Rotary compressor and refrigeration cycle device

Abstract

The present application provides a rotary compressor and a refrigeration cycle device capable of improving compression performance. The rotary compressor of the embodiment has a casing that houses a shaft and a compression mechanism portion inside. The compression mechanism portion has an eccentric portion, a cylinder, a roller, a vane, a closing member, and an injection port. The cylinder has a cylinder chamber in which the eccentric portion is disposed. The roller is cylindrical, is fitted to the eccentric portion, and rotates eccentrically in the cylinder chamber. The vane moves in and out in conjunction with the eccentric rotation of the roller, and divides the cylinder chamber into a suction chamber and a compression chamber for gas refrigerant. The closing member closes an end portion of the cylinder chamber in the axial direction of the shaft. The injection port is formed in the closing member, is open to the cylinder chamber, and injects cooling refrigerant introduced from the outside of the casing into the cylinder chamber. The injection port is opened and closed by an end surface of the closing member on the side of the roller and the vane.

Description

TECHNICAL FIELD

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

[0002] In a refrigeration cycle apparatus, a rotary compressor that compresses a gas refrigerant is used. An injection circuit that injects a cooling refrigerant into a cylinder chamber of the rotary compressor is proposed. For the rotary compressor, improvement in compression performance is required.

[0003] Patent Document 1: Japanese Patent Application Laid-Open (JP-A) No. 2000-170678 SUMMARY

[0004] An object of the present application is to provide a rotary compressor and a refrigeration cycle apparatus that can improve compression performance.

[0005] The rotary compressor of the embodiment has a casing that houses a shaft and a compression mechanism portion inside. The compression mechanism portion has an eccentric portion, a cylinder, a roller, a vane, a closing member, and an injection port. The eccentric portion is provided to the shaft. The cylinder has a cylinder chamber in which the eccentric portion is disposed. The roller is cylindrical, is fitted to the eccentric portion, and rotates eccentrically inside the cylinder chamber. The vane moves in and out in conjunction 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 portion of the cylinder chamber in the axial direction of the shaft. The injection port is formed in the closing member, opens to the cylinder chamber, and injects a cooling refrigerant introduced from the outside of the casing into the cylinder chamber. The injection port is opened and closed by an end surface of the closing member on the side of the roller and the vane. BRIEF DESCRIPTION OF DRAWINGS

[0006] Figure 1 is a schematic configuration view of a refrigeration cycle apparatus of the first embodiment including a rotary compressor.

[0007] Figure 2 is an explanatory view of the effect of the injection circuit of the first embodiment.

[0008] Figure 3 is a graph showing the relationship between the eccentric rotation angle of the roller and the opening area ratio of the injection port.

[0009] Figure 4 is a graph showing the relationship between the pressure of the cooling refrigerant of the injection circuit and the pressure of the compression chamber.

[0010] Figure 5 is an explanatory view of the effect of the injection circuit of the second embodiment.

[0011] Figure 6 is a partial cross-sectional view of the rotary compressor of the third embodiment.

[0012] Figure 7 is a diagram illustrating the operation of the injection circuit of the third embodiment.

[0013] Explanation of symbols

[0014] 1: refrigeration cycle device; 2: rotary compressor; 3: heat sink; 4: expansion device; 5: heat sink; 11: housing; 13: shaft; 14: lubricating oil reservoir; 16: partition member (closure member); 20: compression mechanism portion; 21: eccentric portion; 22: roller; 24: cylinder; 25: cylinder chamber; 25p: compression chamber; 25s: suction chamber; 28: suction hole; 28e: end portion; 35, 37: injection port; 40: vane; 41: vane housing hole; 50: vane; 51: vane slot (vane housing hole); 61: first recess; 62: second recess. DETAILED DESCRIPTION

[0015] Hereinafter, a rotary compressor and a refrigeration cycle device according to the embodiments will be described with reference to the drawings.

[0016] Figure 1 is a diagram illustrating the operation of the injection circuit of the third embodiment.

[0017] A refrigeration cycle device 1 will be described briefly.

[0018] The refrigeration cycle device 1 has a rotary compressor 2, a heat sink (e.g., a condenser) 3 connected to the rotary compressor 2, an expansion device (e.g., an expansion valve) 4 connected to the heat sink 3, and a heat sink (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 in a refrigerant flow path 8 of the refrigeration cycle device 1 while changing phase.

[0019] The rotary compressor 2 compresses a low-pressure gaseous refrigerant (fluid) taken into the inside to a high-temperature, high-pressure gaseous refrigerant. The detailed configuration of the rotary compressor 2 will be described later.

[0020] The heat sink 3 radiates heat from the high-temperature, high-pressure gaseous refrigerant supplied from the rotary compressor 2, and makes the high-temperature, high-pressure gaseous refrigerant into a high-pressure liquid refrigerant.

[0021] The expansion device 4 reduces the pressure of the high-pressure liquid refrigerant sent from the heat sink 3, and makes the high-pressure liquid refrigerant into a low-temperature, low-pressure liquid refrigerant.

[0022] The heat absorber 5 vaporizes the low-temperature, low-pressure liquid refrigerant sent from the expansion device 4 into a low-pressure gas refrigerant. In the heat absorber 5, heat of vaporization is taken from the surroundings when the low-pressure liquid refrigerant is vaporized, whereby the surroundings are cooled. The low-pressure gas refrigerant after the heat absorber 5 is taken into the inside of the above-mentioned rotary compressor 2.

[0023] Thus, in the refrigeration cycle device 1 of the present embodiment, the refrigerant as the working fluid circulates in the refrigerant flow path 8 while changing between the gas refrigerant and the liquid refrigerant. The refrigerant radiates heat in the process of changing from the gas refrigerant to the liquid refrigerant, and absorbs heat in the process of changing from the liquid refrigerant to the gas refrigerant. Heating, cooling, and the like are performed by these radiations and absorptions of heat.

[0024] (First Embodiment)

[0025] The rotary compressor 2 of the first embodiment will be described. The rotary compressor 2 of the first embodiment is a so-called swing type rotary compressor 2 in which the vane 40 is integrated with the roller 22.

[0026] 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 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 the vertically upward direction.

[0027] The rotary compressor 2 has a reservoir 6 and a compressor main body 10. The reservoir 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 main body 10 through a suction pipe.

[0028] The compressor main body 10 has a housing 11, a shaft 13, a motor portion 15, a lubricating oil reservoir 14, a plurality of compression mechanism portions 20, and an injection circuit 30.

[0029] The housing 11 is formed in a cylindrical shape with both end portions closed. The housing 11 houses the shaft 13, the motor portion 15, the lubricating oil reservoir 14, and the plurality of compression mechanism portions 20. The housing 11 has a supply portion 12 at the upper end portion thereof. The supply portion 12 supplies the gas refrigerant inside the housing 11 to the heat radiator 3.

[0030] The shaft 13 is disposed along the central axis of the compressor main body 10. The shaft 13 has a plurality of eccentric portions 21.

[0031] The motor portion 15 is disposed in the +Z direction of the shaft 13. The motor portion 15 has a stator 15a and a rotor 15b. The stator 15a is fixed to the inner peripheral surface of the housing 11. The rotor 15b is fixed to the outer peripheral surface of the shaft 13. The motor portion 15 rotationally drives the shaft 13.

[0032] The lubricating oil reservoir 14 is located inside the housing 11 and outside the plurality of compression mechanism sections 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 from the lower end of the shaft 13 along the central axis. The lubricating oil in the lubricating oil reservoir 14 is supplied to the sliding parts of the compressor body 10 through the lubricating oil flow path as the shaft 13 rotates.

[0033] Multiple compression units 20 compress gaseous refrigerant in conjunction with the rotation of shaft 13. The multiple compression units 20 are arranged in the -Z direction of shaft 13. The multiple compression units 20 are fixed to frame 11a. The outer peripheral surface of frame 11a is fixed to the inner peripheral surface of housing 11. The multiple compression units 20 include a first compression unit 20A and a second compression unit 20B. The first compression unit 20A and the second compression unit 20B are arranged sequentially from the +Z direction to the -Z direction. The configuration of the first compression unit 20A will be described below as representative. The configuration of the second compression unit 20B is the same as that of the first compression unit 20A, except for the eccentric direction of the eccentric portion 21.

[0034] The first compression mechanism 20A includes an eccentric part 21, a roller 22, a blade 40, and a cylinder 24.

[0035] The eccentric portion 21 is cylindrical and integrally formed with the shaft 13. When viewed from the +Z direction, the center of the eccentric portion 21 is eccentric to the central axis of the shaft 13.

[0036] The roller 22 is cylindrical and is fitted around the outer periphery of the eccentric portion 21. The roller 22 rotates eccentrically together with the eccentric portion 21 inside the cylinder chamber 25.

[0037] Figure 2 yes Figure 1 A sectional view along line II-II.

[0038] like Figure 2 As shown in (a), the blade 40 is integrally formed with the roller 22. The blade 40 is flat. The blade 40 extends radially outward from the outer peripheral surface of the roller 22. The cylinder 24 has a blade receiving hole 41. A pair of blade receiving holes 41 are arranged radially on the shaft 13, having a back pressure space 42a and a bushing groove 42b formed in an interconnected state, and a throat 43 is formed between the back pressure space 42a and the bushing groove 42b. A pair of generally semi-circular bushings 42c are embedded in the bushing groove 42b. The pair of bushings 42c are configured to oscillate about the axis of the bushing groove 42b. The back pressure space 42a is formed to be generally circular. The blade 40 can be retracted between the pair of bushings 42c as the roller 22 rotates.

[0039] In the present application, an X direction (1st direction) and a Y direction (2nd 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 portion 43 (or the vane receiving hole 41) is set 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 portion 43 toward the center of the shaft 13. The Y direction is a direction perpendicular to the Z direction and the X direction.

[0040] The cylinder 24 discharges the gas refrigerant compressed inside the cylinder chamber 25 to the inside of the housing 11. The cylinder 24 has the cylinder chamber 25, a suction hole 28, and a discharge hole 29 (refer to Figure 1 ).

[0041] The cylinder chamber 25 is formed by penetrating the radially central portion of the cylinder 24 along the Z direction. The cylinder chamber 25 internally receives the eccentric portion 21, the roller 22, and the vane 40. As shown in (d) of Figure 2 , the vane 40 divides the inside of the cylinder chamber 25 into a suction chamber 25s and a compression chamber 25p together with the roller 22. The suction hole 28 communicates the suction chamber 25s with the reservoir 6 shown in (a) of Figure 1 . The discharge hole 29 is formed in the bearing 17 (the 1st bearing 17A or the 2nd bearing 17B). The discharge hole 29 communicates the compression chamber 25p with the muffler chamber 19 (the 1st muffler chamber 19A or the 2nd muffler chamber 19B) via a valve core 29v.

[0042] The volume of the suction chamber 25s increases by the eccentric rotation of the roller 22. The gas refrigerant (the refrigerant of the 1st state) is sucked from the reservoir 6 to the suction chamber 25s through the suction hole 28. The volume of the compression chamber 25p decreases by the eccentric rotation of the roller 22, and the gas refrigerant is compressed. If the gas refrigerant exceeds the discharge pressure, the valve core 29v is pushed away. The gas refrigerant is discharged from the compression chamber 25p to the muffler chamber 19 through the discharge hole 29.

[0043] As shown in (a) of Figure 1 , the rotary compressor 2 has a partition member (enclosing member) 16, a 1st bearing 17A, a 2nd bearing 17B, a 1st muffler 18A, and a 2nd muffler 18B.

[0044] The partition member 16 is arranged between the 1st compression mechanism portion 20A and the 2nd compression mechanism portion 20B. The partition member 16 encloses the -Z direction end portion of the cylinder chamber 25 of the 1st compression mechanism portion 20A. The partition member 16 encloses the +Z direction end portion of the cylinder chamber 25 of the 2nd compression mechanism portion 20B.

[0045] The 1st bearing (main bearing) 17A is arranged in the +Z direction of the plurality of compression mechanism portions 20, and supports the shaft 13. The 1st bearing 17A encloses the +Z direction end portion of the cylinder chamber 25 of the 1st compression mechanism portion 20A.

[0046] The 2nd bearing (secondary bearing) 17B is arranged in the -Z direction of the plurality of compression mechanism portions 20, and supports the shaft 13. The 2nd bearing 17B closes the -Z direction end of the cylinder chamber 25 of the 2nd compression mechanism portion 20B.

[0047] The 1st muffler 18A forms a 1st muffler chamber 19A between the 1st bearing 17A. The gas refrigerant compressed by the 1st compression mechanism portion 20A is discharged from the discharge hole 29 to the 1st muffler chamber 19A. The gas refrigerant discharged to the 1st muffler chamber 19A is discharged from the muffler hole 19e to the inside of the housing 11.

[0048] The 2nd muffler 18B forms a 2nd muffler chamber 19B between the 2nd bearing 17B. The gas refrigerant compressed by the 2nd compression mechanism portion 20B is discharged from a discharge hole (not shown) to the 2nd muffler chamber 19B. The 2nd muffler chamber 19B communicates with the 1st muffler chamber 19A via a muffler chamber interpassage (not shown).

[0049] The injection circuit 30 will be described in detail.

[0050] The injection circuit 30 intermittently injects the cooling refrigerant (the 2nd state refrigerant, the intermediate pressure refrigerant, the liquid refrigerant) introduced from the outside of the housing 11 into the cylinder chamber 25. The injection circuit 30 has a pipe 32, a run-on valve 33, a branch flow path 34, and an injection port 35.

[0051] The pipe 32 introduces the cooling refrigerant from the outside of the housing 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. In the case where the expansion device 4 has a high-pressure side expansion device and a low-pressure side expansion device, the pipe 32 can also branch from the refrigerant flow path 8 between the high-pressure side expansion device and the low-pressure side expansion device. The pipe 32 can also branch from the refrigerant flow path 8 via a gas-liquid separator. The pipe 32 extends to the inside of the partition member 16 through the housing 11 and the lubricating oil reservoir 14. The gas-liquid two-phase refrigerant of lower temperature than the gas refrigerant compressed by the compression mechanism portion 20 flows in the refrigerant flow path 8 between the radiator 3 and the expansion device 4. The pipe 32 introduces this gas-liquid two-phase refrigerant as the cooling refrigerant to the inside of the housing 11.

[0052] The run-on valve 33 is provided to the pipe 32 outside the housing 11. The run-on valve 33 can cut off the introduction of the cooling refrigerant to the inside of the housing 11.

[0053] The branch flow path 34 is formed in the partition member 16. The branch flow path 34 extends from the front end of the pipe 32 inside the partition member 16 toward the plurality of compression mechanism portions 20. The branch flow path 34 communicates the injection ports 35 of the plurality of compression mechanism portions 20 with the common pipe 32.

[0054] Inlet 35 is the opening of the branch flow path 34 into the cylinder block chamber 25. Inlet 35 is circular in shape. Inlet 35 is formed in the partition member 16. Inlet 35 injects cooling refrigerant introduced from the outside of the housing 11 into the interior of the cylinder block chamber 25.

[0055] like Figure 2 As shown in (d), the injection port 35 is positioned in the Y direction closer to the compression chamber 25p than the reference line 44. The injection port 35 is positioned within the width of the blade 40 arranged along the X direction in the Y direction. When the roller 22 rotates to its maximum eccentricity in the +X direction, the injection port 35 is positioned in the X direction between the outer periphery of the roller 22 and the outer periphery of the cylinder chamber 25. Figure 2 As shown in (a), when the roller 22 rotates to its maximum eccentricity in the -X direction, the injection port 35 is positioned in the X direction between the inner and outer circumferences of the roller 22. The injection port 35 does not protrude into the inner side of the inner circumference of the roller 22.

[0056] The function of the injection circuit 30 is illustrated by comparing it with existing technologies. Figure 2 This is an explanatory diagram of the function of injection circuit 30, and it is... Figure 1 A cross-sectional view at line II-II. Figure 2 For comparison purposes, the injection port 35c of the prior art is included together with the injection port 35 of the first embodiment.

[0057] The first half of the compression process of the gaseous refrigerant in cylinder chamber 25 (refer to...) Figure 2 (c) The pressure of the cooling refrigerant in the injection circuit 30 is greater than the pressure in the cylinder chamber 25. The cooling refrigerant is injected into the cylinder chamber 25 through the injection port. The liquid refrigerant contained in the injected cooling refrigerant absorbs heat and evaporates in the cylinder chamber 25. As a result, the gaseous refrigerant being compressed and the compression mechanism 20 are cooled. The amount of refrigerant being compressed increases, therefore, the compression performance of the rotary compressor 2 is improved.

[0058] When the refrigerant for cooling injected into the cylinder chamber 25 flows into the suction port 28, the amount of gaseous refrigerant drawn into the cylinder chamber 25 through the suction port 28 decreases. Consequently, the compression performance of the rotary compressor 2 decreases. Figure 2 At time (b), the eccentric leading edge of roller 22 is located at the end 28e of suction hole 28 on the downstream side of the eccentric rotation direction of roller 22. Figure 2 Before the time specified in (b), when the injection port opens into the cylinder block chamber 25, the injected refrigerant may flow into the suction port 28. It is required that at least until... Figure 2 The injection port shall be closed by time (b) (hereinafter referred to as requirement 1).

[0059] like Figure 1 As shown, the gaseous refrigerant compressed to discharge pressure in the cylinder chamber 25 is discharged into the interior of the housing 11. The pressure of the lubricating oil reservoir 14 housed inside the housing 11 is the same as the discharge pressure. As described above, the lubricating oil in the lubricating oil reservoir 14 is supplied to the sliding portion of the compressor body 10 through a lubricating oil flow path formed along the central axis of the shaft 13. Discharge pressure lubricating oil exists on the inner side of the inner circumference of the roller 22. If the injection port opens to the inner side of the inner circumference of the roller 22, lubricating oil may flow into the injection circuit 30 from the injection port. It is required that the injection port does not open to the inner side of the inner circumference of the roller 22 (hereinafter referred to as the second requirement).

[0060] Figure 4 It 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. Figure 4 The horizontal axis is the eccentric rotation angle (sometimes simply called the rotation angle) θ of roller 22 from the baseline 44. The rotation angle θ is the angle from the center of the throat 43 to the leading edge of roller 22 in the eccentric rotation direction. Figure 4 In the diagram, the solid line represents the pressure of the compression chamber 25p under high load, and the dashed line represents the pressure of the compression chamber 25p under low load. The single-dotted line represents the pressure of the refrigerant used for cooling in the injection circuit 30 under high load, and the double-dotted line represents the pressure of the refrigerant used for cooling in the injection circuit 30 under low load. High load refers to the state where the rotary compressor 2 operates at high speed, and low load refers to the state where the rotary compressor 2 operates at low speed. Under high load, the pressure of the refrigerant flowing in the refrigeration cycle unit 1 increases. Correspondingly, the pressure of the refrigerant used for cooling in the injection circuit 30 increases. Furthermore, the pressure inside the housing 11 increases, and the discharge pressure of the gaseous refrigerant from the compression chamber 25p increases.

[0061] As the rotation angle θ increases, the pressure in the compression chamber 25p increases. Under high load, at θ = 180°, the pressure in the compression chamber 25p is higher than the pressure of the refrigerant used for cooling in the injection circuit 30. After θ = 180°, if the injection port is open to the compression chamber 25p, the compressed gaseous refrigerant may flow into the injection circuit 30 from the injection port. It is required that the injection port be closed at least after θ = 180° (hereinafter referred to as requirement 3).

[0062] In the prior art, the injection port 35c opens and closes only through the Z-direction end face of the roller 22. Therefore, the design freedom related to the position and opening area of ​​the injection port 35c is limited. For example... Figure 2 As shown in (a), the injection port 35c is located at a rotation angle θ of approximately 315°. The injection port 35c is exactly at... Figure 2 At time (b), the cylinder chamber 25 opens. Inlet 35c is located at... Figure 2The moment of (f) is closest to the inner circumference of roller 22, but just before it opens to the inside of the inner circumference. The design freedom of injection inlet 35c is small, therefore, there are limitations to designing it in a way that barely meets the first and second requirements.

[0063] Figure 3 This is a graph showing the relationship between the eccentric rotation angle of the roller and the ratio of the injection port opening area. Figure 3 In the graph, the solid line represents the injection port 35 of the embodiment, and the dashed line represents the injection port 35c of the prior art. The vertical axis represents the opening area ratio of the injection port, which is normalized by setting the maximum opening area of ​​the prior art injection port 35c to 1.

[0064] The design freedom of the injection port 35c in the prior art is relatively small. The range of the rotation angle θ of the injection port 35c with the maximum opening area increases. Figure 2 At the moment when θ = 180° of (d), the opening is made into the compression chamber 25p. For example... Figure 3 As shown, the injection port 35c is not closed until the rotation angle θ becomes approximately 225°. Injection port 35c fails to meet requirement 3.

[0065] The design of the injection port 35c in the existing technology has limited freedom. 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. The improvement of the cooling performance and compression performance of the rotary compressor 2 is limited.

[0066] In this embodiment, the injection port 35 opens and closes via the Z-direction end faces of the roller 22 and the blade 40. Therefore, there is considerable design freedom related to the position and opening area of ​​the injection port 35. The oscillating blade 40 opens and closes the injection port 35, thus providing extremely high design freedom for the injection port 35. Figure 2 As shown in (a), the injection port 35 is located immediately before the rotation angle θ of 360°.

[0067] Figure 2 (a) is the moment when θ = 0°. The inlet 35 is closed by the Z-direction end face of the roller 22. The inlet 35 is closest to the inner circumference of the roller 22, but does not open to the inner side of the inner circumference. The inlet 35 satisfies the second requirement. Lubricating oil on the inner side of the inner circumference of the roller 22 is difficult to flow into the inlet 35. This suppresses insufficient lubricating oil in the rotary compressor 2.

[0068] exist Figure 2 In (b), the eccentrically positioned front end of roller 22 is located at the end 28e of suction port 28 downstream of the eccentric rotation direction of roller 22. Figure 2 The rotation angle θ of (b) is set to θ1. The injection inlet 35 is closed by the Z-direction end face of the roller 22. The injection inlet 35 satisfies the first requirement.

[0069] Figure 2 (c) is the time when θ = 90°. The entire injection port 35 is opened to the cylinder chamber 25. The opening of the injection port 35 is performed only by the Z-direction end surface of the roller 22. The injection port 35 moves relatively in the radial direction of the roller 22 from the fully closed state in which the entire injection port 35 is closed to the fully open state in which the opening area of the injection port 35 is largest. As shown in Figure 3 , the opening of the injection port 35 is performed in a short time in a narrow range of the rotation angle θ.

[0070] Figure 2 (d) is the time when θ = 180°. The entire injection port 35 is closed by the Z-direction end surface of the vane 40. In the range of 180° < θ, the opening area of the injection port 35 is smaller than that of the injection port 35c of the related art. The injection port 35 satisfies the first requirement. The gaseous refrigerant compressed by the cylinder chamber 25 is difficult to flow into the injection circuit 30 from the injection port 35. Figure 2 (e) and Figure 2 (f) are the times when the injection port 35 is closed by the Z-direction end surface of the vane 40 or the roller 22. The injection port 35 satisfies the third requirement. The gaseous refrigerant compressed by the cylinder chamber 25 is difficult to flow into the injection circuit 30 from the injection port 35 at the time of high load.

[0071] As shown in Figure 4 , at the time of low load, at the time when the rotation angle θ is 140°, the pressure of the compression chamber 25p is higher than the pressure of the cooling refrigerant of the injection circuit 30. As shown in Figure 3 , at θ = 140°, the opening area ratio of the injection port 35 of the embodiment is the same as that of the injection port 35c of the related art. In the range of 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 related art. The gaseous refrigerant compressed by the cylinder chamber 25 is also difficult to flow into the injection circuit 30 from the injection port 35 at the time of low load.

[0072] The design freedom of the injection port 35 of the embodiment is large. It is possible to increase the opening area of the injection port 35. As shown in Figure 3 , the opening area of the injection port 35 of the embodiment is twice as large as that of the injection port 35c of the related art. It is possible to suppress the pressure loss of the cooling refrigerant at the injection port 35. It is possible to inject a sufficient amount of the cooling refrigerant into the cylinder chamber 25. The cooling performance and the compression performance of the rotary compressor 2 are improved.

[0073] As shown in Figure 2 (b), in the eccentric rotation direction of the roller 22, the angle from the center of the throat portion 43 (or the vane housing hole 41) to the end portion 28e of the suction hole 28 is set to θ1. As shown in Figure 2 (c), the angle from the center of the throat portion 43 (or the vane housing hole 41) to the front end of the eccentric direction of the roller 22 at which the opening area of the injection port 35 is largest is set to θmax. At this time, the following mathematical formula 1 is established.

[0074] θ1 < θmax < 140°... (1)

[0075] As shown in FIG. 1, θ1 is about 30°. θmax is substantially 90° < θmax < 110°. θmax satisfies the mathematical expression 1. Figure 3

[0076] By θ1 < θmax, the opening area of the injection port 35 becomes maximum after the front end in the eccentric direction of the roller 22 passes the end portion 28e of the suction hole 28. The opening area of the injection port 35 does not become maximum before this, and thus the inflow of the cooling refrigerant to the suction hole 28 can be suppressed.

[0077] By θmax < 140°, the opening area of the injection port 35 becomes maximum before the pressure of the compression chamber 25p is higher than the pressure of the cooling refrigerant of the injection circuit 30 at the time of low load. The opening area of the injection port 35 does not become maximum after this, and thus the inflow of the compressed gas refrigerant to the injection port 35 can be suppressed.

[0078] As described in detail above, in the rotary compressor 2 of the first embodiment, the injection port 35 of the cooling refrigerant is opened and closed by the end surface of the partition member 16 side of the roller 22 and the vane 40.

[0079] The design freedom of the injection port 35 is large. The injection port 35 is not opened to the cylinder chamber 25 after the pressure of the gas refrigerant of the cylinder chamber 25 is higher than the pressure of the cooling refrigerant. The gas refrigerant hardly flows into the injection port 35. The compression performance of the rotary compressor 2 is improved.

[0080] The vane 40 is integrated with the roller 22.

[0081] The swing-type vane 40 opens and closes the injection port 35, and thus the design freedom of the injection port 35 is extremely large. The compression performance of the rotary compressor 2 is improved.

[0082] Since no gap is generated between the vane 40 and the outer peripheral surface of the roller 22, the injection port 35 can be closed without a gap.

[0083] The transition of the injection port 35 from the closed state to the state where the opening area is maximum is performed only by the end surface of the partition member 16 side of the roller 22.

[0084] At the time when the injection port 35 is opened, the pressure of the cooling refrigerant is substantially higher than the pressure of the cylinder chamber 25. The opening of the injection port 35 is performed only by the end surface of the partition member 16 side of the roller 22 for a short time. The pressure loss of the cooling refrigerant can be suppressed, and a sufficient amount of the cooling refrigerant can be injected into the cylinder chamber 25. The cooling performance and the compression performance of the rotary compressor 2 are improved.

[0085] ​In the eccentric rotation direction of the roller 22, the angle from the center of the throat 43 (or the blade receiving hole 41) to the end 28e of the suction hole 28 downstream of the roller 22 in the eccentric rotation direction is defined as θ1. In the eccentric rotation direction of the roller 22, the angle from the center of the throat 43 (or the blade receiving hole 41) to the front end of the roller 22 in the eccentric direction where the opening area of ​​the injection port 35 is maximized is defined as θmax. At this time, θ1 < θmax < 140° holds true.

[0086] By ensuring θ1 < θmax, the inflow of cooling refrigerant into the suction port 28 can be suppressed. By ensuring θmax < 140°, the inflow of compressed gaseous refrigerant into the injection port 35 can be suppressed. The compression performance of the rotary compressor 2 is improved.

[0087] The refrigeration cycle apparatus 1 of the first embodiment includes the rotary compressor 2, radiator 3, expansion device 4, and absorber 5 described above. 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.

[0088] Because of the rotary compressor 2 described above, the performance of the refrigeration cycle device 1 can be improved.

[0089] (Second Implementation)

[0090] The rotary compressor of the second embodiment will be described.

[0091] Figure 5 Is with Figure 1 A cross-sectional view of the portion corresponding to line II-II. The rotary compressor of the second embodiment differs from the oscillating compressor of the first embodiment in that it is a rotary type. Description of the second embodiment, which has the same components as the first embodiment, is omitted.

[0092] The rotary compressor of the second embodiment is a so-called rotary compressor in which the blades 50 and rollers 22 are separate.

[0093] like Figure 5 As shown in (c), the blade 50 is flat. The cylinder 24 has a blade groove 51 as a blade receiving hole, supporting the blade 50 so that it can move in and out of the cylinder chamber 25. The blade 50 is disposed inside the blade groove 51. The blade 50 can move along the blade groove 51 in the X direction. A lubricating oil hole 52 is formed at the end of the blade groove 51 in the -X direction. Lubricating oil from the lubricating oil reservoir 14 is introduced into the lubricating oil hole 52. As described above, the lubricating oil is under discharge pressure. The blade 50 is forced in the +X direction by the lubricating oil in the lubricating oil hole 52. The leading edge of the blade 50 in the +X direction abuts against the outer peripheral surface of the roller 22. The blade 50 moves in and out of the blade groove 51 relative to the cylinder chamber 25 as the roller 22 rotates eccentrically.

[0094] The injection circuit has an injection port 37.

[0095] Inlet 37 is oblong or elliptical in shape. The length of inlet 37 in the X direction is longer than its length in the Y direction. Inlet 37 is formed in the sliding region of the separator 16 relative to the blade 50. Inlet 37 is positioned closer to the compression chamber 25p of the cylinder block chamber 25 than the center of this sliding region in the Y direction. Inlet 37 is positioned on the compression chamber 25p side of the reference line 44 in the Y direction.

[0096] like Figure 5 As shown in (a), when the roller 22 rotates to its maximum eccentricity in the -X direction, the injection port 37 is positioned in the X direction between the inner and outer circumferences of the roller 22. Figure 5 As shown in (c), when the roller 22 rotates to its maximum eccentricity in the +X direction, the injection port 37 is positioned in the X direction between the outer periphery of the roller 22 and the outer periphery of the cylinder chamber 25. As described below, the injection port 37 opens into the cylinder chamber 25 between the tip of the blade 50 and the outer peripheral surface of the roller 22.

[0097] The function of the injection circuit is explained.

[0098] Figure 5 This is an explanatory diagram illustrating the function of the injection circuit, and it is related to... Figure 1 A cross-sectional view of a portion corresponding to line II-II. The injection port 37 is opened and closed by the end face of the roller 22 and the blade 50 in the Z direction. Therefore, the design of the injection port 37 has a relatively large degree of freedom.

[0099] Figure 5 (a) is the moment when θ = 0°. The inlet 37 is closed by the Z-direction end face of the roller 22. The inlet 37 is closest to the inner circumference of the roller 22, but does not open to the inner side of the inner circumference. The inlet 37 satisfies the second requirement. Lubricating oil on the inner side of the inner circumference of the roller 22 is difficult to flow into the inlet 37. This can suppress insufficient lubricating oil in the rotary compressor.

[0100] exist Figure 5 (a) and Figure 5 At the moment between (b), the eccentric front end of roller 22 passes through end 28e of suction hole 28. Inlet 37 is closed by the Z-direction end face of roller 22 until that moment. Inlet 37 satisfies requirement 1.

[0101] Figure 5(b) is the moment when θ = 90°, which is the first half of the compression process in cylinder chamber 25. Inlet 37 opens into cylinder chamber 25 between the tip of blade 50 and the outer circumferential surface of roller 22. Roller 22 rotates eccentrically toward the suction chamber 25s side of reference line 44. The gap between the tip of blade 50 and the outer circumferential surface of roller 22 is larger on the compression chamber 25p side than on the suction chamber 25s side of reference line 44. Inlet 37 is positioned in the Y direction on the compression chamber 25p side of reference line 44. The opening area of ​​inlet 37 into cylinder chamber 25 increases. A sufficient amount of refrigerant for cooling is injected into cylinder chamber 25 through inlet 37.

[0102] Figure 5 (c) is the moment when θ = 180°, which is the latter half of the compression process in cylinder chamber 25. The entire injection inlet 37 is closed by the Z-direction end face of the blade 50.

[0103] Figure 5 (d) is the moment when θ = 270°. Roller 22 rotates eccentrically toward the compression chamber 25p side of reference line 44. The clearance between the tip of blade 50 and the outer circumferential surface of roller 22 is smaller on the compression chamber 25p side than on the suction chamber 25s side of reference line 44. Inlet 37 is positioned in the Y direction on the compression chamber 25p side of reference line 44. Between the tip of blade 50 and the outer circumferential surface of roller 22, the opening area of ​​inlet 37 toward cylinder chamber 25 decreases. The inflow of compressed gaseous refrigerant into the injection circuit from inlet 17 becomes less. Within the range of 180° < θ, inlet 37 is almost closed. Inlet 37 satisfies the third requirement. Under high load, it is difficult for compressed gaseous refrigerant from cylinder chamber 25 to flow into the injection circuit from inlet 37.

[0104] Similar to the first embodiment, in the eccentric rotation direction of the roller 22, the angle from the center of the blade groove 51 to the end 28e of the suction hole 28 is set as θ1. The angle from the center of the blade groove 51 to the front end of the roller 22 in the eccentric direction where the opening area of ​​the injection port 37 is maximized is set as θmax. In this case, θ1 < θmax < 140° holds true.

[0105] As detailed above, in Figure 5 In the rotary compressor of the second embodiment shown in (c), the blades 50 and the rollers 22 are separate. The injection inlet 37 is formed in the region of the partition member 16 that slides relative to the blades 50, at a position closer to the center of the compression chamber 25p in the Y direction. The injection inlet 37 opens into the cylinder chamber 25 between the front end of the blades 50 on the cylinder chamber 25 side and the outer peripheral surface of the rollers 22.

[0106] The injection port 37 has a large degree of freedom in design. In the first half of the compression process, the opening area of the injection port 37 is made 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 is made small, and the compressed gas refrigerant is difficult to flow from the injection port 37 into the injection circuit 30. The compression performance of the rotary compressor is improved.

[0107] The length of the injection port 37 in the X direction is longer than the length in the Y direction.

[0108] By adjusting the length of the injection port 37 in the X direction, the range of the rotation angle θ at which the injection port 37 opens to the cylinder chamber 25 can be adjusted. A sufficient amount of cooling refrigerant is injected into the cylinder chamber 25.

[0109] (3rd Embodiment)

[0110] The rotary compressor of the 3rd embodiment will be described.

[0111] Figure 6 is a partial cross-sectional view of the rotary compressor of the 3rd embodiment. Figure 7 is a cross-sectional view of the VII-VII line of Figure 6 . The 1st compression mechanism portion 20A of Figure 6 is in the state of (b) of Figure 7 , and the 2nd compression mechanism portion 20B is in the state of (d) of Figure 7 .

[0112] As shown in Figure 7 , the rotary compressor of the 3rd embodiment is the same as the 2nd embodiment. As shown in Figure 6 , the 3rd embodiment differs from the 2nd embodiment in that the injection port 37 is the opening of the 1st recess 61. The description of the 3rd embodiment will be omitted for portions that are the same as the 2nd embodiment.

[0113] The injection circuit has the injection port 37, the 1st recess 61, the 2nd recess 62, the 3rd recess 63, the distribution flow path 64, and the pipe 32. Hereinafter, the injection port 37, the 1st recess 61, the 2nd recess 62, and the 3rd recess 63 formed on the 1st compression mechanism portion 20A side will be described, but these components are also formed identically on the 2nd compression mechanism portion 20B side.

[0114] The injection port 37 is the opening of the 1st recess 61.

[0115] The 1st recess 61 is formed on the end surface of the partition member 16 on the 1st compression mechanism portion 20A side.

[0116] A second recess 62 is formed in an end surface of the vane 50 on the partition member 16 side. An opening of the second recess 62 is closed by the partition member 16. The second recess 62 extends in the X direction from a central portion of the vane 50 toward an end portion in the +X direction. An end portion in the +X direction of the second recess 62 is communicable with the first recess 61.

[0117] A third recess 63 is formed in an end surface of the partition member 16 on the first compression mechanism portion 20A side. An opening of the third recess 63 is closed by the cylinder block 24 of the first compression mechanism portion 20A. As shown in (a) of FIG. 6, the third recess 63 extends in the Y direction. An end portion of the third recess 63 opens toward the vane groove 51 formed in the cylinder block 24. Figure 7

[0118] A pipe 32 extends from the outside to the inside of the housing 11. The pipe 32 is disposed in the cylinder block 24 of the first compression mechanism portion 20A.

[0119] As shown in (a) of FIG. 6, the distribution flow path 64 extends from a front end of the pipe 32 toward the -Z direction. The distribution flow path 64 is communicable with the third recess 63 formed in the partition member 16 on the first compression mechanism portion 20A side. The distribution flow path 64 penetrates the partition member 16 in the Z direction. The distribution flow path 64 is communicable with the third recess 63 formed in the partition member 16 on the second compression mechanism portion 20B side. Figure 6

[0120] An effect of the injection circuit will be described.

[0121] Figure 7 is a cross-sectional view of the VII-VII line of Figure 6 .

[0122] Figure 7 (a) of FIG. 6 is a time when θ = 0°. The vane 50 is moved most in the -X direction. An end portion in the +X direction of the second recess 62 is not communicable with the first recess 61. The injection port 37 is closed by an end surface in the Z direction of the roller 22. Cooling refrigerant is not injected from the injection port 37 to the cylinder chamber 25.

[0123] Figure 7 (b) of FIG. 6 is a time when θ = 90°. The vane 50 is moved in the +X direction. An end portion in the -X direction of the second recess 62 is communicable with the third recess 63, and an end portion in the +X direction is communicable with the first recess 61. The pipe 32, the distribution flow path 64, the third recess 63, the second recess 62, the first recess 61, and the injection port 37 are sequentially communicable. Between a front end of the vane 50 and an outer peripheral surface of the roller 22, the injection port 37 opens to the cylinder chamber 25. Cooling refrigerant is injected from the injection port 37 to the cylinder chamber 25.

[0124] Figure 7 ​​(c) is the time when θ = 180°. The vane 50 is moved to the maximum in the +X direction. The -X direction end of the 2nd recess 62 is not communicated with the 3rd recess 63. The injection port 37 is closed by the Z direction end surface of the vane 50. The cooling refrigerant is not injected from the injection port 37 to the cylinder chamber 25.

[0125] Figure 6 (d) is the time when θ = 270°. The vane 50 is moved in the -X direction. The -X direction end of the 2nd recess 62 is communicated with the 3rd recess 63, and the +X direction end is communicated with the 1st recess 61. As in the 2nd embodiment, the opening area of the injection port 37 to the cylinder chamber 25 is small between the front end of the vane 50 and the outer peripheral surface of the roller 22. The inflow of the compressed gas refrigerant from the injection port 17 to the injection circuit is reduced.

[0126] In the 3rd embodiment, as in the 2nd embodiment, the cooling refrigerant is intermittently injected from the injection port 37 to the cylinder chamber 25.

[0127] As described in detail above, in the 3rd embodiment of the rotary compressor shown in ​ In the 3rd embodiment of the rotary compressor shown in

[0128] The injection circuit can be configured to the cylinder 24, instead of 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.

[0129] In the above embodiments, the rotary compressor 2 has two compression mechanism portions 20 (the 1st compression mechanism portion 20A and the 2nd compression mechanism portion 20B). In contrast, the rotary compressor 2 can have only one compression mechanism portion 20, or three or more compression mechanism portions 20.

[0130] In addition, in the above embodiments, the rotary compressor that cools the compression mechanism portion by injecting the liquid refrigerant is described, but the rotary compressor that injects the gas refrigerant of the intermediate pressure can be provided. Thus, the rotary compressor that suppresses the reduction of the reliability, improves the energy saving, and increases the refrigeration and heating capacity can be formed.

[0131] According to at least one of the above embodiments, the injection port 35, 37 is opened and closed by the Z direction end surface of the partition member 16 of the roller 22 and the vanes 40, 50. Thus, the compression performance of the rotary compressor can be improved.

[0132] The refrigeration cycle apparatus 1 is not limited to one using the rotary compressor 2 of the present embodiment. In the rotary compressor 2 of the above-described embodiment, the configuration using two cylinders is described, but it is not limited thereto. The number of cylinders can be one or more than three.

[0133] Further, the first bearing 17A or the second bearing 17B can be provided as a closed member, and the injection ports 35, 37 can be provided in the first bearing 17A or the second bearing 17B.

[0134] The embodiments of the present application are described, but these embodiments are suggested as examples, and are not intended to limit the scope of the application. These embodiments can be implemented in other various ways, and various omissions, substitutions, and changes can be made within the scope of the gist of the application. These embodiments and modifications are included in the scope and gist of the application, and are included in the application described in the technical scope and the range equivalent thereto.

Claims

1. A rotary compressor, wherein, It has a housing that internally houses the shaft and the compression mechanism. The above-mentioned compression mechanism has: An eccentric portion is provided on the aforementioned shaft; The cylinder block has a cylinder block chamber for the aforementioned eccentric portion; The roller is cylindrical and is externally embedded in the aforementioned eccentric portion, rotating eccentrically within the aforementioned cylinder chamber. The blades move forward and backward in sync with the eccentric rotation of the rollers, dividing the cylinder chamber into the refrigerant suction chamber and the compression chamber in the first state. A sealing component that seals the end of the cylinder chamber axially along the aforementioned shaft; and An injection inlet, formed in the aforementioned sealed component, opens into the aforementioned cylinder chamber, through which refrigerant in its second state, introduced from outside the aforementioned housing, is injected into the aforementioned cylinder chamber. The aforementioned injection port is opened and closed by the end face of the aforementioned roller and the aforementioned sealing component side of the aforementioned blade. The aforementioned blade and roller are separate parts, and can move along the blade groove formed in the cylinder in the first direction. The front end of the cylinder chamber side in the first direction abuts against the outer peripheral surface of the roller. The aforementioned injection port is formed in the region of the aforementioned sealing component that slides relative to the aforementioned blade, at a position closer to the center of the aforementioned compression chamber than the center of the second direction, which is orthogonal to the aforementioned axial direction and the aforementioned first direction. The aforementioned injection port opens into the cylinder chamber between the front end of the aforementioned blade on the cylinder chamber side and the outer peripheral surface of the aforementioned roller. The aforementioned injection port is an opening formed in the first recess of the aforementioned sealing member. The blade has a second recess on the end face of the closed component side that can communicate with the first recess.

2. The rotary compressor according to claim 1, wherein, The length of the injection port in the first direction is longer than the length in the second direction.

3. The rotary compressor according to claim 1 or 2, wherein, The aforementioned blades move in and out of the blade receiving holes formed in the cylinder relative to the cylinder chamber as the rollers rotate eccentrically. The cylinder block has a suction port for drawing in the refrigerant in the first state into the cylinder block chamber. When the angle from the center of the blade receiving hole to the end of the suction hole downstream of the roller in the eccentric rotation direction is defined as θ1, In the eccentric rotation direction of the roller, when the angle at the front end of the roller in the eccentric direction from the center of the blade receiving hole to the opening area of ​​the injection port is maximized is set as θmax, The condition θ1 < θmax < 140° holds true.

4. A refrigeration cycle device, comprising: The rotary compressor according to any one of claims 1 to 3; A radiator, connected to the aforementioned rotary compressor; An expansion device, connected to the aforementioned radiator; and A heat absorber is connected between the expansion device and the rotary compressor.

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