts 20. The lubricating oil storage part 14 stores the lubricating oil for lubricating the sliding parts of the compressor main body 10. A lubricating oil flow path (not shown) is formed along the central axis from the lower end part of the shaft 13. The lubricating oil in the lubricating oil storage part 14 passes through the lubricating oil flow path as the shaft 13 rotates and is supplied to the sliding parts of the compressor main body 10.

[0017] The plurality of compression mechanism parts 20 compress the gaseous refrigerant by the rotation of the shaft 13. The plurality of compression mechanism parts 20 are arranged in the -Z direction of the shaft 13. The plurality of compression mechanism parts 20 are fixed to the frame 11a. The outer peripheral surface of the frame 11a is fixed to the inner peripheral surface of the case 11. The plurality of compression mechanism parts 20 have two compression mechanism parts 20, namely a first compression mechanism part 20A and a second compression mechanism part 20B. The first compression mechanism part 20A and the second compression mechanism part 20B are arranged side by side in this order from the +Z direction to the -Z direction. Below, the configuration of the first compression mechanism part 20A will be described as a representative. The configuration of the second compression mechanism part 20B is the same as that of the first compression mechanism part 20A except for the eccentric direction of the eccentric part 21.

[0018] The first compression mechanism part 20A has an eccentric part 21, a roller 22, and a cylinder 24. The eccentric part 21 is columnar and is integrally formed with the shaft 13. When viewed from the +Z direction, the center of the eccentric part 21 is eccentric from the central axis of the shaft 13. The roller 22 is formed in a cylindrical shape and is fitted on the outer periphery of the eccentric part 21. The roller 22 eccentrically rotates together with the eccentric part 21 inside the cylinder chamber 25.

[0019] The cylinder 24 discharges the gaseous refrigerant compressed inside the cylinder chamber 25 into the inside of the case 11. FIG. 3 is a cross-sectional view taken along line III-III of FIG. 1. As shown in FIG. 3(c), the cylinder 24 has a cylinder chamber 25, a vane 26, a suction hole 28, and a discharge hole 29 (see FIG. 1).

[0020] The cylinder chamber 25 is formed to penetrate the radial center of the cylinder 24 in the Z direction. The cylinder chamber 25 houses an eccentric portion 21 and a roller 22 inside. The vane 26 is housed in a vane groove formed in the cylinder 24 and can move forward and backward inside the cylinder chamber 25. The tip of the vane 26 is biased to contact the outer peripheral surface of the roller 22. The vane 26, together with the roller 22, partitions the inside of the cylinder chamber 25 into a suction chamber 25s and a compression chamber 25p. The suction hole 28 communicates the suction chamber 25s with the accumulator 6 shown in FIG. 1. The discharge hole 29 communicates the compression chamber 25p with the muffler chamber 19 (the first muffler chamber 19A or the second muffler chamber 19B) via a valve body 29v.

[0021] Due to the eccentric rotation of the roller 22, the volume of the suction chamber 25s increases. The gaseous refrigerant (refrigerant in the first state) is sucked into the suction chamber 25s from the accumulator 6 through the suction hole 28. Due to the eccentric rotation of the roller 22, the volume of the compression chamber 25p decreases and the gaseous refrigerant is compressed. When the gaseous refrigerant exceeds the discharge pressure, the valve body 29v is pushed open. The gaseous refrigerant is discharged from the compression chamber 25p through the discharge hole 29 into the muffler chamber 19.

[0022] As shown in FIG. 1, the rotary compressor 2 has a partition member (closing member) 16, a first bearing 17A, a second bearing 17B, a first muffler 18A, and a second muffler 18B. The partition member 16 is disposed between the first compression mechanism portion 20A and the second compression mechanism portion 20B. The partition member 16 closes the -Z direction end of the cylinder chamber 25 of the first compression mechanism portion 20A. The partition member 16 closes the +Z direction end of the cylinder chamber 25 of the second compression mechanism portion 20B.

[0023] The first bearing (main bearing) 17A is arranged in the +Z direction of the plurality of compression mechanism parts 20 and supports the shaft 13. The first bearing 17A closes the +Z-direction end of the cylinder chamber 25 of the first compression mechanism part 20A. The second bearing (auxiliary bearing) 17B is arranged in the -Z direction of the plurality of compression mechanism parts 20 and supports the shaft 13. The second bearing 17B closes the -Z-direction end of the cylinder chamber 25 of the second compression mechanism part 20B.

[0024] The first muffler 18A forms a first muffler chamber 19A between it and the first bearing 17A. The gaseous refrigerant compressed by the first compression mechanism part 20A is discharged from the discharge hole 29 into the first muffler chamber 19A. The gaseous refrigerant discharged into the first muffler chamber 19A is discharged into the inside of the case 11 from the muffler hole 19e. The second muffler 18B forms a second muffler chamber 19B between it and the second bearing 17B. The gaseous refrigerant compressed by the second compression mechanism part 20B is discharged from a discharge hole (not shown) into the second muffler chamber 19B. The second muffler chamber 19B communicates with the first muffler chamber 19A via a muffler chamber intermediate passage (not shown).

[0025] (First Embodiment) The injection mechanism 30 will be described in detail. The injection mechanism 30 intermittently injects a cooling refrigerant (refrigerant in the second state, intermediate-pressure refrigerant, liquid refrigerant) introduced from the outside of the case 11 into the cylinder chamber 25. The injection mechanism 30 includes an introduction part, a guide part 40, a moving body 50, and a biasing member 60. The guide part 40, the moving body 50, and the biasing member 60 are formed in each of the plurality of compression mechanism parts 20.

[0026] The introduction part includes a pipe 32, a shut-off valve 33, a branch flow path 34, and an opening 35 (see FIG. 2). The pipe 32 introduces the cooling refrigerant from outside the case 11. The pipe 32 branches from the refrigerant flow path 8 between the radiator 3 and the expansion device 4 of the refrigeration cycle device 1. The pipe 32 may branch from the refrigerant flow path 8 via a gas-liquid separator. The pipe 32 extends into the interior of the partition member 16 through the case 11 and the lubricating oil storage portion 14. In the refrigerant flow path 8 between the radiator 3 and the expansion device 4, a gas-liquid two-phase refrigerant that is colder than the gaseous refrigerant compressed by the compression mechanism portion 20 flows. The pipe 32 introduces this gas-liquid two-phase refrigerant into the interior of the case 11 as the cooling refrigerant. The shut-off valve 33 is installed in the pipe 32 outside the case 11. The shut-off valve 33 can shut off the introduction of the cooling refrigerant into the interior of the case 11.

[0027] Figure 2 is an enlarged view of part II of Figure 1. The branch flow path 34 extends from the tip of the pipe 32 inside the partition member 16 toward the plurality of compression mechanism portions 20 (see Figure 1). The branch flow path 34 communicates the opening 35 of the plurality of compression mechanism portions 20 with the common pipe 32. The branch flow path 34 of the first embodiment is formed in the partition member 16. The opening 35 communicates with the pipe 32 via the branch flow path 34. The opening 35 opens into the guide portion 40 described below. The opening 35 is disposed near the cylinder chamber 25 in the radial direction of the shaft 13. The opening 35 of the first embodiment is formed in the partition member 16.

[0028] The guide portion 40 is formed in the cylinder 24. The guide portion 40 communicates the cylinder chamber 25 and the lubricating oil storage portion 14. In the present application, the X direction and the Y direction are defined as follows. The X direction (first direction) is the direction in which the guide portion 40 extends. The +X direction (first inner direction) is the cylinder chamber 25 side of the guide portion 40, and the -X direction (first outer direction) is the lubricating oil storage portion 14 side of the guide portion 40. For example, the X direction is parallel to the radial direction of the shaft 13. The Y direction (second direction) is a direction orthogonal to the X direction and the Z direction. For example, the X direction and the Y direction are horizontal directions.

[0029] The guide portion 40 of the first embodiment is a guide groove 41. The guide groove 41 is formed on the end face on the side of the partition member 16 of the cylinder 24. For example, the depth of the guide groove 41 in the Z direction is about 1 / 3 of the height of the cylinder 24 in the Z direction. The opening of the guide groove 41 is blocked by the partition member 16. The aforementioned opening 35 opens into the guide groove 41.

[0030] The moving body 50 is disposed inside the guide portion 40. The moving body 50 is movable along the X direction. The tip of the moving body 50 in the +X direction abuts against the outer peripheral surface of the roller 22. The tip of the moving body 50 in the -X direction is exposed to the lubricating oil storage portion 14. The moving body 50 receives the differential pressure between the lubricating oil storage portion 14 and the cylinder chamber 25. As described above, the gaseous refrigerant compressed to the discharge pressure in the cylinder chamber 25 is discharged into the case 11. The pressure of the lubricating oil storage portion 14 accommodated inside the case 11 is equivalent to the discharge pressure. The pressure in the cylinder chamber 25 before reaching the discharge pressure is lower than the pressure of the lubricating oil storage portion 14. Due to the differential pressure between the lubricating oil storage portion 14 and the cylinder chamber 25, the moving body 50 abuts against the outer peripheral surface of the roller 22. As the roller 22 eccentrically rotates, the moving body 50 moves in the X direction.

[0031] The moving body 50 has a recess 52 on its outer surface. The recess 52 can communicate the opening 35 and the cylinder chamber 25 as the moving body 50 moves. The opening 35 is blocked by the outer surface of the moving body 50 except when it is exposed to the recess 52. Even when the moving body 50 moves most in the -X direction as the roller 22 eccentrically rotates, the opening 35 is not exposed in the +X direction of the moving body 50. The opening 35 is not exposed in the gap between the tip of the moving body 50 in the +X direction and the roller 22.

[0032] The moving body 50 of the first embodiment is a plate 51. The shape of the cross section of the plate 51 orthogonal to the X direction is a rectangular shape with the Z direction as the longitudinal direction and the Y direction as the short direction. The contact portion between the tip of the plate 51 in the +X direction and the outer peripheral surface of the roller 22 is linear or rectangular extending in the Z direction. The plate 51 may have a diamond-like carbon film on its outer surface. The recess 52 is formed on the end face of the plate 51 on the side of the partition member 16. The recess 52 is formed in the intermediate portion of the plate 51 in the X direction. The recess 52 penetrates the plate 51 in the Y direction. When viewed from the Y direction, the recess 52 has a rectangular shape. When the plate 51 moves in the +X direction with the eccentric rotation of the roller 22, both sides of the recess 52 in the Y direction open to the cylinder chamber 25.

[0033] As shown in FIG. 1, the injection mechanism 30 includes a biasing member 60 and a holding member 63 as a biasing unit. The biasing member (assist member) 60 is disposed in the -X direction of the moving body 50. The biasing member 60 biases the moving body 50 in the +X direction. At least when the moving body 50 moves to the most -X position, the biasing member 60 applies a biasing force in the +X direction to the moving body 50. The greater the amount of movement of the moving body 50 in the -X direction, the greater the biasing force in the +X direction.

[0034] As described above, due to the differential pressure between the lubricating oil storage portion 14 and the cylinder chamber 25, a force in the +X direction (hereinafter sometimes referred to as a differential pressure force) acts on the moving body 50. The pressure of the lubricating oil storage portion 14 is equivalent to the discharge pressure. When the pressure in the cylinder chamber 25 approaches the discharge pressure, the differential pressure force acting on the moving body 50 decreases. The followability of the moving body 50 with respect to the eccentric rotation of the roller 22 becomes weak. It becomes difficult to inject a predetermined amount of cooling refrigerant into the cylinder chamber 25 at a predetermined timing. By the biasing member 60 biasing the moving body 50 in the +X direction, the decrease in the differential pressure force acting on the moving body 50 is compensated.

[0035] The biasing member 60 of the first embodiment is a coil spring 61. The coil spring 61 is disposed between the -X direction end of the plate 51 and the inner peripheral surface of the case 11. As shown in FIG. 2, when the plate 51 moves in the +X direction, the +X direction end of the coil spring 61 enters the guide groove 41 formed in the cylinder 24. The width of the coil spring 61 in the Y direction is larger than the width of the guide groove 41 in the Y direction. A relief hole 62 is formed in the cylinder 24 to avoid interference with the coil spring 61. The Z direction centers 61c of the coil spring 61 and the relief hole 62 are on the opposite side of the recess 52 with the Z direction center 51c of the plate 51 interposed therebetween. Even when the plate 51 moves in the -X direction, communication between the relief hole 62 and the recess 52 is suppressed.

[0036] As shown in FIG. 1, the holding member 63 is a member separate from the compression mechanism portion 20 and is fixed to the inner surface of the case 11. The holding member 63 has a holding hole. The -X direction end of the coil spring 61 is inserted into the holding hole, and the end of the coil spring 61 is held. The end of the coil spring 61 is positioned by the holding member 63.

[0037] The operation of the injection mechanism 30 will be described. FIG. 3 is an explanatory view of the operation of the injection mechanism of the first embodiment and is a cross-sectional view taken along line III-III of FIG. 1. The plate 51 is biased in the +X direction by a coil spring (not shown). The +X direction tip of the plate 51 abuts against the outer periphery of the roller 22. From FIGS. 3(a) to (d), the roller 22 eccentrically rotates inside the cylinder chamber 25. Along with this, the plate 51 moves in the X direction along the guide groove 41.

[0038] In FIG. 3(a), compression of the gaseous refrigerant in the cylinder chamber 25 is started. The opening 35 is exposed in the recess 52 of the plate 51. The recess 52 is inside the guide groove 41 and is not exposed to the cylinder chamber 25. The opening 35 and the cylinder chamber 25 are not in communication. Cooling refrigerant is not injected from the opening 35 into the cylinder chamber 25.

[0039] In Fig. 3(b), the plate 51 moves in the +X direction. The recess 52 is exposed to the cylinder chamber 25, and the opening 35 and the cylinder chamber 25 communicate with each other. The pressure of the cooling refrigerant is greater than the pressure of the gaseous refrigerant in the cylinder chamber 25. The cooling refrigerant is injected into the cylinder chamber 25 through both sides in the Y direction of the recess 52 from the opening 35. Both sides in the Y direction of the recess 52 serve as the injection flow paths for the cooling refrigerant. The gaseous refrigerant in the cylinder chamber 25 and the compression mechanism portion 20 are cooled by the cooling refrigerant.

[0040] In Fig. 3(c), the plate 51 moves in the -X direction. The recess 52 is accommodated inside the guide groove 41 again. The communication between the opening 35 and the cylinder chamber 25 is blocked. The injection of the cooling refrigerant from the opening 35 into the cylinder chamber 25 ends. As described above, the injection mechanism 30 intermittently injects the cooling refrigerant into the cylinder chamber 25.

[0041] In Fig. 3(d), the compression of the gaseous refrigerant in the cylinder chamber 25 proceeds. The pressure of the gaseous refrigerant in the cylinder chamber 25 approaches the discharge pressure. The discharge pressure is the pressure at which the gaseous refrigerant pushes open the valve body 29v shown in Fig. 1 and is discharged into the case 11. The pressure in the lubricating oil storage portion 14 inside the case 11 is equivalent to the discharge pressure. The differential pressure acting on the plate 51 becomes small. The plate 51 is biased in the +X direction by the coil spring 61. The tip of the plate 51 in the +X direction maintains contact with the outer peripheral surface of the roller 22.

[0042] In Fig. 3(d), the plate 51 moves in the -X direction. The recess 52 of the plate 51 moves in the -X direction of the opening 35. The opening 35 is blocked by the end face of the plate 51 in the +X direction of the recess 52. The high-pressure gaseous refrigerant in the cylinder chamber 25 hardly flows into the opening 35.

[0043] As described in detail above, the rotary compressor 2 of the first embodiment has a case 11 that houses a shaft 13, a compression mechanism section 20, and a lubricating oil storage section 14 therein. The compression mechanism section 20 includes an eccentric section 21, a cylinder 24, a roller 22, a partition member 16, and an injection mechanism 30. The eccentric section 21 is provided on the shaft 13. The cylinder 24 has a cylinder chamber 25 in which the eccentric section 21 is disposed, and discharges the gaseous refrigerant compressed inside the cylinder chamber 25 into the case 11. The roller 22 has a cylindrical shape, is fitted onto the eccentric section 21, and eccentrically rotates within the cylinder chamber 25. The partition member 16 closes the end of the cylinder chamber 25 in the Z direction, which is the axial direction of the shaft 13. The injection mechanism 30 injects the cooling refrigerant introduced from outside the case 11 into the cylinder chamber 25. The injection mechanism 30 includes a pipe 32, a guide section 40, an opening 35, and a moving body 50. The pipe 32 introduces the cooling refrigerant from outside the case 11. The guide section 40 is formed in the cylinder 24 and communicates the cylinder chamber 25 with the lubricating oil storage section 14. The opening 35 communicates with the pipe 32 and opens into the guide section 40. The moving body 50 is disposed inside the guide section 40 and is movable along the X direction in which the guide section 40 extends. The tip of the moving body 50 in the +X direction, which is the cylinder chamber 25 side in the X direction, abuts against the outer peripheral surface of the roller 22. The tip of the moving body 50 in the -X direction, which is the opposite direction of the +X direction, is exposed to the lubricating oil storage section 14. The injection mechanism 30 injects the cooling refrigerant into the cylinder chamber 25 as the moving body 50 moves.

[0044] The guide section 40 communicates the cylinder chamber 25 with the lubricating oil storage section 14. The moving body 50 is disposed inside the guide section 40. Due to the differential pressure between the lubricating oil storage section 14 and the cylinder chamber 25, lubricating oil is supplied to the sliding portion between the guide section 40 and the moving body 50. Wear of the sliding portion is suppressed, and a decrease in the reliability of the rotary compressor 2 is suppressed. Due to the differential pressure between the lubricating oil storage section 14 and the cylinder chamber 25, the moving body 50 abuts against the outer peripheral surface of the roller 22. The moving body 50 moves following the eccentric rotation of the roller 22. A predetermined amount of the cooling refrigerant is injected into the cylinder chamber 25 at a predetermined timing.

[0045] The moving body 50 has a recess 52 on its outer surface. The recess 52 can communicate the opening 35 and the cylinder chamber 25 as the moving body 50 moves. The opening 35 is blocked by the moving body 50 except when it is exposed to the recess 52. The opening 35 is not exposed in the gap between the tip of the moving body 50 in the +X direction and the roller 22. There is lubricating oil in the sliding part between the tip of the moving body 50 in the +X direction and the outer peripheral surface of the roller 22. It is difficult for the lubricating oil in the sliding part to be removed by the cooling refrigerant injected from the opening 35. Wear of the sliding part is suppressed, and a decrease in the reliability of the rotary compressor 2 is suppressed. The opening 35 is not exposed in the +X direction of the moving body 50. It is difficult for the high-pressure gas refrigerant in the cylinder chamber 25 to flow into the opening 35. A decrease in the compression performance of the compression mechanism part 20 is suppressed.

[0046] The moving body 50 is a plate 51. The shape of the cross-section of the plate 51 orthogonal to the X direction is a rectangular shape with the Z direction as the longitudinal direction and the Y direction orthogonal to the Z direction and the X direction as the short-side direction. At the sliding part between the tip of the plate 51 in the +X direction and the outer peripheral surface of the roller 22, the contact area between the two increases and the surface pressure decreases. Wear of the sliding part is suppressed, and a decrease in the reliability of the rotary compressor 2 is suppressed.

[0047] The guide part 40 is a guide groove 41. The guide groove 41 is formed on the end surface of the cylinder 24 on the side of the partition member 16 and is blocked by the partition member 16. The opening 35 is formed in the partition member 16 and opens into the guide groove 41. The recess 52 is formed on the end surface of the plate 51 on the side of the partition member 16 and penetrates in the Y direction. The shape of the recess 52 is simple and the machining of the recess 52 is easy. Since the recess 52 penetrates in the Y direction, when the recess 52 communicates the opening 35 and the cylinder chamber 25, both sides of the recess 52 in the Y direction become injection channels for the cooling refrigerant. The cross-sectional area of the injection channel increases, and a sufficient amount of the cooling refrigerant is injected into the cylinder chamber 25.

[0048] The injection mechanism 30 has a coil spring 61 that biases the plate 51 in the +X direction. The center 61c of the coil spring 61 in the Z direction is on the opposite side of the recess 52 with the center 51c of the plate 51 in the Z direction interposed therebetween. A relief hole 62 for avoiding interference with the coil spring 61 is formed in the cylinder 24. Even when the plate 51 moves in the -X direction, the communication between the relief hole 62 and the recess 52 is suppressed. The design freedom of the coil spring 61 and the recess 52 is increased. The plate 51 may be misfitted into the guide groove 41 with the top and bottom reversed. In this case, since the position of the coil spring 61 is displaced from the position of the relief hole 62, the coil spring 61 cannot be mounted. Therefore, misfitting of the plate 51 is suppressed.

[0049] The injection mechanism 30 has a holding member 63. The holding member 63 is fixed to the case 11 and holds the end of the coil spring 61 on the side opposite to the plate 51. Since the holding member 63, which is a separate member from the compression mechanism portion 20, holds the end of the coil spring 61, an increase in the size of the compression mechanism portion 20 is suppressed. The design freedom of the end position of the coil spring 61 is increased.

[0050] A plurality of compression mechanism portions 20 are arranged side by side in the Z direction. The injection mechanism 30 has a branch flow path 34. The branch flow path 34 communicates the common pipe 32 with the openings 35 of the plurality of compression mechanism portions 20. There is no need to provide a pipe 32 for each of the plurality of compression mechanism portions 20. The cost of the rotary compressor 2 is suppressed.

[0051] The refrigeration cycle device 1 of the first embodiment has the aforementioned rotary compressor 2, a radiator 3, an expansion device 4, and an absorber 5. The radiator 3 is connected to the rotary compressor 2. The expansion device 4 is connected to the radiator 3. The absorber 5 is connected between the expansion device 4 and the rotary compressor 2. Since it has the aforementioned rotary compressor 2, a decrease in the reliability of the refrigeration cycle device 1 is suppressed.

[0052] In the first embodiment, the guide groove 41 is formed on the end face of the cylinder 24 on the side of the partition member 16 and is closed by the partition member 16. In contrast, the guide groove 41 may be formed on the end face of the cylinder 24 on the side of the bearing 17 (the first bearing 17A or the second bearing 17B) and be closed by the bearing 17. At this time, the opening 35 that opens into the guide groove 41 is formed in the cylinder 24 or the bearing 17.

[0053] (Second Embodiment) The rotary compressor 2 of the second embodiment will be described. FIG. 4 is a cross-sectional view of the rotary compressor of the second embodiment. FIG. 5 is an enlarged view of part V in FIG. 4. The second embodiment is different from the first embodiment in that the guide portion 40 is the guide hole 46 and the moving body 50 is the rod 56. The description of the second embodiment regarding the points that are the same as those of the first embodiment may be omitted.

[0054] The guide portion 40 of the second embodiment is the guide hole 46. The guide hole 46 is formed in the cylinder 24. The central axis of the guide hole 46 is parallel to the X direction. The shape of the cross-section of the guide hole 46 perpendicular to the X direction is circular. The guide hole 46 is arranged closer to the partition member 16 than the center of the cylinder 24 in the Z direction. As shown in FIG. 5, the branch flow path 34 is formed in the partition member 16 and the cylinder 24. The opening 35 is formed in the cylinder 24 and opens into the guide hole 46.

[0055] The moving body 50 of the second embodiment is the rod 56. The rod 56 has a cylindrical shape and is axisymmetric. The rod 56 is arranged inside the guide hole 46. The rod 56 has a diamond-like carbon film (HV0.025 is about 2500) on its outer peripheral surface. Since the friction coefficient of the diamond-like carbon film is small, wear of the sliding portion between the rod 56 and the guide hole 46 is suppressed. The rod 56 receives a differential pressure in the +X direction. The tip of the rod 56 in the +X direction abuts against the outer peripheral surface of the roller 22. The rod 56 moves in the X direction as the roller 22 eccentrically rotates.

[0056] The recess 57 is formed over the entire circumference of the outer peripheral surface of the rod 56. The depth of the recess 57 is the same over the entire circumference of the rod 56. The diameter of the rod 56 in the formation region of the recess 57 is smaller than the diameter of the rod 56 in the non-formation region of the recess 57. The recess 57 is formed by a lathe process or the like. The recess 52 is formed in the intermediate portion of the rod 56 in the X direction.

[0057] FIG. 6 is an explanatory view of the operation of the injection mechanism and is a cross-sectional view taken along line VI-VI of FIG. 4. In FIG. 6(c), the +X direction end portion of the recess 57 is at the +X direction end portion of the guide hole 46. At this time, the length L2 of the fitting portion between the rod 56 and the guide hole 46 in the -X direction from the recess 57 is longer than the length L1 of the recess 57 in the X direction. The fitting clearance between the inner portion 58 of the rod 56 in the +X direction from the recess 57 and the guide hole 46 is larger than the fitting clearance between the outer portion 59 of the rod 56 in the -X direction from the recess 57 and the guide hole 46.

[0058] The operation of the injection mechanism 30 will be described. FIG. 6(a) corresponds to FIG. 3(a). The opening 35 is exposed to the recess 57 of the rod 56. The recess 57 is inside the guide hole 46 and is not exposed to the cylinder chamber 25. The opening 35 and the cylinder chamber 25 are not in communication. The cooling refrigerant is not injected from the opening 35 into the cylinder chamber 25. FIG. 6(b) corresponds to FIG. 3(b). The rod 56 moves in the +X direction. The recess 57 is exposed to the cylinder chamber 25, and the opening 35 and the cylinder chamber 25 are in communication. The cooling refrigerant is injected from the opening 35 through the recess 57 into the cylinder chamber 25. The recess 57 is a part of the injection flow path of the cooling refrigerant.

[0059] FIG. 6(c) corresponds to FIG. 3(c). The rod 56 moves in the -X direction. The recess 57 is again housed inside the guide hole 46. The communication between the opening 35 and the cylinder chamber 25 is blocked. The injection of the cooling refrigerant from the opening 35 into the cylinder chamber 25 ends. FIG. 6(d) corresponds to FIG. 3(d). The rod 56 moves in the -X direction. The recess 57 of the rod 56 moves in the -X direction of the opening 35. The opening 35 is closed by the outer peripheral surface of the inner portion 58 of the rod 56 in the +X direction of the recess 57. The high-pressure gas refrigerant in the cylinder chamber 25 hardly flows into the opening 35.

[0060] As described in detail above, in the rotary compressor 2 of the second embodiment, the guide portion 40 is the guide hole 46 formed in the cylinder 24. The opening 35 is formed in the cylinder 24 and opens to the guide hole 46. The moving body 50 is the rod 56. The recess 57 is formed on the outer surface of the rod 56. Since the recess 57 is formed on the outer surface of the rod 56, the recess 57 is easy to process.

[0061] The rod 56 has a cylindrical shape. The recess 57 is formed over the entire circumference of the rod 56. The recess 57 is extremely easy to process. Since the recess 57, which is a part of the injection flow path, is formed over the entire circumference, the flow path cross-sectional area of the injection flow path increases. A sufficient amount of cooling refrigerant is injected into the cylinder chamber 25.

[0062] As shown in FIG. 6(c), when the end portion of the recess 57 in the +X direction is at the end portion of the guide hole 46 in the +X direction, the length L2 of the fitting portion between the rod 56 and the guide hole 46 in the -X direction from the recess 57 is longer than the length L1 of the recess 57 in the X direction. Since the fitting portion between the rod 56 and the guide hole 46 is long, the inclination of the rod 56 with respect to the guide hole 46 is suppressed. When the end portion of the recess 57 in the +X direction enters the guide hole 46, the wear of the rod 56 and the guide hole 46 is suppressed. The decrease in the reliability of the rotary compressor 2 is suppressed.

[0063] The fitting gap between the inner portion 58 of the rod 56 in the +X direction from the recess 57 and the guide hole 46 is larger than the fitting gap between the outer portion 59 of the rod 56 in the -X direction from the recess 57 and the guide hole 46. Since the fitting gap between the outer portion 59 of the rod 56 and the guide hole 46 is small, the inclination of the rod 56 with respect to the guide hole 46 is suppressed. Since the fitting gap between the inner portion 58 of the rod 56 and the guide hole 46 is large, wear of the inner portion 58 of the rod 56 and the guide hole 46 is suppressed. A decrease in the reliability of the rotary compressor 2 is suppressed.

[0064] The rod 56 has a diamond-like carbon film on its outer surface. The friction coefficient of the sliding portion between the rod 56 and the guide hole 46 is reduced. Wear of the sliding portion is suppressed, and a decrease in the reliability of the rotary compressor 2 is suppressed.

[0065] (First Modified Example) The rotary compressor 2 of the first modified example of the second embodiment will be described. FIG. 7 is a cross-sectional view of the rotary compressor 2 of the first modified example. FIG. 8 is an enlarged view of the VIII-VIII portion of FIG. 7. The first modified example is different from the second embodiment in that it has a first leaf spring 65 as the biasing member 60. The description of the first modified example for the points that are the same as those of the second embodiment may be omitted.

[0066] The biasing member 60 of the first modified example is the first leaf spring 65. The first leaf spring 65 has a U shape. The first leaf spring 65 is a cantilever leaf spring. The first leaf spring 65 is fixed to one of the rod 56 and the case 11 and not fixed to the other. In the first modified example, the +X direction end of the first leaf spring 65 is fixed to the -X direction end of the rod 56. The -X direction end of the first leaf spring 65 is not fixed to any member including the case 11.

[0067] The operation of the injection mechanism 30 will be described. FIG. 9 is an explanatory view of the operation of the injection mechanism of the first modified example and is a cross-sectional view taken along the IX-IX line of FIG. 7. FIGS. 9(a) to (c) correspond to FIGS. 6(a) to (c). Since the rod 56 is in the +X direction, the -X direction end of the first leaf spring 65 is separated from the case 11.

[0068] Figure 9(d) corresponds to Figure 6(d). The pressure of the gaseous refrigerant in the cylinder chamber 25 approaches the discharge pressure. The differential pressure acting in the +X direction on the rod 56 decreases. As the roller 22 rotates eccentrically, the rod 56 moves in the -X direction. An inertial force in the -X direction acts on the rod 56. The -X direction end of the first leaf spring 65 abuts against the case 11.

[0069] In Figure 9(e), the tip of the roller 22 in the eccentric direction reaches the position of the rod 56. The rod 56 moves further in the -X direction. The first leaf spring 65 is compressed by the case 11. A biasing force in the +X direction acts on the rod 56 from the first leaf spring 65. The decrease in the differential pressure acting in the +X direction on the rod 56 is compensated for by the biasing force of the first leaf spring 65. The followability of the rod 56 with respect to the eccentric rotation of the roller 22 is maintained.

[0070] In Figure 9(f), the roller 22 passes by the rod 56. The rod 56 moves in the +X direction. The compression of the first leaf spring 65 by the case 11 is released. The biasing force in the +X direction acting on the rod 56 from the first leaf spring 65 is eliminated. The +X direction tip of the rod 56 is exposed to the suction chamber 25s of the cylinder chamber 25. The pressure in the suction chamber 25s is low. The differential pressure acting in the +X direction on the rod 56 increases. The followability of the rod 56 with respect to the eccentric rotation of the roller 22 is maintained.

[0071] As described in detail above, in the first modification, the first leaf spring 65 is fixed to one of the rod 56 and the case 11 and not fixed to the other. The first leaf spring 65 intermittently contacts the other member to apply a force in the +X direction to the rod 56. Even when the amount of movement of the rod 56 in the X direction is large, it is not necessary to increase the deflection amount of the first leaf spring 65. The first leaf spring 65 is miniaturized.

[0072] (Second Modification) The rotary compressor 2 of the second modification of the second embodiment will be described. FIG. 10 is an explanatory view of an injection mechanism according to a second modification of the second embodiment, and is a cross-sectional view of a portion corresponding to line IX-IX in FIG. 7. The second modification is different from the second embodiment in that it has a second leaf spring 66 as a biasing member 60. The description of the second modification regarding the points that are the same as those of the second embodiment may be omitted.

[0073] The biasing member 60 of the second modification is the second leaf spring 66. The second leaf spring 66 has a U shape. The second leaf spring 66 is a leaf spring supported at both ends. In the second modification, one end of the second leaf spring 66 is fixed to the rod 56, and the other end is fixed to the cylinder 24. The other end of the second leaf spring 66 may be fixed to the case 11.

[0074] The operation of the injection mechanism 30 will be described. FIG. 10(a) corresponds to FIG. 9(b). The rod 56 is in the +X direction. The differential pressure force in the +X direction acting on the rod 56 is large. The rod 56 moves in the X direction following the eccentric rotation of the roller 22.

[0075] FIG. 10(b) corresponds to FIG. 9(e). The pressure of the gaseous refrigerant in the cylinder chamber 25 approaches the discharge pressure. The differential pressure force in the +X direction acting on the rod 56 becomes small. The tip of the roller 22 in the eccentric direction reaches the position of the rod 56. The rod 56 moves most in the -X direction, but the rod 56 and the second leaf spring 66 do not contact the case 11. The distance in the X direction between one end and the other end of the second leaf spring 66 widens. A biasing force in the +X direction acts on the rod 56 from the second leaf spring 66. The decrease in the differential pressure force in the +X direction acting on the rod 56 is compensated by the biasing force of the second leaf spring 66. The followability of the rod 56 with respect to the eccentric rotation of the roller 22 is maintained.

[0076] As described in detail above, in the second modification, one end of the second leaf spring 66 is fixed to the rod 56, and the other end is fixed to the cylinder 24. Since the rod 56 and the second leaf spring 66 are positioned with respect to the cylinder 24, the accuracy of the rotary compressor 2 is improved. Since the second leaf spring 66 does not contact other members, the generation of noise is suppressed.

[0077] (Third Modified Example) The rotary compressor 2 according to the third modified example of the second embodiment will be described. FIG. 11 is an explanatory view of an injection mechanism according to the third modified example of the second embodiment. The third modified example is different from the second embodiment in that it has a first magnet 67 and a second magnet 68 as biasing members 60. The description of the third modified example for the points that are the same as those of the second embodiment may be omitted.

[0078] The biasing member 60 of the third modified example is the first magnet 67 and the second magnet 68. The first magnet 67 is attached to the -X direction end of the rod 56. The second magnet 68 is attached to the inner peripheral surface of the case 11 in the -X direction of the rod 56. The -X direction of the first magnet 67 and the +X direction of the second magnet 68 are both polarized to the N pole or both to the S pole. The first magnet 67 and the second magnet 68 act on each other with a repulsive force.

[0079] The rod 56 is formed of a non-magnetic material. For example, the non-magnetic material is austenitic stainless steel (such as SUS304). Since the rod 56 is difficult to be magnetized by the first magnet 67, the adhesion of iron powder or the like to the rod 56 is suppressed.

[0080] The operation of the injection mechanism 30 will be described. FIG. 11 corresponds to FIG. 9(e). The pressure of the gaseous refrigerant in the cylinder chamber 25 approaches the discharge pressure. The differential pressure force in the +X direction acting on the rod 56 becomes small. The tip of the roller 22 in the eccentric direction reaches the position of the rod 56. The rod 56 moves most in the -X direction, but the first magnet 67 does not contact the second magnet 68. The X-direction interval between the first magnet 67 and the second magnet 68 becomes narrow. A repulsive force in the +X direction acts on the first magnet 67 from the second magnet 68. The decrease in the differential pressure force in the +X direction acting on the rod 56 is compensated by the repulsive force of the magnet. The followability of the rod 56 with respect to the eccentric rotation of the roller 22 is maintained.

[0081] As described in detail above, in the third modification example, the rod 56 has the first magnet 67 at the end in the -X direction. The injection mechanism 30 has the second magnet 68 that applies a force in the +X direction to the first magnet 67 in the -X direction of the first magnet 67. The second magnet 68 is non-contact with the first magnet 67 and applies a force in the +X direction to the first magnet 67 and the rod 56. Generation of noise is suppressed.

[0082] The rod 56 is formed of a non-magnetic material. Since the rod 56 is hardly magnetized by the first magnet 67, adhesion of iron powder or the like to the rod 56 is suppressed. Wear of the rod 56 and the guide hole 46 is suppressed, and a decrease in the reliability of the rotary compressor is suppressed.

[0083] The biasing member 60 of the first to third modification examples described above is attached to the rod 56 of the second embodiment. Instead of the coil spring 61 attached to the plate 51 of the first embodiment, the biasing member 60 of the first to third modification examples may be attached.

[0084] In the above-described embodiment, the pipe 32 of the injection mechanism 30 extends into the partition member 16 through the case 11. On the other hand, the pipe 32 may extend into the cylinder 24 through the case 11.

[0085] In the above-described embodiment, the rotary compressor 2 has two compression mechanism parts 20 (the first compression mechanism part 20A and the second compression mechanism part 20B). On the other hand, the rotary compressor 2 may have only one compression mechanism part 20, or may have three or more compression mechanism parts 20.

[0086] In the above-described embodiment, the rotary compressor 2 is a so-called rotary type compressor in which the vane 26 and the roller 22 shown in FIG. 3(c) are separate bodies. On the other hand, the rotary compressor 2 may be a so-called swing type compressor in which the vane and the roller are integrated.

[0087] According to at least one embodiment described above, the injection mechanism 30 has a guide part 40 and a moving body 50. The guide part 40 communicates the cylinder chamber 25 with the lubricating oil storage part 14. The moving body 50 is disposed inside the guide part 40. The injection mechanism 30 injects a cooling refrigerant into the cylinder chamber 25 as the moving body 50 moves. Thereby, a decrease in the reliability of the rotary compressor 2 can be suppressed. In addition, in the above-described embodiment, the rotary compressor that cools the compression mechanism part by injecting a liquid refrigerant has been described, but a rotary compressor that injects an intermediate-pressure gas refrigerant may also be used. Thereby, it is possible to obtain a rotary compressor that suppresses a decrease in reliability, improves energy saving performance, and increases heating and cooling capacity.

[0088] Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are also included in the invention described in the claims and the equivalent scope thereof.

Description of Reference Numerals

[0089] 1... Refrigeration cycle device, 2... Rotary compressor, 3... Radiator, 4... Expansion device, 5... Heat absorber, 11... Case, 13... Shaft, 14... Lubricating oil storage part, 16... Partition member (closing member), 20... Compression mechanism part, 20A... First compression mechanism part, 20B... Second compression mechanism part, 21... Eccentric part, 22... Roller, 24... Cylinder, 25... Cylinder chamber, 30... Injection mechanism, 32... Pipe, 34... Branch flow path, 35... Opening, 40... Guide part, 41... Guide groove, 46... Guide hole, 50... Moving body, 51... Plate, 52... Recess, 56... Rod, 57... Recess, 58... Inner part, 59... Outer part, 60... Biasing member, 61... Coil spring, 63... Holding member, 67... First magnet, 68... Second magnet.

Claims

1. A case that houses a shaft, a compression mechanism section, and a lubricating oil storage section inside, The compression mechanism section An eccentric portion provided on the shaft, A cylinder having a cylinder chamber in which the eccentric portion is disposed, and discharging the gas refrigerant compressed inside the cylinder chamber to the inside of the case, A roller that is cylindrical, fitted to the eccentric portion, and eccentrically rotates inside the cylinder chamber, A closing member that closes an end portion of the cylinder chamber in the axial direction of the shaft, An injection mechanism that injects the refrigerant introduced from the outside of the case into the cylinder chamber, The injection mechanism A pipe that introduces the refrigerant from the outside of the case, A guide portion formed in the cylinder, communicating the cylinder chamber and the lubricating oil storage section, An opening that communicates with the pipe and opens to the guide portion, A moving body that is disposed inside the guide portion, is movable along a first direction in which the guide portion extends, a tip end in a first inner direction on the cylinder chamber side in the first direction abuts against an outer peripheral surface of the roller, and a tip end in a first outer direction opposite to the first inner direction is exposed to the lubricating oil storage section, The injection mechanism injects the refrigerant into the cylinder chamber as the moving body moves, The moving body has a recess on an outer surface, The recess can communicate the opening and the cylinder chamber as the moving body moves, The opening is closed by the moving body except when it is exposed to the recess, The moving body is a plate, The shape of a cross section of the plate orthogonal to the first direction is a rectangular shape having the axial direction as a longitudinal direction and a second direction orthogonal to the axial direction and the first direction as a short direction, The guide portion is a guide groove formed on the end surface of the cylinder on the side of the closing member and closed by the closing member. The opening is formed in the closing member and opens into the guide groove. The recess is formed on the end surface of the plate on the side of the closing member and penetrates in the second direction. Rotary compressor.

2. The injection mechanism has a biasing member that biases the plate in the first inward direction. The axial center of the biasing member is on the opposite side of the recess with the axial center of the plate interposed therebetween. The rotary compressor according to claim 1.

3. The injection mechanism has a holding member that is fixed to the case and holds the end of the biasing member on the side opposite to the plate. The rotary compressor according to claim 2.

4. The moving body has a diamond-like carbon film on its outer surface. The rotary compressor according to any one of claims 1 to 3.

5. The moving body has a first magnet at its end in the first outward direction. The injection mechanism has a second magnet that applies a force in the first inward direction to the first magnet in the first outward direction of the first magnet. The rotary compressor according to any one of claims 1 to 4.

6. The moving body is formed of a non-magnetic material. The rotary compressor according to claim 5.

7. A plurality of the compression mechanism portions are arranged side by side in the axial direction. The injection mechanism has a branch flow path that communicates with a common pipe of the openings of the plurality of compression mechanism portions. The rotary compressor according to any one of claims 1 to 6.

8. A rotary compressor according to any one of claims 1 to 7, a radiator connected to the rotary compressor, an expansion device connected to the radiator, and a heat absorber connected between the expansion device and the rotary compressor. A refrigeration cycle device.

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