Rotary compressor and refrigeration cycle device

Abstract

To provide a rotary compressor capable of improving a compression performance and a refrigeration cycle device.SOLUTION: A rotary compressor includes a case having a shaft and a compression mechanism part accommodated therein. The compression mechanism part includes an eccentric part, a cylinder, a roller, a blade, a closing member and a filling port. The cylinder includes a cylinder chamber in which the eccentric part is disposed. The roller has a cylindrical shape, is fitted to the eccentric part and eccentrically rotates in the cylinder chamber. The blade moves forwards / backwards along with the eccentric rotation of the roller and divides the cylinder chamber into a suction chamber and a compression chamber of a gas refrigerant. The closing member closes an end of the cylinder chamber in the axial direction of the shaft. The filling port is formed in the closing member, opened in the cylinder chamber and used for filling a cooling refrigerant introduced from outside of the case in the cylinder chamber. The filling port is opened / closed by end surfaces on the closing member side of the roller and the blade.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] An embodiment of the present invention relates to a rotary compressor and a refrigeration cycle device. [Background technology]

[0002] In a refrigeration cycle device, a rotary compressor is used to compress a gas refrigerant. An injection circuit that injects a cooling refrigerant into a cylinder chamber of the rotary compressor has been proposed. The rotary compressor is required to have improved compression performance. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2000-170678 A Summary of the Invention [Problem to be solved by the invention]

[0004] An object of the present invention is to provide a rotary compressor and a refrigeration cycle device capable of improving compression performance. [Means for solving the problem]

[0005] A rotary compressor according to an embodiment has a case that houses a shaft and a compression mechanism. The compression mechanism has an eccentric part, a cylinder, a roller, a blade, a blocking member, and an inlet. The eccentric part is provided on the shaft. The cylinder has a cylinder chamber in which the eccentric part is disposed. The roller is cylindrical, is fitted into the eccentric part, and rotates eccentrically within the cylinder chamber. The blade moves back and forth with the eccentric rotation of the roller, and divides the cylinder chamber into a gas refrigerant suction chamber and a compression chamber. The blocking member blocks an end of the cylinder chamber in the axial direction of the shaft. The inlet is formed in the blocking member and opens into the cylinder chamber, and injects a cooling refrigerant introduced from outside the case into the cylinder chamber. The inlet is opened and closed by end faces of the roller and the blade on the blocking member side. The blade is separate from the roller and can move in a first direction along a blade groove formed in the cylinder, with the tip on the cylinder chamber side in the first direction abutting the outer circumferential surface of the roller. The injection port is formed in the region of the blocking member where it slides with the blade, closer to the compression chamber than the center in the axial direction and in a second direction perpendicular to the first direction. The injection port opens into the cylinder chamber between the tip of the blade on the cylinder chamber side and the outer circumferential surface of the roller. The injection port is an opening of a first recess formed in the blocking member. The blade has a second recess in its end face on the blocking member side that can communicate with the first recess. [Brief description of the drawings]

[0006] [Figure 1] 1 is a schematic configuration diagram of a refrigeration cycle device including a cross-sectional view of a rotary compressor of a first embodiment. [Diagram 2] FIG. 4 is an explanatory diagram of the operation of the injection circuit according to the first embodiment. [Diagram 3] 13 is a graph showing the relationship between the eccentric rotation angle of the roller and the opening area ratio of the injection port. [Figure 4] 5 is a graph showing the relationship between the pressure of the cooling refrigerant in the injection circuit and the pressure in the compression chamber. [Diagram 5] FIG. 11 is an explanatory diagram of the operation of the injection circuit according to the second embodiment. [Figure 6] FIG. 11 is a partial cross-sectional view of a rotary compressor according to a third embodiment. [Figure 7] FIG. 11 is an explanatory diagram of the operation of the injection circuit according to the third embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0007] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a rotary compressor and a refrigeration cycle device according to embodiments 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 a first embodiment.

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

[0009] The rotary compressor 2 compresses a low-pressure gas refrigerant (fluid) taken in, to produce a high-temperature, high-pressure gas refrigerant. A specific configuration of the rotary compressor 2 will be described later.

[0010] The radiator 3 radiates heat from the high-temperature, high-pressure gas refrigerant supplied from the rotary compressor 2, and converts the high-temperature, high-pressure gas 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, and converts the high-pressure liquid refrigerant into a low-temperature, low-pressure liquid refrigerant. The heat absorber 5 vaporizes the low-temperature, low-pressure liquid refrigerant sent from the expansion device 4, turning it into a low-pressure gaseous refrigerant. When the low-pressure liquid refrigerant vaporizes in the heat absorber 5, it absorbs heat of vaporization from the surroundings, thereby cooling the surroundings. The low-pressure gaseous refrigerant that has passed through the heat absorber 5 is taken into the rotary compressor 2 described above.

[0011] In this manner, in the refrigeration cycle device 1 of the present embodiment, the refrigerant, which is a working fluid, circulates through the refrigerant flow passage 8 while changing phase between a gas refrigerant and a liquid refrigerant. The refrigerant releases heat during the phase change from a gas refrigerant to a liquid refrigerant, and absorbs heat during the phase change from a liquid refrigerant to a gas refrigerant. These heat releases and absorptions are used for heating, cooling, and the like.

[0012] (First embodiment) A rotary compressor 2 according to a first embodiment will be described. The rotary compressor 2 according to the first embodiment is a so-called swing type rotary compressor 2 in which the blades 40 and the rollers 22 are integrated.

[0013] 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 unit 20 toward the electric motor unit 15, and the -Z direction is the opposite side to the +Z direction. For example, the Z direction is the vertical direction, and the +Z direction is vertically upward.

[0014] The rotary compressor 2 has an accumulator 6 and a compressor body 10. The accumulator 6 separates the refrigerant sent from the heat absorber 5 into a gas refrigerant and a liquid refrigerant. The gas refrigerant is taken into the compressor body 10 through a suction pipe.

[0015] The compressor body 10 has a case 11 , a shaft 13 , an electric motor section 15 , a lubricant oil reservoir section 14 , a plurality of compression mechanism sections 20 , and an injection circuit 30 . The case 11 is formed in a cylindrical shape with both ends closed. The case 11 houses a shaft 13, an electric motor unit 15, a lubricating oil storage unit 14, and a plurality of compression mechanisms 20. The case 11 has a supply unit 12 at an upper end. The supply unit 12 supplies the gas refrigerant inside the case 11 to the radiator 3.

[0016] The shaft 13 is disposed along the central axis of the compressor body 10. The shaft 13 has a plurality of eccentric portions 21. The electric motor unit 15 is disposed 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 circumferential surface of the case 11. The rotor 15b is fixed to the outer circumferential surface of the shaft 13. The electric motor unit 15 drives the shaft 13 to rotate.

[0017] The lubricating oil reservoir 14 is an area inside the case 11 and outside the multiple compression mechanism parts 20. The lubricating oil reservoir 14 stores lubricating oil that lubricates the sliding parts of the compressor body 10. A lubricating oil flow path (not shown) is formed along the central axis from the lower end of the shaft 13. The lubricating oil in the lubricating oil reservoir 14 passes through the lubricating oil flow path as the shaft 13 rotates, and is supplied to the sliding parts of the compressor body 10.

[0018] The multiple compression mechanism parts 20 compress the gas refrigerant by the rotation of the shaft 13. The multiple compression mechanism parts 20 are arranged in the -Z direction of the shaft 13. The multiple 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 multiple compression mechanism parts 20 include two compression mechanism parts 20, 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. The configuration of the first compression mechanism part 20A will be described below 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.

[0019] The first compression mechanism section 20A has an eccentric section 21, a roller 22, a blade 40, and a cylinder 24. The eccentric portion 21 has a cylindrical shape and is formed integrally with the shaft 13. The center of the eccentric portion 21 is eccentric from the central axis of the shaft 13 when viewed from the +Z direction. The roller 22 is formed in a cylindrical shape and is fitted onto the outer periphery of the eccentric portion 21. The roller 22 eccentrically rotates together with the eccentric portion 21 inside the cylinder chamber 25.

[0020] FIG. 2 is a cross-sectional view taken along line II-II in FIG. As shown in FIG. 2(a), the blade 40 is formed integrally with the roller 22. The blade 40 has a flat plate shape. The blade 40 extends from the outer circumferential surface of the roller 22 to the outside in the radial direction of the roller 22. The cylinder 24 has a blade accommodation hole 41. The pair of blade accommodation holes 41 are aligned in the radial direction of the shaft 13 and have a back pressure space 42a and a bush groove 42b formed in a mutually connected state, and a throat portion 43 is formed between the back pressure space 42a and the bush groove 42b. A pair of approximately semicircular bushes 42c are fitted into the bush groove 42b. The pair of bushes 42c are configured to oscillate around the axis of the bush groove 42b. The back pressure space 42a is formed in an approximately circular shape. The blade 40 is accommodated between the pair of bushes 42c so as to be able to advance and retreat as the roller 22 rotates.

[0021] In the present application, the X direction (first direction) and the Y direction (second direction) are defined as follows. In a plane perpendicular to the Z direction, a line connecting the center of the shaft 13 and the center of the throat 43 (or the blade housing hole 41) is defined as a reference line 44. The X direction is a direction parallel to the reference line 44. The +X direction is a direction from the center of the throat 43 toward the center of the shaft 13. The Y direction is a direction perpendicular to the Z and X directions.

[0022] The cylinder 24 discharges the gas refrigerant compressed inside the cylinder chamber 25 into the inside of the case 11. The cylinder 24 has a cylinder chamber 25, a suction hole 28, and a discharge hole 29 (see FIG. 1).

[0023] The cylinder chamber 25 is formed penetrating the center of the cylinder 24 in the radial direction in the Z direction. The cylinder chamber 25 accommodates the eccentric portion 21, the roller 22, and the blade 40 therein. As shown in FIG. 2(d), the blade 40, together with the roller 22, divides 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 is formed in the bearing 17 (the first bearing 17A or the second bearing 17B). 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 the valve body 29v.

[0024] The eccentric rotation of roller 22 increases the volume of suction chamber 25s. Gas refrigerant (refrigerant in the first state) is sucked from accumulator 6 through suction hole 28 into suction chamber 25s. The eccentric rotation of roller 22 reduces the volume of compression chamber 25p, compressing the gas refrigerant. When the gas refrigerant exceeds the discharge pressure, valve body 29v is pushed open. The gas refrigerant is discharged from compression chamber 25p through discharge hole 29 into muffler chamber 19.

[0025] As shown in FIG. 1, the rotary compressor 2 includes a partition member (blocking 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.

[0026] The first bearing (main bearing) 17A is disposed in the +Z direction of the multiple compression mechanism sections 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 section 20A. The second bearing (auxiliary bearing) 17B is disposed in the -Z direction of the multiple compression mechanism sections 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 section 20B.

[0027] First muffler 18A forms a first muffler chamber 19A between first bearing 17A and itself. The gas refrigerant compressed by first compression mechanism 20A is discharged into first muffler chamber 19A from discharge hole 29. The gas refrigerant discharged into first muffler chamber 19A is discharged into case 11 from muffler hole 19e. The second muffler 18B forms a second muffler chamber 19B between itself and the second bearing 17B. The gas refrigerant compressed by the second compression mechanism 20B is discharged from a discharge hole (not shown) into the second muffler chamber 19B. The second muffler chamber 19B is in communication with the first muffler chamber 19A via a muffler chamber passage (not shown).

[0028] The injection circuit 30 will now be described in detail. The injection circuit 30 intermittently injects the cooling refrigerant (the refrigerant in the second state, the intermediate pressure refrigerant, or the liquid refrigerant) introduced from outside the case 11 into the cylinder chamber 25. The injection circuit 30 has a pipe 32, a stop valve 33, a branch flow path 34, and an injection port 35.

[0029] The piping 32 introduces the cooling refrigerant from the outside of the case 11. The piping 32 branches off from the refrigerant flow path 8 between the radiator 3 and the expansion device 4 of the refrigeration cycle device 1. When the expansion device 4 has a high-pressure side expansion device and a low-pressure side expansion device, the piping 32 may branch off from the refrigerant flow path 8 between the high-pressure side expansion device and the low-pressure side expansion device. The piping 32 may branch off from the refrigerant flow path 8 via a gas-liquid separator. The piping 32 passes through the case 11 and the lubricant oil storage section 14 and extends into the inside of the partition member 16. A gas-liquid two-phase refrigerant that is lower in temperature than the gas refrigerant compressed by the compression mechanism section 20 flows through the refrigerant flow path 8 between the radiator 3 and the expansion device 4. The piping 32 introduces this gas-liquid two-phase refrigerant into the inside of the case 11 as a cooling refrigerant.

[0030] The shutoff valve 33 is disposed in the pipe 32 outside the case 11. The shutoff valve 33 is capable of stopping the introduction of the cooling refrigerant into the inside of the case 11. The branch flow passage 34 is formed in the partition member 16. The branch flow passage 34 extends from a tip of the pipe 32 inside the partition member 16 toward the multiple compression mechanism parts 20. The branch flow passage 34 connects the injection ports 35 of the multiple compression mechanism parts 20 to the common pipe 32.

[0031] The inlet 35 is an opening of the branch passage 34 into the cylinder chamber 25. The inlet 35 has a circular shape. The inlet 35 is formed in the partition member 16. The inlet 35 injects the cooling refrigerant introduced from the outside of the case 11 into the cylinder chamber 25. As shown in FIG. 2(d), the injection port 35 is disposed closer to the compression chamber 25p in the Y direction than the reference line 44. The injection port 35 is disposed within the range of the Y-direction width of the blade 40 disposed along the X direction. When the roller 22 rotates eccentrically to the maximum in the +X direction, the injection port 35 is disposed between the outer periphery of the roller 22 and the outer periphery of the cylinder chamber 25 in the X direction. As shown in FIG. 2(a), when the roller 22 rotates eccentrically to the maximum in the -X direction, the injection port 35 is disposed between the inner periphery and the outer periphery of the roller 22 in the X direction. The injection port 35 is not exposed inside the inner periphery of the roller 22.

[0032] The operation of the injection circuit 30 will be described in comparison with the conventional technology. Figure 2 is an explanatory diagram of the operation of the injection circuit 30, and is a cross-sectional view taken along line II-II in Figure 1. In Figure 2, the injection port 35 of the first embodiment is shown together with the injection port 35c of the conventional technology for comparison.

[0033] In the first half of the compression process of the gas refrigerant in the cylinder chamber 25 (see FIG. 2(c)), the pressure of the cooling refrigerant in the injection circuit 30 is higher than the pressure in the cylinder chamber 25. The cooling refrigerant is injected into the cylinder chamber 25 from an injection port. The liquid refrigerant contained in the injected cooling refrigerant absorbs heat and evaporates in the cylinder chamber 25. This cools the gas refrigerant being compressed and the compression mechanism 20. As the amount of refrigerant compressed increases, the compression performance of the rotary compressor 2 improves.

[0034] When the cooling refrigerant injected into the cylinder chamber 25 flows into the suction hole 28, the amount of gaseous refrigerant sucked into the cylinder chamber 25 from the suction hole 28 decreases. This reduces the compression performance of the rotary compressor 2. At the time of FIG. 2(b), the leading end of the roller 22 in the eccentric direction is at the end 28e of the suction hole 28 on the downstream side in the eccentric rotation direction of the roller 22. If the injection port opens into the cylinder chamber 25 before the time of FIG. 2(b), the injected cooling refrigerant may flow into the suction hole 28. It is required that the injection port be closed at least until the time of FIG. 2(b) (hereinafter, referred to as the first requirement).

[0035] As shown in FIG. 1, the gas refrigerant compressed to the discharge pressure in the cylinder chamber 25 is discharged into the case 11. The pressure of the lubricating oil reservoir 14 housed in the case 11 is equal to the discharge pressure. As described above, the lubricating oil in the lubricating oil reservoir 14 passes through the lubricating oil flow path formed along the central axis of the shaft 13 and is supplied to the sliding parts of the compressor body 10. Lubricating oil at the discharge pressure is present inside the inner circumference of the roller 22. If the inlet opens inside the inner circumference of the roller 22, there is a possibility that the lubricating oil will flow from the inlet into the injection circuit 30. It is required that the inlet does not open inside the inner circumference of the roller 22 (hereinafter referred to as the second requirement).

[0036] FIG. 4 is a graph showing the relationship between the pressure of the cooling refrigerant in the injection circuit 30 and the pressure in the compression chamber 25p. The horizontal axis of FIG. 4 is the eccentric rotation angle (sometimes simply referred to as the rotation angle) θ of the roller 22 from the reference line 44. The rotation angle θ is the angle from the center of the throat portion 43 to the tip of the roller 22 in the eccentric direction in the eccentric rotation direction. In FIG. 4, the solid line indicates the pressure in the compression chamber 25p at high load, and the dashed line indicates the pressure in the compression chamber 25p at low load. The dashed line indicates the pressure of the cooling refrigerant in the injection circuit 30 at high load, and the dashed line indicates the pressure of the cooling refrigerant in the injection circuit 30 at low load. The high load state is a state in which the rotary compressor 2 is operated at a high rotation speed, and the low load state is a state in which the rotary compressor 2 is operated at a low rotation speed. At high load, the pressure of the refrigerant flowing through the refrigeration cycle device 1 becomes high. Accordingly, the pressure of the cooling refrigerant in the injection circuit 30 becomes high. Furthermore, the pressure inside the case 11 increases, and the discharge pressure of the gaseous refrigerant from the compression chamber 25p increases.

[0037] As the rotation angle θ increases, the pressure in the compression chamber 25p increases. At high loads, the pressure in the compression chamber 25p exceeds the pressure of the cooling refrigerant in the injection circuit 30 when θ=180°. If the injection port opens to the compression chamber 25p after θ=180°, compressed gaseous refrigerant may flow from the injection port into the injection circuit 30. It is required that the injection port be closed at least after θ=180° (hereinafter referred to as the third requirement).

[0038] The injection port 35c of the prior art is opened and closed only by the end face of the roller 22 in the Z direction. Therefore, the design freedom regarding the position and opening area of ​​the injection port 35c is small. As shown in FIG. 2(a), the injection port 35c is located at a position where the rotation angle θ is about 315°. The injection port 35c opens into the cylinder chamber 25 just at the point in FIG. 2(b). The injection port 35c is closest to the inner circumference of the roller 22 at the point in FIG. 2(f), but does not open to the inside of the inner circumference. Since the design freedom of the injection port 35c is small, it can only be designed to barely satisfy the first and second requirements.

[0039] Fig. 3 is a graph showing the relationship between the eccentric rotation angle of the roller and the opening area ratio of the injection port. In the graph of Fig. 3, the solid line is the injection port 35 of the embodiment, and the dashed line is the injection port 35c of the prior art. The injection port opening area ratio on the vertical axis is normalized with the maximum opening area of ​​the injection port 35c of the prior art set to 1.

[0040] The design freedom of the injection port 35c of the prior art is small. The range of the rotation angle θ at which the injection port 35c opens with the maximum opening area becomes large. The injection port 35c opens to the compression chamber 25p at θ=180° in FIG. 2(d). As shown in FIG. 3, the injection port 35c is not closed until the rotation angle θ reaches about 225°. The injection port 35c cannot satisfy the third requirement. The design freedom of the injection port 35c in the conventional technology is small. It is difficult to increase the opening area of ​​the injection port 35c. The amount of cooling refrigerant injected into the cylinder chamber 25 is insufficient. There is a limit to improving the cooling performance and compression performance of the rotary compressor 2.

[0041] The injection port 35 of the embodiment is opened and closed by the end faces in the Z direction of the roller 22 and the blade 40. Therefore, there is a large degree of freedom in designing the position and opening area of ​​the injection port 35. Since the swing-type blade 40 opens and closes the injection port 35, there is an extremely large degree of freedom in designing the injection port 35. As shown in Fig. 2(a), the injection port 35 is located at a position just before the rotation angle θ of 360°.

[0042] FIG. 2(a) is the time when θ=0°. The inlet 35 is blocked by the end face of the roller 22 in the Z direction. The inlet 35 is closest to the inner circumference of the roller 22, but does not open to the inside of the inner circumference. The inlet 35 satisfies the second requirement. The lubricating oil on the inside of the inner circumference of the roller 22 is unlikely to flow into the inlet 35. A shortage of lubricating oil in the rotary compressor 2 is suppressed.

[0043] In Fig. 2(b), the leading end of roller 22 in the eccentric direction is at end 28e of suction hole 28 on the downstream side in the eccentric rotation direction of roller 22. The rotation angle θ in Fig. 2(b) is set to θ1. Inlet 35 is closed by the end face of roller 22 in the Z direction. Inlet 35 satisfies the first requirement.

[0044] FIG. 2(c) is the time when θ=90°. The entire injection port 35 opens to the cylinder chamber 25. The injection port 35 is opened only by the end face of the roller 22 in the Z direction. The injection port 35 moves relative to the roller 22 in the radial direction, and transitions from a fully closed state in which the entire port is blocked to a fully open state in which the opening area is maximum. As shown in FIG. 3, the injection port 35 opens in a short period of time within a narrow range of the rotation angle θ.

[0045] Fig. 2(d) is the time when θ = 180°. The entire inlet 35 is blocked by the Z-direction end face of the blade 40. Even in Figs. 2(e) and 2(f) where 180° < θ, the inlet 35 is blocked by the Z-direction end face of the blade 40 or the roller 22. The inlet 35 satisfies the third requirement. Under high load, the gas refrigerant compressed in the cylinder chamber 25 does not easily flow from the inlet 35 into the injection circuit 30.

[0046] As shown in Fig. 4, at the time of low load, the pressure in the compression chamber 25p exceeds the pressure of the cooling refrigerant in the injection circuit 30 when the rotation angle θ is 140°. As shown in Fig. 3, at θ = 140°, the opening area ratio of the injection port 35 of the embodiment is equivalent to that of the injection port 35c of the conventional technology. At 140° < θ, the opening area ratio of the injection port 35 of the embodiment is smaller than that of the injection port 35c of the conventional technology. Even at the time of low load, the gas refrigerant compressed in the cylinder chamber 25 is unlikely to flow into the injection circuit 30 from the injection port 35.

[0047] The inlet 35 of the embodiment has a large degree of freedom in design. The opening area of ​​the inlet 35 can be increased. As shown in FIG. 3, the opening area of ​​the inlet 35 of the embodiment is twice as large as that of the inlet 35c of the conventional technology. The pressure loss of the cooling refrigerant at the inlet 35 is suppressed. A sufficient amount of the cooling refrigerant is injected into the cylinder chamber 25. The cooling performance and compression performance of the rotary compressor 2 are improved.

[0048] As shown in Fig. 2(b), in the eccentric rotation direction of roller 22, the angle from the center of throat 43 (or blade housing hole 41) to end 28e of suction hole 28 is defined as θ1. As shown in Fig. 2(c), the angle from the center of throat 43 (or blade housing hole 41) to the tip of roller 22 in the eccentric direction at which the opening area of ​​injection port 35 is maximum is defined as θmax. At this time, the following formula 1 is established. θ1<θmax<140° (1) 3, θ1 is about 30°. θmax is generally in the range of 90°<θmax<110°. θmax satisfies the formula 1.

[0049] Because θ1<θmax, the opening area of ​​the injection port 35 becomes maximum after the tip of the roller 22 in the eccentric direction passes the end 28e of the suction hole 28. Since the opening area of ​​the injection port 35 does not become maximum before that, the inflow of the cooling refrigerant into the suction hole 28 is suppressed. When θmax<140°, the opening area of ​​the injection port 35 becomes maximum before the pressure in the compression chamber 25p exceeds the pressure of the cooling refrigerant in the injection circuit 30 under low load. Since the opening area of ​​the injection port 35 does not become maximum thereafter, the inflow of the compressed gas refrigerant into the injection port 35 is suppressed.

[0050] As described above in detail, in the rotary compressor 2 of the first embodiment, the inlet 35 for the cooling refrigerant is opened and closed by the end faces of the roller 22 and the blade 40 on the partition member 16 side. There is a large degree of freedom in designing the inlet 35. After the pressure of the gaseous refrigerant in the cylinder chamber 25 exceeds the pressure of the cooling refrigerant, the inlet 35 does not open to the cylinder chamber 25. The gaseous refrigerant does not easily flow into the inlet 35. The compression performance of the rotary compressor 2 is improved.

[0051] The blade 40 is integral with the roller 22 . Since the swing-type blade 40 opens and closes the injection port 35, there is a great degree of freedom in designing the injection port 35. The compression performance of the rotary compressor 2 is improved. Since no gap is generated between the blade 40 and the outer circumferential surface of the roller 22, the injection port 35 can be closed without any gap.

[0052] The transfer of the injection port 35 from a closed state to a state in which the opening area is maximum is effected only by the end face of the roller 22 on the partition member 16 side. When the inlet 35 is opened, the pressure of the cooling refrigerant is much higher than the pressure in the cylinder chamber 25. The inlet 35 is opened in a short time only by the end face of the roller 22 on the partition member 16 side. Pressure loss of the cooling refrigerant is suppressed, and a sufficient amount of cooling refrigerant is injected into the cylinder chamber 25. The cooling performance and compression performance of the rotary compressor 2 are improved.

[0053] In the eccentric rotation direction of roller 22, θ1 is the angle from the center of throat 43 (or blade housing hole 41) to end 28e of suction hole 28 on the downstream side in the eccentric rotation direction of roller 22. In the eccentric rotation direction of roller 22, θmax is the angle from the center of throat 43 (or blade housing hole 41) to the tip of roller 22 in the eccentric direction at which the opening area of ​​injection port 35 is maximum. In this case, θ1<θmax<140° holds. When θ1<θmax, the inflow of the cooling refrigerant into the suction hole 28 is suppressed. When θmax<140°, the inflow of the compressed gas refrigerant into the inlet 35 is suppressed. The compression performance of the rotary compressor 2 is improved.

[0054] The refrigeration cycle device 1 of the first embodiment has the above-mentioned rotary compressor 2, a radiator 3, an expansion device 4, and a heat absorber 5. The radiator 3 is connected to the rotary compressor 2. The expansion device 4 is connected to the radiator 3. The heat absorber 5 is connected between the expansion device 4 and the rotary compressor 2. Since the refrigeration cycle device 1 includes the rotary compressor 2 described above, the performance of the refrigeration cycle device 1 can be improved.

[0055] Second embodiment A rotary compressor according to a second embodiment will be described. Fig. 5 is a cross-sectional view of a portion corresponding to line II-II in Fig. 1. The rotary compressor of the second embodiment is a rotary type, which is different from the swing type of the first embodiment. Explanation of the second embodiment in the portions having the same configuration as the first embodiment will be omitted. The rotary compressor of the second embodiment is a so-called rotary type rotary compressor in which the blades 50 and the rollers 22 are separate.

[0056] The blade 50 has a flat plate shape as shown in FIG. 5(c). The cylinder 24 has a blade groove 51 as a blade accommodating hole, and supports the blade 50 in the cylinder chamber 25 so that the blade 50 can advance and retreat. The blade 50 is disposed inside the blade groove 51. The blade 50 is movable in the X direction along the blade groove 51. A lubricant hole 52 is formed at the end of the blade groove 51 in the -X direction. The lubricant in the lubricant reservoir 14 is introduced into the lubricant hole 52. As described above, the lubricant is discharged at pressure. The blade 50 is biased in the +X direction by the lubricant in the lubricant hole 52. The tip of the blade 50 in the +X direction abuts against the outer circumferential surface of the roller 22. The blade 50 moves in and out of the cylinder chamber 25 from the blade groove 51 in accordance with the eccentric rotation of the roller 22.

[0057] The injection circuit has an injection port 37 . The inlet 37 has an oval or elliptical shape. The length of the inlet 37 in the X direction is longer than the length in the Y direction. The inlet 37 is formed in a sliding area with the blade 50 of the partition member 16. The inlet 37 is disposed closer to the compression chamber 25p of the cylinder chamber 25 than the center of the sliding area in the Y direction. The inlet 37 is disposed on the compression chamber 25p side of the reference line 44 in the Y direction.

[0058] As shown in Fig. 5(a), when roller 22 has rotated eccentrically to the maximum in the -X direction, injection port 37 is disposed between the inner and outer peripheries of roller 22 in the X direction. As shown in Fig. 5(c), when roller 22 has rotated eccentrically to the maximum in the +X direction, injection port 37 is disposed between the outer periphery of roller 22 and the outer periphery of cylinder chamber 25 in the X direction. As described below, injection port 37 opens into cylinder chamber 25 between the tip of blade 50 and the outer circumferential surface of roller 22.

[0059] The operation of the injection circuit will now be described. Fig. 5 is an explanatory diagram of the operation of the injection circuit, and is a cross-sectional view of a portion corresponding to line II-II in Fig. 1. Injection port 37 is opened and closed by end faces in the Z direction of roller 22 and blade 50. Therefore, the design freedom of injection port 37 is large.

[0060] FIG. 5(a) is the time when θ=0°. The inlet 37 is closed by the end face of the roller 22 in the Z direction. The inlet 37 is closest to the inner circumference of the roller 22, but does not open to the inside of the inner circumference. The inlet 37 satisfies the second requirement. The lubricating oil on the inside of the inner circumference of the roller 22 is unlikely to flow into the inlet 37. A shortage of lubricating oil in the rotary compressor is suppressed.

[0061] 5(a) and 5(b), the leading end of the roller 22 in the eccentric direction passes the end 28e of the suction hole 28. Up to this point, the injection port 37 is blocked by the end face in the Z direction of the roller 22. The injection port 37 satisfies the first requirement.

[0062] FIG. 5(b) shows the state when θ=90°, which is the first half of the compression process in the cylinder chamber 25. The inlet 37 opens into the cylinder chamber 25 between the tip of the blade 50 and the outer circumferential surface of the roller 22. The roller 22 rotates eccentrically toward the suction chamber 25s side of the reference line 44. The gap between the tip of the blade 50 and the outer circumferential surface of the roller 22 is larger on the compression chamber 25p side than on the suction chamber 25s side of the reference line 44. The inlet 37 is disposed on the compression chamber 25p side of the reference line 44 in the Y direction. The opening area of ​​the inlet 37 into the cylinder chamber 25 becomes larger. A sufficient amount of cooling refrigerant is injected into the cylinder chamber 25 from the inlet 37.

[0063] 5(c) shows the time when θ=180°, which is the latter half of the compression process in the cylinder chamber 25. The entire injection port 37 is blocked by the end face of the blade 50 in the Z direction.

[0064] FIG. 5(d) is the time when θ=270°. The roller 22 rotates eccentrically toward the compression chamber 25p side of the reference line 44. The gap between the tip of the blade 50 and the outer circumferential surface of the roller 22 is smaller on the compression chamber 25p side than on the suction chamber 25s side of the reference line 44. The inlet 37 is disposed on the compression chamber 25p side of the reference line 44 in the Y direction. Between the tip of the blade 50 and the outer circumferential surface of the roller 22, the opening area of ​​the inlet 37 to the cylinder chamber 25 becomes smaller. The inflow of the gas refrigerant compressed inside the cylinder chamber 25 from the inlet 17 to the injection circuit becomes smaller. In the range of 180°<θ, the inlet 37 is almost closed. The inlet 37 satisfies the third requirement. Under high load, the gas refrigerant compressed in the cylinder chamber 25 is less likely to flow from the inlet 37 to the injection circuit.

[0065] As in the first embodiment, the angle from the center of the blade groove 51 to the end 28e of the suction hole 28 in the eccentric rotation direction of the roller 22 is defined as θ1. The angle from the center of the blade groove 51 to the tip of the roller 22 in the eccentric direction at which the opening area of ​​the injection port 37 is maximum is defined as θmax. In this case, θ1<θmax<140° holds.

[0066] As described above in detail, in the rotary compressor of the second embodiment shown in Fig. 5(c), the blade 50 is separate from the roller 22. The inlet 37 is formed in the region of the partition member 16 where the blade 50 slides, closer to the compression chamber 25p than the center in the Y direction. The inlet 37 opens into the cylinder chamber 25 between the tip of the blade 50 on the cylinder chamber 25 side and the outer circumferential surface of the roller 22. There is a large degree of freedom in designing the injection port 37. In the first half of the compression process, the opening area of ​​the injection port 37 becomes large, and a sufficient amount of cooling refrigerant is injected into the cylinder chamber 25. In the second half of the compression process, the opening area of ​​the injection port 37 becomes small, and the compressed gas refrigerant does not easily flow from the injection port 37 into the injection circuit 30. The compression performance of the rotary compressor is improved.

[0067] The length of the inlet 37 in the X direction is longer than the length in the Y direction. By adjusting the length of the injection port 37 in the X direction, it is possible to adjust the range of the rotation angle θ at which the injection port 37 opens into the cylinder chamber 25. A sufficient amount of cooling refrigerant is injected into the cylinder chamber 25.

[0068] (Third embodiment) A rotary compressor according to a third embodiment will be described. Fig. 6 is a partial cross-sectional view of a rotary compressor of a third embodiment. Fig. 7 is a cross-sectional view taken along line VII-VII in Fig. 6. The first compression mechanism 20A in Fig. 6 is in the state shown in Fig. 7(b), and the second compression mechanism 20B is in the state shown in Fig. 7(d).

[0069] As shown in Fig. 7, the rotary compressor of the third embodiment is of the same rotary type as the second embodiment. As shown in Fig. 6, the third embodiment differs from the second embodiment in that the inlet 37 is an opening of the branch flow path in that the inlet 37 is an opening of the first recess 61. Description of the third embodiment in the parts having the same configuration as the second embodiment will be omitted.

[0070] The injection circuit has an injection port 37, a first recess 61, a second recess 62, a third recess 63, a distribution flow path 64, and a pipe 32. The injection port 37, the first recess 61, the second recess 62, and the third recess 63 formed on the first compression mechanism part 20A side will be described below, but these are also formed similarly on the second compression mechanism part 20B side. The injection port 37 is an opening of the first recess 61 . The first recess 61 is formed in the end face of the partition member 16 on the first compression mechanism section 20A side.

[0071] The second recess 62 is formed on the end face of the blade 50 on the partition member 16 side. The opening of the second recess 62 is closed by the partition member 16. The second recess 62 extends in the X direction from the center of the blade 50 in the X direction to the end in the +X direction. The end of the second recess 62 in the +X direction can communicate with the first recess 61.

[0072] The third recess 63 is formed in the end surface of the partition member 16 on the first compression mechanism unit 20A side. The opening of the third recess 63 is closed by the cylinder 24 of the first compression mechanism unit 20A. As shown in FIG. 7(b), the third recess 63 extends in the Y direction. The end of the third recess 63 opens into the blade groove 51 formed in the cylinder 24.

[0073] The pipe 32 extends from the outside to the inside of the case 11. The pipe 32 is disposed in the cylinder 24 of the first compression mechanism portion 20A. 6, the distribution passage 64 extends in the -Z direction from the tip of the pipe 32. The distribution passage 64 communicates with a third recess 63 formed on the first compression mechanism unit 20A side of the partition member 16. The distribution passage 64 penetrates the partition member 16 in the Z direction. The distribution passage 64 communicates with a third recess 63 formed on the second compression mechanism unit 20B side of the partition member 16.

[0074] The operation of the injection circuit will now be described. FIG. 7 is a diagram for explaining the operation of the injection circuit, and is a cross-sectional view taken along line VII-VII in FIG.

[0075] 7(a) is the time when θ=0°. The blade 50 moves furthest in the -X direction. The end of the second recess 62 in the +X direction does not communicate with the first recess 61. The inlet 37 is closed by the end face of the roller 22 in the Z direction. No cooling refrigerant is injected into the cylinder chamber 25 from the inlet 37.

[0076] 7(b) is the time when θ=90°. The blade 50 moves in the +X direction. The -X direction end of the second recess 62 communicates with the third recess 63, and the +X direction end communicates with the first recess 61. The piping 32, the distribution flow passage 64, the third recess 63, the second recess 62, the first recess 61, and the injection port 37 communicate in this order. Between the tip of the blade 50 and the outer circumferential surface of the roller 22, the injection port 37 opens into the cylinder chamber 25. A cooling refrigerant is injected into the cylinder chamber 25 from the injection port 37.

[0077] 7(c) is the time when θ=180°. The blade 50 moves furthest in the +X direction. The -X direction end of the second recess 62 does not communicate with the third recess 63. The inlet 37 is closed by the Z direction end face of the blade 50. No cooling refrigerant is injected into the cylinder chamber 25 from the inlet 37.

[0078] 7(d) is the time when θ=270°. The blade 50 moves in the -X direction. The -X direction end of the second recess 62 communicates with the third recess 63, and the +X direction end communicates with the first recess 61. As in the second embodiment, the opening area of ​​the injection port 37 to the cylinder chamber 25 is small between the tip of the blade 50 and the outer circumferential surface of the roller 22. The flow of compressed gas refrigerant from the injection port 17 to the injection circuit is reduced. In the third embodiment, as in the second embodiment, the cooling refrigerant is intermittently injected into the cylinder chamber 25 through the injection port 37.

[0079] As described above in detail, in the rotary compressor of the third embodiment shown in Fig. 6, the inlet 37 is an opening of the first recess 61 formed in the partition member 16. The blade 50 has the second recess 62 capable of communicating with the first recess 61 on the end face on the partition member 16 side. The piping 32 for the cooling refrigerant of the injection circuit can be arranged in the cylinder 24, not in the partition member 16. The discharge hole 29 of the cylinder chamber 25 can be formed in the partition member 16 in addition to the bearing 17. The compression performance of the rotary compressor is improved.

[0080] In the embodiment described above, the rotary compressor 2 has two compression mechanism units 20 (the first compression mechanism unit 20A and the second compression mechanism unit 20B). In contrast, the rotary compressor 2 may have only one compression mechanism unit 20, or may have three or more compression mechanism units 20. In the above embodiment, the rotary compressor cools the compression mechanism by injecting a liquid refrigerant, but the rotary compressor may inject an intermediate pressure gas refrigerant, thereby making it possible to provide a rotary compressor with improved energy saving and increased cooling and heating capabilities while suppressing deterioration in reliability.

[0081] According to at least one of the embodiments described above, there are injection ports 35, 37 that are opened and closed by the end faces of the roller 22 and the blades 40, 50 on the partition member 16 side. This can improve the compression performance of the rotary compressor. The refrigeration cycle device 1 using the rotary compressor 2 of this embodiment is not limited to this. In the rotary compressor 2 of the embodiment described above, a configuration using two cylinders has been described, but this is not limited to this. The number of cylinders may be one, or three or more. Also, the first bearing 17A or the second bearing 17B may be used as a closing member, and the injection ports 35, 37 may be provided in the first bearing 17A or the second bearing 17B.

[0082] 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, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope of the invention and its equivalents described in the claims, as well as in the scope and spirit of the invention. [Explanation of symbols]

[0083] 1...refrigeration cycle device, 2...rotary compressor, 3...heat radiator, 4...expansion device, 5...heat sink, 11...case, 13...shaft, 14...lubricating oil storage section, 16...partition member (blocking member), 20...compression mechanism section, 21...eccentric section, 22...roller, 24...cylinder, 25...cylinder chamber, 25p...compression chamber, 25s...suction chamber, 28...suction hole, 28e...end section, 35, 37...inlet, 40...blade, 41...blade accommodating hole, 50...blade, 51...blade groove (blade accommodating hole), 61...first recess, 62...second recess.

Claims

1. A case is provided for accommodating a shaft and a compression mechanism therein, The compression mechanism includes: an eccentric portion provided on the shaft; a cylinder having a cylinder chamber in which the eccentric portion is disposed; a roller having a cylindrical shape, fitted to the eccentric portion, and eccentrically rotating within the cylinder chamber; a blade that moves back and forth with the eccentric rotation of the roller to divide the cylinder chamber into a suction chamber and a compression chamber for the refrigerant in a first state; a closing member that closes an end of the cylinder chamber in an axial direction of the shaft; an injection port formed in the closing member, opening into the cylinder chamber, and through which the refrigerant in the second state introduced from the outside of the case is injected into the cylinder chamber; the injection port is opened and closed by end faces of the roller and the blade on the closing member side; the blade is separate from the roller, and is movable in a first direction along a blade groove formed in the cylinder, and a tip end of the blade on the cylinder chamber side in the first direction abuts against an outer circumferential surface of the roller; the injection port is formed in a region of the closing member where the blade slides against the injection port, closer to the compression chamber than a center in the axial direction and a second direction perpendicular to the first direction; the injection port is open to the cylinder chamber between a tip of the blade on the cylinder chamber side and an outer circumferential surface of the roller, the injection port is an opening of a first recess formed in the blocking member, The blade has a second recess in an end surface on the closing member side, the second recess being capable of communicating with the first recess. Rotary compressor.

2. The injection port has a length in the first direction that is longer than a length in the second direction. The rotary compressor according to claim 1 .

3. The blade moves in and out of the cylinder chamber through a blade receiving hole formed in the cylinder in accordance with the eccentric rotation of the roller, The cylinder has a suction hole that draws the refrigerant in the first state into the cylinder chamber, In the eccentric rotation direction of the roller, an angle from the center of the blade accommodating hole to an end of the suction hole on the downstream side in the eccentric rotation direction of the roller is defined as θ1, When the angle from the center of the blade housing hole to the tip of the roller in the eccentric direction at which the opening area of ​​the injection port is maximum in the eccentric rotation direction of the roller is defined as θmax, θ1<θmax<140° is satisfied. The rotary compressor according to claim 1 or 2.

4. A rotary compressor according to any one of claims 1 to 3, a radiator connected to the rotary compressor; an expansion device connected to the heat sink; a heat sink connected between the expansion device and the rotary compressor. Refrigeration cycle equipment.

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