Compressors and refrigeration cycle systems

Abstract

To provide a compressor equipped with an injection mechanism that can improve reliability by suppressing the decrease in cooling efficiency at a low cost. [Solution] The compressor comprises a plurality of cylinders, a rotating shaft, a plurality of rollers, and a plurality of blades. Each blade of the plurality of cylinders has a blade groove formed in the shape of a groove on the side surface facing the compression chamber, among the side surfaces that face the circumferential direction with respect to the axis of the rotating shaft in pairs. Each blade hole of the plurality of cylinders has an injection hole that opens in the wall opposite the side surface of the blade facing the compression chamber, so as to be able to communicate with the blade groove. In each of the plurality of cylinders, the injection hole and the compression chamber transition between an injection open state, where they communicate via the blade groove, and an injection closed state, where they do not communicate. The plurality of cylinders can be in either all injection closed state, or one injection open state and the others injection closed state.

Description

Technical Field

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

Background Art

[0002] A refrigeration cycle apparatus such as an air conditioner mainly includes a compressor, a condenser, an expansion valve, and an evaporator. The compressor mainly includes, for example, an electric motor unit that rotates a rotating shaft, a compression mechanism unit connected to the electric motor unit via the rotating shaft, and a sealed container that houses the electric motor unit and the compression mechanism unit. The electric motor unit includes, for example, a so-called inner rotor type motor, and includes a rotor fixed to the rotating shaft and a stator fixed to the inner peripheral portion of the sealed container. The rotating shaft has a crank pin portion (eccentric portion). The compression mechanism unit includes, for example, a cylinder that forms a cylinder chamber, and a roller that is fitted to the eccentric portion of the rotating shaft and eccentrically rotates in the cylinder chamber. The inside of the cylinder chamber is partitioned into a refrigerant suction chamber and a compression chamber by a blade. The rotating shaft is rotatably supported by a bearing disposed in the compression mechanism unit.

[0003] For example, during heating operation or warming operation, an air conditioner absorbs heat from the outside air in the evaporator and supplies the heat to indoor air or hot water in the condenser. At this time, as the outside air temperature rises, the amount of heat absorbed by the evaporator increases, and the temperature and pressure of the refrigerant sucked into the compressor rise. As a result, if the compressor becomes overheated, the temperature of the discharged refrigerant of the compressor may rise excessively. Therefore, as a countermeasure for suppressing such a temperature rise of the compressor, a compressor provided with an injection mechanism is known.

[0004] An injection mechanism has a flow path (injection flow path) that branches the refrigerant, for example, downstream of the condenser in the refrigerant circulation path. The injection flow path is connected to the compressor's compression chamber via connecting pipes or passages formed in the compression mechanism. With such an injection mechanism, a portion of the refrigerant that has passed through the condenser, for example, liquid phase refrigerant or gas-liquid two-phase refrigerant, is injected into the compression chamber, and the gas phase refrigerant drawn into the suction chamber is cooled by this refrigerant. As a result, overheating of the compressor is suppressed.

[0005] Known injection mechanisms include those that open and close injection ports using roller end faces that rotate eccentrically within the compression chamber, and those that incorporate operating mechanisms such as injection pistons and valves in the cylinder to control timing. However, in devices where the injection port is opened and closed at the roller end face, depending on the location where liquid-phase refrigerant or gas-liquid two-phase refrigerant is injected into the compression chamber, there is a risk that the compression chamber and the suction chamber may communicate within the cylinder chamber via the injection mechanism. This can cause re-expansion losses and lead to a decrease in compressor efficiency. Furthermore, if operating mechanisms such as injection pistons and valve mechanisms are provided, the number of parts increases, resulting in a complex structure and increased manufacturing costs. In addition, the increased number of operating parts may increase the risk of failure and lead to a decrease in reliability. If the compressor has multiple cylinders, depending on the path within each cylinder of the injection flow path, there is a risk that the compression chambers of these cylinders may communicate with each other via the injection mechanism. If such communication occurs, it may reduce the cooling effect of the compressor. [Prior art documents] [Patent Documents]

[0006] [Patent Document 1] Japanese Patent Publication No. 2004-324652 [Patent Document 2] Japanese Patent Publication No. 2012-57568 [Patent Document 3] International Publication No. 2020 / 213080 [Overview of the project] [Problems that the invention aims to solve]

[0007] The present invention was made based on this, and its objective is to provide a compressor equipped with an injection mechanism that can improve the reliability of the compressor and refrigeration cycle by suppressing the decrease in the cooling effect of the compressor at a low cost. [Means for solving the problem]

[0008] According to the embodiment, the compressor comprises a plurality of cylinders, a rotating shaft, a plurality of rollers, and a plurality of blades. The plurality of cylinders are annular in shape and each forms a cylinder chamber having a suction chamber for drawing in refrigerant and a compression chamber for compressing the refrigerant. The rotating shaft has a plurality of eccentric portions, one of which are arranged in each of the cylinder chambers of the plurality of cylinders. The plurality of rollers are fitted one by one to each of the plurality of eccentric portions and rotate eccentrically within the cylinder chamber with respect to the axis of the rotating shaft. Each of the plurality of blades is substantially flat and moves back and forth within the cylinder chamber in accordance with the eccentric rotation of each of the plurality of rollers, dividing the cylinder chamber into the suction chamber and the compression chamber. Each of the plurality of cylinders has a blade hole that opens on its inner circumference and extends radially outward to accommodate the blade. Each of the plurality of cylinders has a blade groove formed in a groove shape on the side surface facing the compression chamber, among the side surfaces facing the circumferential direction with respect to the axis of the rotating shaft, in pairs. Each of the plurality of cylinders has an injection hole in the wall portion of the blade facing the surface portion of the blade that faces the compression chamber, which opens to communicate with the blade groove. In each of the plurality of cylinders, the injection hole and the compression chamber transition between an injection open state, where they communicate via the blade groove, and an injection closed state, where they do not communicate. The plurality of cylinders may be all in the injection closed state, or one in the injection open state and the others in the injection closed state. [Brief explanation of the drawing]

[0009] [Figure 1] This is a schematic circuit diagram showing the configuration of an air conditioner according to the first embodiment. [Figure 2] This is a longitudinal cross-sectional view of a compressor according to the first embodiment. [Figure 3] This is a longitudinal cross-sectional view showing a schematic enlargement of a portion of the compressor shown in Figure 2. [Figure 4] This diagram schematically shows the compression mechanism of the compressor according to the first embodiment, viewed from above. [Figure 5] This diagram schematically shows the positional relationship between the blade groove and the spring insertion hole when the blade is in its most retracted state relative to the cylinder chamber in the first embodiment. [Figure 6A] Figure 1 schematically shows the state transitions of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment. [Figure 6B] Figure 2 schematically shows the state transitions of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment. [Figure 6C] Figure 3 schematically shows the state transitions of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment. [Figure 6D] Figure 4 schematically shows the state transitions of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment. [Figure 6E] Figure 5 schematically shows the state transitions of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment. [Figure 6F] Figure 6 schematically shows the state transitions of the injection mechanism in the cylinder during the refrigerant compression process in the first embodiment. [Figure 7A]In the first embodiment, this is a diagram showing the transition between an injection - possible state (injection - open state) where the injection hole and the compression chamber communicate via the blade groove and an injection - impossible state (injection - closed state) where they do not communicate, for each cylinder according to the rotation angle. [Figure 7B] This is a diagram showing the transition between the injection - open state and the injection - closed state for each cylinder according to the rotation angle when there are three cylinders. [Figure 8] This is a longitudinal sectional view schematically enlarging a part of the compressor according to the second embodiment. [Figure 9] This is a diagram schematically showing the blade according to the second embodiment from the circumferential direction. [Figure 10A] In the second embodiment, this is the first diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process. [Figure 10B] In the second embodiment, this is the second diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process. [Figure 10C] In the second embodiment, this is the third diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process. [Figure 10D] In the second embodiment, this is the fourth diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process. [Figure 10E] In the second embodiment, this is the fifth diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process. [Figure 10F] In the second embodiment, this is the sixth diagram schematically showing the state transition of the injection mechanism in the cylinder during the refrigerant compression process. [Figure 11] In the second embodiment, this is a diagram showing the locus of the relationship between the rotation angle, the compression load ratio, and the groove cross - sectional area ratio. [Figure 12] In the second embodiment, this is a diagram showing the relationship between the injection state, the rotation angle, and the groove cross - sectional area ratio. [Figure 13] It is a longitudinal sectional view schematically enlarging a part of a compressor according to a third embodiment. [Figure 14] It is a view schematically showing a blade according to a third embodiment from the circumferential direction. [Figure 15A] In a third embodiment, it is a first diagram schematically showing the state transition of an injection mechanism in a cylinder in a refrigerant compression process. [Figure 15B] In a third embodiment, it is a second diagram schematically showing the state transition of an injection mechanism in a cylinder in a refrigerant compression process. [Figure 15C] In a third embodiment, it is a third diagram schematically showing the state transition of an injection mechanism in a cylinder in a refrigerant compression process. [Figure 15D] In a third embodiment, it is a fourth diagram schematically showing the state transition of an injection mechanism in a cylinder in a refrigerant compression process. [Figure 15E] In a third embodiment, it is a fifth diagram schematically showing the state transition of an injection mechanism in a cylinder in a refrigerant compression process. [Figure 15F] In a third embodiment, it is a sixth diagram schematically showing the state transition of an injection mechanism in a cylinder in a refrigerant compression process. [Figure 16] It is a diagram showing the relationship between an injection state, a rotation angle, and a groove cross-sectional area ratio in a third embodiment.

MODE FOR CARRYING OUT THE INVENTION

[0010] (First Embodiment) FIG. 1 is a refrigeration cycle circuit diagram of an air conditioner 1 according to the present embodiment. The air conditioner 1 is a device that performs air conditioning by such a refrigeration cycle and is an example of a refrigeration cycle device. The air conditioner 1 mainly includes a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, an outdoor blower 400, an expansion device 5, an indoor heat exchanger 6, and an indoor blower 600.

[0011] As shown in Figure 1, the discharge side of the compressor 2 is connected to the first port 3a of the four-way valve 3. The second port 3b of the four-way valve 3 is connected to the outdoor heat exchanger 4. The outdoor heat exchanger 4 is connected to the indoor heat exchanger 6 via the expansion device 5. The indoor heat exchanger 6 is connected to the third port 3c of the four-way valve 3. The fourth port 3d of the four-way valve 3 is connected to the suction side of the compressor 2 via the accumulator 8.

[0012] The refrigerant circulates through a circulation circuit 7 from the discharge side of the compressor 2, via the outdoor heat exchanger 4, expansion device 5, indoor heat exchanger 6, and accumulator 8, to the suction side. As the refrigerant, a chlorine-free refrigerant is preferred, and applicable examples include R32, R448A, R449A, R449B, R407G, R407H, R449C, R454A, R454B, R454C, R456A, R516A, R460B, R463A, R744, and HC-based refrigerants.

[0013] For example, when the air conditioner 1 operates in cooling mode, the four-way valve 3 switches so that the first port 3a communicates with the second port 3b, and the third port 3c communicates with the fourth port 3d. When the air conditioner 1 starts operating in cooling mode, the high-temperature, high-pressure gaseous refrigerant compressed by the compressor 2 is discharged into the circulation circuit 7. The discharged gaseous refrigerant is guided through the four-way valve 3 to the outdoor heat exchanger 4, which functions as a condenser (heat radiator).

[0014] The gaseous refrigerant introduced into the outdoor heat exchanger 4 condenses through heat exchange with the air (outside air) drawn in by the outdoor fan 400, changing into a high-pressure liquid-phase refrigerant. The high-pressure liquid-phase refrigerant is reduced in pressure as it passes through the expansion device 5, changing into a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is introduced into the indoor heat exchanger 6, which functions as an evaporator (heat absorber), and also exchanges heat with the air (inside air) drawn in by the indoor fan 600 as it passes through the indoor heat exchanger 6.

[0015] As a result, the two-phase gaseous refrigerant absorbs heat from the air and evaporates, changing into a low-temperature, low-pressure gaseous refrigerant. The air passing through the indoor heat exchanger 6 is cooled by the latent heat of vaporization of the liquid-phase refrigerant and sent as cool air to the areas that need air conditioning (cooling) by the indoor blower 600.

[0016] The low-temperature, low-pressure gaseous refrigerant that has passed through the indoor heat exchanger 6 is guided to the accumulator 8 via the four-way valve 3. If any liquid refrigerant that has not evaporated is mixed in with the refrigerant, it is separated into liquid and gaseous refrigerant here. The low-temperature, low-pressure gaseous refrigerant separated from the liquid refrigerant is drawn from the accumulator 8 to the compressor 2, where it is compressed again into high-temperature, high-pressure gaseous refrigerant and discharged into the circulation circuit 7.

[0017] On the other hand, when the air conditioner 1 operates in heating mode, the four-way valve 3 switches so that the first port 3a communicates with the third port 3c and the second port 3b communicates with the fourth port 3d. When the air conditioner 1 starts operating in heating mode, the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 2 is guided to the indoor heat exchanger 6 via the four-way valve 3 and undergoes heat exchange with the air passing through the indoor heat exchanger 6. In this case, the indoor heat exchanger 6 functions as a condenser.

[0018] As a result, the gaseous refrigerant passing through the indoor heat exchanger 6 condenses by exchanging heat with the air (indoor air) drawn in by the indoor blower 600, and changes into a high-pressure liquid refrigerant. The air passing through the indoor heat exchanger 6 is heated by the heat exchange with the gaseous refrigerant and sent as warm air to the areas that need air conditioning (heating) by the indoor blower 600.

[0019] The high-temperature liquid-phase refrigerant that has passed through the indoor heat exchanger 6 is led to the expansion device 5, and as it passes through the expansion device 5, it is depressurized and changed into a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is led to the outdoor heat exchanger 4, which functions as an evaporator, and evaporates by exchanging heat with the air (outside air) drawn in by the outdoor fan 400, changing into a low-temperature, low-pressure gas-phase refrigerant. The low-temperature, low-pressure gas-phase refrigerant that has passed through the outdoor heat exchanger 4 is drawn into the compressor 2 via the four-way valve 3 and the accumulator 8, and is compressed again into a high-temperature, high-pressure gas-phase refrigerant in the compressor 2 and discharged into the circulation circuit 7.

[0020] In this embodiment, the air conditioner 1 is capable of operating in either cooling mode or heating mode. However, the air conditioner 1 may also be a cooling-only unit or a heating-only unit that can operate in either cooling mode or heating mode only.

[0021] Furthermore, in this embodiment, the circulation circuit 7 is equipped with a flow path (hereinafter referred to as the injection flow path) 7a that branches the refrigerant downstream of the condenser. The injection flow path 7a is a bypass path (injection path) that branches off a portion of the refrigerant flowing from the condenser to the evaporator (hereinafter referred to as the injected refrigerant) downstream of the condenser and upstream of the evaporator and leads it to the compressor 2 (specifically the compression chambers 23b and 24b described later). The injected refrigerant is, for example, a liquid-phase refrigerant or a gas-liquid two-phase refrigerant. In the example shown in Figure 1, the injection flow path 7a is branched between the outdoor heat exchanger 4 and the expansion device 5 and connected to the compressor 2 via a connecting pipe 7b. The injection flow path 7a may have, for example, a solenoid valve, an expansion valve, a check valve, etc. (all not shown) along its path. By providing such an injection channel 7a, the injected refrigerant is injected into the compression chambers 23b and 24b of cylinders 13 and 14 of the compressor 2, which will be described later, and the high-temperature gaseous refrigerant drawn into the compressor 2 is cooled by the injected refrigerant. This prevents the compressor 2 from overheating.

[0022] Next, the specific configuration of the compressor 2 used in the air conditioner 1 will be described with reference to Figure 2. Figure 2 is a schematic longitudinal cross-sectional view of the compressor 2. Figure 3 is a schematic enlarged longitudinal cross-sectional view of a part of the compressor 2 shown in Figure 2. As shown in Figures 2 and 3, the compressor 2 is a so-called vertical rotary compressor, and its main elements are a sealed container 10, a compression mechanism 11, and an electric motor 12. In the following description, the side where the compression mechanism 11 is located will be considered the bottom and the side where the electric motor 12 is located will be considered the top, based on the relative positional relationship of the compression mechanism 11 and the electric motor 12, which are aligned along the central axis O1 of the sealed container 10, which will be described later.

[0023] The sealed container 10 has a cylindrical peripheral wall 10a and stands perpendicular to the installation surface. The installation surface is, for example, the bottom plate of an outdoor unit. A discharge pipe 10b is provided at the upper end of the sealed container 10. The discharge pipe 10b is connected to the first port 3a of the four-way valve 3 via a circulation circuit 7. An oil reservoir 10c for storing lubricating oil is provided at the lower part of the sealed container 10.

[0024] The compression mechanism 11 is a mechanism for compressing the refrigerant. The compression mechanism 11 is housed in the lower part of the sealed container 10 so as to be immersed in lubricating oil. In the example shown in Figure 2, the compression mechanism 11 has a twin-cylinder structure and mainly comprises a first cylinder 13, a second cylinder 14, and a rotating shaft 15. The first cylinder 13 and the second cylinder 14 are annular in shape and form cylinder chambers 23 and 24, which have suction ports 23c and 24c for drawing in the refrigerant and discharge ports for discharging the compressed refrigerant, as will be described later. The first cylinder 13 and the second cylinder 14 each have rollers (rolling pistons) 16 and 17 and blades 18 and 19 inside. Note that the number of cylinders in the compression mechanism is not limited to two, but may be one or three or more.

[0025] The first cylinder 13 is fixed to the inner surface of the peripheral wall 10a of the sealed container 10 via a first bearing 21 or a frame. The second cylinder 14 is fixed to the lower surface of the first cylinder 13 via a partition plate 20.

[0026] A first bearing 21 is fixed above the first cylinder 13. The first bearing 21 covers the inner diameter of the first cylinder 13 from above and protrudes upward toward the first cylinder 13. The space enclosed by the inner diameter of the first cylinder 13, the partition plate 20, and the first bearing 21 constitutes the first cylinder chamber 23. The partition plate 20 corresponds to a closing member that defines the lower surface of the first cylinder chamber 23, and the first bearing 21 corresponds to a closing member that defines the upper surface of the first cylinder chamber 23.

[0027] A second bearing 22 is fixed below the second cylinder 14. The second bearing 22 covers the inner diameter of the second cylinder 14 from below and protrudes downward toward the second cylinder 14. The space enclosed by the inner diameter of the second cylinder 14, the partition plate 20, and the second bearing 22 constitutes the second cylinder chamber 24. The partition plate 20 corresponds to a closing member that defines the upper surface of the second cylinder chamber 24, and the second bearing 22 corresponds to a closing member that defines the lower surface of the second cylinder chamber 24. The first cylinder chamber 23 and the second cylinder chamber 24 are arranged concentrically with the central axis O1 of the sealed container 10.

[0028] The first cylinder chamber 23 and the second cylinder chamber 24 are connected to the accumulator 8 via suction pipes 10d and 10e, which are part of the circulation circuit 7. The gaseous refrigerant, separated from the liquid phase refrigerant in the accumulator 8, is guided through these suction pipes 10d and 10e to the first cylinder chamber 23 and the second cylinder chamber 24 from the suction ports 23c and 24c.

[0029] The rotating shaft 15 has its axis coaxial with the central axis O1 of the sealed container 10 and penetrates the first cylinder chamber 23, the second cylinder chamber 24, and the partition plate 20. The rotating shaft 15 has a first journal portion 27a, a second journal portion 27b, and a pair of crankpin portions (eccentric portions) 28a, 28b. In other words, the rotating shaft 15 is configured as a crankshaft. The first journal portion 27a is rotatably supported by a first bearing 21. The second journal portion 27b is rotatably supported by a second bearing 22.

[0030] Furthermore, the rotating shaft 15 has an extension 27c that extends coaxially from the first journal portion 27a. The extension 27c passes through the first bearing 21 and protrudes above the compression mechanism portion 11. The rotor 33 of the electric motor portion 12, which will be described later, is fixed to the extension 27c.

[0031] The eccentric portions 28a and 28b are located between the first journal portion 27a and the second journal portion 27b. The eccentric portions 28a and 28b are equally spaced in the circumferential direction with, for example, a phase difference of 180 degrees, and their eccentricity with respect to the central axis O1 of the sealed container 10 is the same. One eccentric portion (hereinafter referred to as the first eccentric portion) 28a is located in the first cylinder chamber 23. The other eccentric portion (hereinafter referred to as the second eccentric portion) 28b is located in the second cylinder chamber 24.

[0032] Figure 4 is a schematic diagram showing the compression mechanism 11 from above. Figure 4 shows the internal configuration of the first cylinder 13. The internal configurations of the first cylinder 13 and the second cylinder 14 are substantially the same, except for parts that differ according to the phase difference between the first eccentric portion 28a and the second eccentric portion 28b. Therefore, the internal configuration of the second cylinder 14 is similar to the configuration shown in Figure 4.

[0033] As shown in Figures 3 and 4, the cylindrical first roller 16 is fitted onto the outer circumferential surface 29a of the first eccentric portion 28a. A small gap is provided between the inner circumferential surface 16a of the first roller 16 and the outer circumferential surface 29a of the first eccentric portion 28a, allowing the first roller 16 to rotate relative to the first eccentric portion 28a. As a result, when the rotating shaft 15 rotates, the first roller 16 rotates eccentrically with respect to the axis (central axis O1) of the rotating shaft 15 within the first cylinder chamber 23, and a part of the outer circumferential surface 16b of the first roller 16 comes into contact with the inner circumferential surface of the first cylinder chamber 23.

[0034] The cylindrical second roller 17 is fitted onto the outer circumferential surface 29b of the second eccentric portion 28b. A small gap is provided between the inner circumferential surface 17a of the second roller 17 and the outer circumferential surface 29b of the second eccentric portion 28b, allowing the second roller 17 to rotate relative to the second eccentric portion 28b. As a result, when the rotating shaft 15 rotates, the second roller 17 rotates eccentrically with respect to the axis (central axis O1) of the rotating shaft 15 within the second cylinder chamber 24, and a portion of the outer circumferential surface 17b of the second roller 17 comes into contact with the inner circumferential surface of the second cylinder chamber 24.

[0035] As shown in Figures 3 and 4, a first blade 18 is positioned in the first cylinder 13, and a second blade 19 is positioned in the second cylinder 14. The first blade 18 and the second blade 19 are substantially flattened. The cylinders 13 and 14 have blade holes 13a and 14a that open on the inner circumference and extend radially outward to accommodate the blades 18 and 19. The first blade 18 is supported in the first blade hole 13a, biased radially inward by a spring 13b. Similarly, the second blade 19 is supported in the second blade hole 14a, biased radially inward by a spring 14b. The springs 13b and 14b are positioned in the spring insertion holes 13c and 14c of the cylinders 13 and 14, and press the blades 18 and 19 toward the rollers 16 and 17 in the blade holes 13a and 14a. The spring insertion holes 13c and 14c are spaces formed between the blade holes 13a and 14a and the outer circumferential surfaces of the cylinders 13 and 14, and are in the internal space of the sealed container 10, communicating with the outside of the cylinders 13 and 14. The tips 18a and 19a of each blade 18 and 19 are pressed against the outer circumferential surfaces 16b and 17b of the rollers 16 and 17 by the pressing force of the springs 13b and 14b. These blades 18 and 19 work together with the rollers 16 and 17 to divide the cylinder chambers 23 and 24 into suction chambers 23a and 24a and compression chambers 23b and 24b, respectively, and move in the direction of entering (advancing) into the cylinder chambers 23 and 24, or exiting (retreating) from the cylinder chambers 23 and 24, that is, they move forward and backward as the rollers 16 and 17 rotate eccentrically. As the blades 18 and 19 move forward and backward relative to the cylinder chambers 23 and 24, the volumes of the suction chambers 23a and 24a and the compression chambers 23b and 24b of the cylinder chambers 23 and 24 change, and the gaseous refrigerant drawn into the cylinder chambers 23 and 24 from the suction pipes 10d and 10e is compressed.

[0036] The high-temperature, high-pressure gaseous refrigerant compressed in the first cylinder chamber 23 and the second cylinder chamber 24 is discharged into the sealed container 10 via a discharge valve mechanism (not shown). The discharged gaseous refrigerant rises inside the sealed container 10. Furthermore, while the compression mechanism 11 is operating, the lubricating oil (refrigerant oil) stored in the oil reservoir 10c of the sealed container 10 is agitated into a mist and rises inside the sealed container 10 towards the discharge pipe 10b, carried by the flow of the gaseous refrigerant.

[0037] The motor unit 12 is a mechanism that drives the compression mechanism unit 11, specifically the rotating shaft 15. The motor unit 12 is housed in the middle section of the sealed container 10 along the central axis O1 so as to be located between the compression mechanism unit 11 and the discharge pipe 10b. The motor unit 12 includes a so-called inner rotor type motor, comprising a rotor 33 fixed to the rotating shaft 15, and a stator 34 fixed to the inner circumferential surface of the peripheral wall 10a of the sealed container 10.

[0038] The rotor 33 is composed of, for example, a cylindrical rotor core fixed coaxially to the rotating shaft 15, and a plurality of permanent magnets arranged on the rotor core. The rotor 33 is arranged coaxially with the stator 34, with a small air gap between them.

[0039] The stator 34 comprises, for example, a cylindrical stator core and windings (coils) wrapped around the stator core, and is arranged to surround the rotor 33. By energizing the coils, the rotor 33 rotates around the central axis O1 relative to the stator 34, and the rotation shaft 15 rotates together with the rotor 33.

[0040] The compressor 2 having this configuration is equipped with an injection mechanism. Therefore, the compression mechanism 11 has a portion of the injection flow path 7a of the circulation circuit 7 as an injection mechanism. The injection mechanism in the compression mechanism 11, specifically in cylinders 13 and 14, will be described in detail below. In this embodiment, as described above, the internal configuration of the first cylinder 13 and the internal configuration of the second cylinder 14 are substantially the same, except for parts that differ according to the phase difference between the first eccentric portion 28a and the second eccentric portion 28b.

[0041] In this embodiment, the injection passage 7a has passages 40, 50, and 60 formed in the compressor 2. These passages 40, 50, and 60 constitute a part of the injection passage 7a in the compressor 2 and guide a portion of the liquid phase refrigerant (injection refrigerant) diverted from the circulation circuit 7 to the compression chambers 23b and 24b of the cylinders 13 and 14. Passage 40 is formed inside the partition plate 20 and connects the connecting pipe 7b to passage 50. Passage 50 is formed inside the cylinders 13 and 14 and connects passage 40 to passage 60. Passage 60 is formed on the side surfaces of the blades 18 and 19 and connects passage 50 to the compression chambers 23b and 24b. Each of the passages 40, 50, and 60 will be described further below.

[0042] The flow path (hereinafter referred to as the injection passage) 40 opens on the outer circumferential surface 20a of the partition plate 20 and extends radially, further extending along the central axis O1 and opening on the upper surface 20b and the lower surface 20c, respectively. The radial direction of the partition plate 20 is in the direction toward the central axis O1 along the normal to the outer circumferential surface 20a. The injected refrigerant flows into the injection passage 40 from the opening 41 on the outer circumferential surface 20a and is guided to the opening 42a on the upper surface 20b and the opening 42b on the lower surface 20c. That is, the injection passage 40 is composed of a partition plate inlet side flow path (lateral flow path) 40a that extends radially and two partition plate outlet side flow paths (vertical flow paths) 40b and 40c that branch vertically from the partition plate inlet side flow path 40a along the central axis O1. The opening 41 is in communication with the connecting pipe 7b. Opening 42a communicates with opening 53 of cylinder 13, which will be described later. Opening 42b communicates with opening 55 of cylinder 14, which will be described later.

[0043] The flow path 50 includes a flow path 51 formed inside the first cylinder 13 (hereinafter referred to as the first cylinder flow path) and a flow path 52 formed inside the second cylinder 14 (hereinafter referred to as the second cylinder flow path).

[0044] The first cylinder passage 51 opens to the lower surface 13d of the first cylinder 13, and the second cylinder passage 52 opens to the upper surface 14d of the second cylinder 14, both extending along the central axis O1. The first and second cylinder passages 51 and 52 then bend in a direction intersecting the central axis O1 and extend further, opening to the side walls 13e and 14e of the first and second blade holes 13a and 14a. The side walls 13e and 14e are the walls on the compression chambers 23b and 24b side of the first and second cylinder chambers 23 and 24, respectively, which are the walls on the discharge side, opposite to the refrigerant suction side (suction chambers 23a and 24a) of the pair of opposing side walls 13e, 13f and 14e, 14f along the circumferential direction of the first and second blade holes 13a and 14a. The side walls 13e and 14e are the wall portions that face the compression chambers 23b and 24b of the blades 18 and 19 (described later) in the first and second blade holes 13a and 14a (side portions 18b and 19b). The injected refrigerant flows into the first and second cylinder passages 51 and 52 from the openings 53 and 54 and is guided to the openings 54 and 56 of the side walls 13e and 14e (hereinafter referred to as injection holes). That is, the first and second cylinder passages 51 and 52 are composed of a continuous inlet side passage (longitudinal passage) 51a and 52a that extends along the central axis O1, and an outlet side passage (lateral passage) 51b and 52b that bends and extends from the inlet side passage 51a and 52a in a direction intersecting the central axis O1. Openings 53 and 55 communicate with openings 42a and 42b of the partition plate outlet side flow paths 40b and 40c of the injection communication passage 40. Injection holes 54 and 56 are capable of communicating with the grooves of the first and second blades 18 and 19, which will be described later.

[0045] The flow path 60 has a flow path 61 formed in the first blade 18 (hereinafter referred to as the first blade groove) and a flow path 62 formed in the second blade 19 (hereinafter referred to as the second blade groove). Both the first blade groove 61 and the second blade groove 62 are formed in a groove shape that extends along the direction in which the blades 18 and 19 move toward and toward the cylinder chambers 23 and 24. The direction in which the blades 18 and 19 move toward and toward the cylinders 13 and 14 is along the radial direction. In this embodiment, the first blade groove 61 and the second blade groove 62 are substantially the same in form. However, the forms of these blade grooves 61 and 62 may be different.

[0046] The first and second blade grooves 61 and 62 are grooves formed on the side portions 18b and 19b of the first and second blades 18 and 19, and extend longitudinally in the direction of advancement and retraction of the first and second blades 18 and 19. The side portions 18b and 19b are the surfaces facing the compression chambers 23b and 24b of the first and second cylinder chambers 23 and 24, which are the surfaces opposite to the refrigerant suction side (suction chambers 23a and 24a) of the first and second cylinder chambers 23 and 24, i.e., the discharge side surfaces. Therefore, the first and second blade grooves 61 and 62 do not communicate with the refrigerant suction ports 23c and 24c from the suction pipes 10d and 10e in the suction chambers 23a and 24a. The injected refrigerant flows into the first and second blade grooves 61 and 62 from near the reversing ends 61a and 62a and is guided to near the advancing ends 61b and 62b. The direction of travel of the first and second blades 18 and 19 toward the cylinder chambers 23 and 24 corresponds to the flow direction of the injected refrigerant in the first and second blade grooves 61 and 62. The reversing ends 61a and 62a are able to communicate with the injection holes 54 and 56 of the first and second cylinder passages 51 and 52. The advancing ends 61b and 62b are able to communicate with the compression chambers 23b and 24b, that is, they are able to be opened toward the compression chambers 23b and 24b.

[0047] Figure 5 schematically shows the positional relationship between the blade grooves 61, 62 and the spring insertion holes 13c, 14c when the blades 18, 19 are in their most retracted state relative to the cylinder chambers 23, 24. As shown in Figures 3 to 5, in this embodiment, the groove cross-sectional area of ​​the first blade groove 61 and the second blade groove 62 is kept approximately constant over the entire length of the groove (the dimension shown as L in Figure 5, hereinafter referred to as groove length L), that is, the entire length in the longitudinal direction. Groove length L is the dimension between the groove ends in the direction of advancement and retraction of the blades 18, 19 in each blade groove 61, 62 (between ends 61a, 62a and ends 61b, 62b). In other words, groove length L is the total length of the groove along the direction in which the blades 18, 19 advance and retract in the blade holes 13a, 14a. The groove cross-sectional area is the area of ​​the cross section perpendicular to the longitudinal direction of each blade groove 61, 62. The longitudinal direction of each blade groove 61, 62 is the same as the direction of movement of the blades 18, 19, that is, the flow direction of the injected refrigerant. Therefore, the larger the groove cross-sectional area, the greater the maximum flow rate of the injected refrigerant in each blade groove 61, 62.

[0048] The groove cross-sectional area is estimated by the groove width and groove depth of the blade grooves 61 and 62. The groove width is the dimension shown as W in Figure 5, and is the distance between opposing groove walls 61c, 62c and groove walls 61d, 62d along the central axis O1 of each blade groove 61 and 62. The groove depth is the dimension shown as D in Figure 4, and is the distance from the side surfaces 18b, 19b of the blades 18 and 19 of each blade groove 61 and 62 to the groove bottom (the continuous surface between groove walls 61c, 62c and groove walls 61d, 62d) 61e, 62e.

[0049] The groove cross-sectional area (W × D) of the first blade groove 61 is set to be less than or equal to the opening area (S1) of the opening (injection hole) 54 of the first cylinder passage 51 (W × D ≤ S1). Similarly, the groove cross-sectional area (W × D) of the second blade groove 62 is set to be less than or equal to the opening area (S2) of the opening (injection hole) 56 of the second cylinder passage 52 (W × D ≤ S2). In this embodiment, the groove cross-sectional area of ​​the first blade groove 61 and the groove cross-sectional area of ​​the second blade groove 62 are set to be approximately equal, but they may be different. Also, the opening area (S1) of the injection hole 54 and the opening area (S2) of the injection hole 56 are set to be approximately equal, but they may be different.

[0050] As described above, the first blade groove 61 and the second blade groove 62, having groove width W, groove depth D, and groove length L, are formed on the side portions 18b and 19b of the blades 18 and 19. The cylinders 13 and 14 have spring insertion holes 13c and 14c where springs 13b and 14b are placed. The blades 18 and 19 are supported in the blade holes 13a and 14a while biased by the springs 13b and 14b. When the blades 18 and 19 are supported in the blade holes 13a and 14a, the side portions 18b and 19b of the blades 18 and 19 are positioned opposite the side walls 13e and 14e of the blade holes 13a and 14a. In other words, in this state, the blade grooves 61 and 62 and the injection holes 54 and 56 are positioned to face each other.

[0051] The first blade groove 61 and the second blade groove 62 are configured to communicate with injection holes 54 and 56 near their retraction-side ends 61a and 62a, and with compression chambers 23b and 24b near their advance-side ends 61b and 62b. In contrast, the first blade groove 61 and the second blade groove 62 are not configured to communicate with spring insertion holes 13c and 14c. That is, within the range in which the blades 18 and 19 move back and forth in the blade holes 13a and 14a, the blade grooves 61 and 62 are configured not to communicate with the spring insertion holes 13c and 14c, meaning they are configured not to open toward the spring insertion holes 13c and 14c.

[0052] The state in which the blades 18 and 19 are most retracted relative to the cylinder chambers 23 and 24 is, for example, when the first eccentric portion 28a (first roller 16) or the second eccentric portion 28b (second roller 17) is at top dead center. In the state in which the blades 18 and 19 are most retracted relative to the cylinder chambers 23 and 24, the positions of the first blade groove 61 and the second blade groove 62, for example, the groove length L, are set so that the retracted ends 61a and 62a do not overlap circumferentially with the spring insertion holes 13c and 14c. As an example, the retracted ends 61a and 62a do not reach the retracted end faces 18d and 19d of the blades 18 and 19, but rather abruptly stop before reaching the end faces 18d and 19d. Therefore, when the blades 18 and 19 are in their most retracted state relative to the cylinder chambers 23 and 24, the retracted ends 61a and 62a are located closer to the axis of rotation 15 (central axis O1) than the spring insertion holes 13c and 14c.

[0053] In this embodiment, the first eccentric portion 28a and the second eccentric portion 28b of the rotating shaft 15, and the first roller 16 and the second roller 17 are arranged on the rotating shaft 15 with a phase difference (β) of 180°. Therefore, the first blade groove 61 and the second blade groove 62 are arranged with a groove length L that allows communication with the injection holes 54, 56 and the compression chambers 23b, 24b, but does not allow communication with the spring insertion holes 13c, 14c, within a range where the rotational phase (angle) of the eccentric portions 28a, 28b of the rotating shaft 15 is less than 180° around the bottom dead center. Furthermore, the first blade groove 61 and the second blade groove 62 are arranged with a groove length L that does not allow communication with the space behind the blade holes 13a, 14a at the top dead center.

[0054] Figures 6A to 6F schematically show the state transitions of the injection mechanism in cylinders 13 and 14 during the refrigerant compression process. The first blade groove 61 and the second blade groove 62 are capable of communicating with the injection holes 54 and 56, i.e., the compression chambers 23b and 24b, within a range where the rotational phase (angle) from the top dead center of the eccentric portions 28a and 28b, i.e., rollers 16 and 17, is less than 180°. The rotational direction of rollers 16 and 17 is indicated by arrow A in Figures 6A to 6F. In the example shown in Figures 6A to 6F, the first blade groove 61 and the second blade groove 62 communicate with the injection holes 54 and 56 and the compression chambers 23b and 24b within a range where the rotational angle (crank angle) from the top dead center of the eccentric portions 28a and 28b (rollers 16 and 17) is between 91° and 269°, i.e., the rotational phase (α) is within a range of 178°. At this time, the injection holes 54, 56 and the compression chambers 23b, 24b are in communication via the blade grooves 61, 62. That is, the rotational phase (α) of the eccentric parts 28a, 28b (rollers 16, 17) into which the injected refrigerant is injected is 178°. Therefore, the injectionable rotational phase (α) is smaller than the equal distribution angle of the eccentric parts 28a, 28b (rollers 16, 17) on the rotation axis 15, i.e., the phase difference (β) (α < β). In other words, the compression chambers 23b, 24b, the blade grooves 61, 62 and the injection holes 54, 56 (in short, the cylinder passages 51, 52) are in communication within an angular range (α) smaller than the equal distribution angle of the eccentric parts 28a, 28b, i.e., the phase difference (β), for the duration of one rotation of the rotation axis 15. Furthermore, the outlet-side passages (lateral passages) 51b and 52b of the first and second cylinder passages 51 and 52 formed in the cylinders 13 and 14 may be constructed, for example, by penetrating from the outer circumferential surface of the cylinder to the side walls 13e and 14e of the blade holes 13a and 14a, and sealing the ends of the outer circumferential surface of the cylinder with pins.

[0055] In this embodiment, the phase difference (β) of the eccentric portions 28a and 28b (rollers 16 and 17) on the rotating shaft 15 is 180°. Therefore, for example, if the position of the first blade 18 when the rotation angle of the eccentric portions 28a and 28b and the rollers 16 and 17 is 0° is taken as the top dead center, then the position of the second blade 19 at that time will be the bottom dead center. Consequently, the injection mechanism in cylinders 13 and 14 will have different injection states at the start depending on this phase difference, but the cycle of state transitions will be the same.

[0056] Figure 7A shows the transition between a state in which the injection holes 54, 56 and the compression chambers 23b, 24b are in communication via blade grooves 61, 62 (injection open state) and a state in which they are not in communication (injection closed state), for each cylinder 13, 14 according to the rotation angles of the eccentric portions 28a, 28b and rollers 16, 17.

[0057] As shown in Figures 6A and 7A, for example, when the rotation angle of the eccentric portion 28a and the roller 16 is 0°, the first blade 18 is positioned at top dead center and is not in communication with either the compression chamber 23b or the injection hole 54. In other words, the compression chamber 23b, or more precisely the first cylinder 13, is in a state where no injection refrigerant is injected (hereinafter referred to as the injection closed state). At this time, the second blade groove 62 is in communication with either the compression chamber 24b or the injection hole 56. In other words, the compression chamber 24b, or more precisely the second cylinder 14, is in a state where injection refrigerant is injected (hereinafter referred to as the injection open state).

[0058] As shown in Figures 6B and 7A, the injection closed state in the first cylinder 13 continues from 0° to a predetermined rotation angle of the eccentric portion 28a and the roller 16. In contrast, the injection open state continues in the second cylinder 14.

[0059] As shown in Figures 6C and 7A, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 91°, the first blade groove 61 communicates with the injection hole 54 and also begins to communicate with the compression chamber 23b. In other words, the first cylinder 13 is in a state where injection refrigerant is injected (injection open state). In contrast, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 90°, the second blade groove 62 is no longer in communication with either the compression chamber 24b or the injection hole 56. In other words, the compression chamber 24b, or more precisely the second cylinder 14, is in a state where injection refrigerant is not injected (injection closed state). Therefore, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 90°, both the first cylinder 13 and the second cylinder 14 are in an injection closed state. Furthermore, even when the rotation angle of the eccentric portion 28a and the roller 16 becomes 91°, the second cylinder 14 continues to remain in the injection closed state.

[0060] As shown in Figures 6D and 7A, when the rotation angle of the eccentric portion 28a and the roller 16 is 180°, the first blade 18 is positioned at the bottom dead center. At this time, the blade groove 61 remains in communication with both the compression chamber 23b and the injection hole 54. That is, the first cylinder 13 remains in the injection open state. The second cylinder 14 remains in the injection closed state.

[0061] As shown in Figures 6E and 7A, the injection open state in the first cylinder 13 continues when the rotation angle of the eccentric portion 28a and the roller 16 is from 180° to a predetermined rotation angle. In contrast, the injection closed state continues in the second cylinder 14.

[0062] As shown in Figures 6F and 7A, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 270°, the first blade groove 61 communicates with the injection hole 54 but not with the compression chamber 23b. In other words, the first cylinder 13 is in an injection-closed state. In contrast, the second cylinder 14 continues to be in an injection-closed state. Therefore, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 270°, both the first cylinder 13 and the second cylinder 14 are in an injection-closed state. Subsequently, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 271°, the first cylinder 13 continues to be in an injection-closed state, but the second cylinder 14 communicates with the injection hole 56 and has also begun to communicate with the compression chamber 24b. In other words, the second cylinder 14 transitions to an injection-open state. When the rotation angle of the eccentric portion 28a and the roller 16 becomes 360° and they complete one rotation, the first cylinder 13 remains in the injection closed state, and the second cylinder 14 remains in the injection open state.

[0063] In other words, during one rotation of the eccentric parts 28a, 28b and rollers 16, 17, there are two instances, specifically when the rotation angles are 90° and 270°, in which case both cylinders 13 and 14 are in the injection closed state. When the rotation angle is otherwise, one of the cylinders 13 or 14 is in the injection closed state, and the other is in the injection open state. Therefore, the first cylinder 13 and the second cylinder 14 do not communicate with each other via the injection mechanism (flow paths 40, 50, 60).

[0064] Thereafter, in the first cylinder 13 and the second cylinder 14, the injection open state and the injection closed state described above are repeated according to the rotation angles of the eccentric portions 28a, 28b and the rollers 16, 17.

[0065] As shown in Figure 7A, for example, when the rotation angle of the eccentric portion 28a and the roller 16 is 449°, both the injection closed state of the first cylinder 13 and the injection open state of the second cylinder 14 continue. Even when the rotation angle becomes 450°, the injection closed state of the first cylinder 13 continues. In contrast, when the rotation angle becomes 450°, the second cylinder 14 transitions to the injection closed state. That is, at this time, both the first cylinder 13 and the second cylinder 14 are in the injection closed state.

[0066] Then, when the rotation angle reaches 451°, the first cylinder 13 transitions to the injection open state. In contrast, the second cylinder 14 continues to be in the injection closed state. Subsequently, at a rotation angle of 629°, both the injection open state of the first cylinder 13 and the injection closed state of the second cylinder 14 continue. When the rotation angle reaches 630°, the first cylinder 13 transitions to the injection closed state. In contrast, even at a rotation angle of 630°, the injection closed state of the second cylinder 14 continues.

[0067] Even when the rotation angle reaches 631° from this state, the injection closed state of the first cylinder 13 continues. In contrast, when the rotation angle reaches 631°, the second cylinder 14 transitions to the injection open state. Subsequently, when the rotation angle reaches 720° and the eccentric parts 28a, 28b and rollers 16, 17 have rotated twice, the injection closed state of the first cylinder 13 continues, and the injection open state of the second cylinder 14 continues.

[0068] In this embodiment, the case where the compressor 2 has two cylinders 13 and 14 (twin cylinder type) has been described, but the number of cylinders is not limited to this. For example, if the compressor has three cylinders, the transition of whether injection is possible or not in each cylinder is as follows. In this case, the rotating shaft has three eccentric parts arranged at equal intervals (phase difference of 120°). These eccentric parts are equipped with rollers that are placed inside each cylinder. When the rotating shaft rotates, these eccentric parts and rollers rotate eccentrically with respect to the rotating shaft with a phase difference of 120°. The three cylinders are equipped with an injection mechanism having a flow path that is substantially equivalent to the flow paths 40, 50, and 60 of the injection mechanism described above. That is, the refrigeration cycle circuit of the air conditioner 1 communicates with the compression mechanism section 11 via the injection flow path 7a and connecting pipe 7b, and within the compression mechanism section 11, it has a flow path that branches and communicates with the first, second, and third cylinders.

[0069] Figure 7B shows examples of transitions between the injection open state and the injection closed state for each cylinder (first cylinder, second cylinder, and third cylinder) when the compressor has three cylinders, depending on the rotation angle of the eccentric part and the rollers. Here, the three eccentric sections are each eccentric at an angle of 120°, and as the rotation axis rotates, the compression process proceeds in the order of the first cylinder, the second cylinder, and the third cylinder.

[0070] In the example shown in Figure 7B, when the rotation angle is 0°, the first cylinder, the second cylinder, and the third cylinder are all in the injection closed state. When the rotation angle becomes 2°, the third cylinder transitions to the injection open state. In contrast, the first and second cylinders remain in the injection closed state. Subsequently, even when the rotation angle becomes 60° and then 118°, the first and second cylinders remain in the injection closed state, while the third cylinder remains in the injection open state.

[0071] When the rotation angle reaches 121°, the third cylinder transitions to the injection closed state. In contrast, the first and second cylinders remain in the injection closed state. That is, at this point, all cylinders are in the injection closed state.

[0072] When the rotation angle reaches 122°, the first cylinder transitions to the injection open state. In contrast, the second and third cylinders remain in the injection closed state. Subsequently, even when the rotation angle reaches 180° and then 238°, the first cylinder remains in the injection open state, while the second and third cylinders remain in the injection closed state.

[0073] When the rotation angle reaches 239°, the first cylinder transitions to the injection closed state. In contrast, the second and third cylinders remain in the injection closed state. In other words, at this point, all cylinders are in the injection closed state.

[0074] When the rotation angle reaches 242°, the second cylinder transitions to the injection open state. In contrast, the first and third cylinders remain in the injection closed state. Subsequently, even when the rotation angle reaches 300° and then 358°, the first and third cylinders remain in the injection closed state, while the second cylinder remains in the injection open state.

[0075] When the rotation angle reaches 359°, the second cylinder transitions to the injection closed state. In contrast, the first and third cylinders remain in the injection closed state. In other words, at this point, all cylinders are in the injection closed state.

[0076] When the rotation angle reaches 362°, the third cylinder transitions to the injection open state. In contrast, the first and second cylinders remain in the injection closed state. Subsequently, even when the rotation angle reaches 420° and then 478°, the first and second cylinders remain in the injection closed state, while the third cylinder remains in the injection open state.

[0077] When the rotation angle reaches 479°, the third cylinder transitions to the injection closed state. In contrast, the first and second cylinders remain in the injection closed state. In other words, at this point, all cylinders are in the injection closed state.

[0078] When the rotation angle reaches 482°, the first cylinder transitions to the injection open state. In contrast, the second and third cylinders remain in the injection closed state. Subsequently, even when the rotation angle reaches 540° and then 598°, the first cylinder remains in the injection open state, while the second and third cylinders remain in the injection closed state.

[0079] When the rotation angle reaches 599°, the first cylinder transitions to the injection closed state. In contrast, the second and third cylinders remain in the injection closed state. That is, at this point, all cylinders are in the injection closed state.

[0080] When the rotation angle reaches 602°, the second cylinder transitions to the injection open state. In contrast, the first and third cylinders remain in the injection closed state. Subsequently, even when the rotation angle reaches 660° and then 718°, the first and third cylinders remain in the injection closed state, while the second cylinder remains in the injection open state.

[0081] When the rotation angle reaches 719°, the second cylinder transitions to the injection closed state. In contrast, the first and third cylinders remain in the injection closed state. That is, at this point, all cylinders are in the injection closed state.

[0082] Furthermore, even when the rotation angle reaches 720°, all cylinders remain in the injection closed state. This state is equivalent to the state when the rotation angle is 0°, and thereafter, each cylinder transitions between the injection open state and the injection closed state as appropriate.

[0083] In other words, except when all cylinders are in the injection closed state, one of the three cylinders is in the injection open state, and the other two are in the injection closed state. Also, at the moment the cylinder in the injection open state switches, all cylinders momentarily become the injection closed state. Therefore, the three cylinders do not communicate with each other via the injection mechanism. As a result, the injected refrigerant does not flow into multiple cylinders simultaneously, and the refrigerant in the injection passage does not flow back between cylinders. In particular, in a structure in which the injection passage is branched within the compression mechanism 11, even if the distance between the injection discharge port opening into the compression chamber and the common part of the multiple injection passages is short, backflow into the injection passage can be prevented with a simple structure with a small number of parts.

[0084] As described above, according to this embodiment, within the range in which the blades 18 and 19 move back and forth in the blade holes 13a and 14a, the blade grooves 61 and 62 are positioned so as not to communicate with the spring insertion holes 13c and 14c, that is, they are positioned so as not to open toward the spring insertion holes 13c and 14c. Therefore, it is possible to prevent the blade grooves 61 and 62 from communicating with the inside of the sealed container 10 filled with lubricating oil (refrigerant oil). As a result, the injection refrigerant can be properly injected into the compression chambers 23b and 24b to cool the compressor 2. Consequently, it is possible to suppress the decrease in the cooling effect of the compressor 2 and improve its reliability.

[0085] Furthermore, in this embodiment, the rotational phase (α) of the injectable eccentric portions 28a, 28b (rollers 16, 17) is smaller than the phase difference (β) of the eccentric portions 28a, 28b (rollers 16, 17) on the rotating shaft 15 (α < β). Therefore, communication between the blade grooves 61, 62, the cylinder passages 51, 52, and the injection communication passage 40 can be suppressed. As a result, communication between the compression chamber 23b of the first cylinder 13 and the compression chamber 24b of the second cylinder 14 can be suppressed via the blade grooves 61, 62, the cylinder passages 51, 52, and the injection communication passage 40. This makes it possible to suppress a decrease in the compression performance of the compressor 2.

[0086] In addition, in this embodiment, the blade grooves 61 and 62 are provided on the side portions 18b and 19b. That is, the blade grooves 61 and 62 are located on the opposite side of the refrigerant suction side (suction chambers 23a and 24a) in the cylinder chambers 23 and 24, i.e., on the discharge side. Therefore, the blade grooves 61 and 62 can not communicate with the refrigerant suction ports 23c and 24c in the suction chambers 23a and 24a. As a result, a decrease in the amount of refrigerant suction caused by communication between the blade grooves 61 and 62 and the suction ports 23c and 24c can be suppressed. Consequently, a decrease in the performance of the compressor 2 can also be suppressed. Furthermore, by creating injection channels that communicate with the blade grooves 61 and 62 provided in the side portions 18b and 19b of the blades 18 and 19 from the side walls 13e and 14e of the first and second blade holes 13a and 14a, the machined surface of the blades 18 and 19 is limited to only a portion of the side portions 18b and 19b. Therefore, there is no need to provide through holes or the like in the blades 18 and 19, and a reduction in the strength of the blades 18 and 19 themselves can be suppressed. Furthermore, although the embodiments described above described compressors with two cylinders and compressors with three cylinders, in either case, the injection passages are not opened to multiple cylinders simultaneously. Moreover, even if a pressure difference occurs due to the misalignment of the compression processes of the multiple cylinders when the intermediate part of the injection circuit communicating with multiple cylinders is common, backflow from each of the multiple cylinders into the injection passages can be prevented. By preventing backflow of refrigerant, performance degradation can be suppressed and a high COP can be maintained.

[0087] (Second embodiment) In the first embodiment described above, the groove cross-sectional area (W × D) of the first blade groove 61 and the second blade groove 62 is approximately constant over the groove length L. However, the groove cross-sectional area of ​​the blade groove is not approximately constant over the groove length and may have multiple parts with different groove cross-sectional areas. Such a groove configuration will be described below as the second embodiment. The basic configuration of the compressor 2a according to the second embodiment is the same as that of the compressor 2 of the first embodiment shown in Figure 2. Therefore, in the second embodiment, for each component of the compressor 2a that is the same as or similar to that of the compressor 2, the configuration of the compressor 2 shown in Figure 2 will be referred to, and the same reference numerals will be used, and the explanation will be omitted. Furthermore, the compressor 2a, like the compressor 2, can be applied as one of the components of the air conditioner 1 (Figure 1) of the first embodiment.

[0088] Figure 8 is a schematic, enlarged longitudinal cross-sectional view of a portion of the compressor 2a. As shown in Figure 8, the first blade groove 63 and the second blade groove 64 in this embodiment have two parts with different groove cross-sectional areas. However, there may be three or more such parts. In this embodiment, the configurations of the first blade groove 63 and the second blade groove 64 are substantially equivalent.

[0089] FIG. 9 is a diagram schematically showing the blades according to the second embodiment from the circumferential direction. As shown in FIGS. 8 and 9, the blade grooves 63, 64 have two portions with different groove cross-sectional areas, a first groove portion 71 and a second groove portion 72. The first groove portion 71 and the second groove portion 72 are continuous in the entire length direction of the blade grooves 63, 64 and constitute the respective blade grooves 63, 64. The first groove portion 71 is disposed on the advancing side in the advancing and retreating direction of the blades 18, 19 into the cylinder chambers 23, 24. The second groove portion 72 is disposed on the retreating side in the advancing and retreating direction of the blades 18, 19 into the cylinder chambers 23, 24. That is, in such an advancing and retreating direction, the first groove portion 71 is closer to the advancing direction than the second groove portion 72, and conversely, the second groove portion 72 is closer to the retreating direction than the first groove portion 71.

[0090] In the present embodiment, the first groove portion 71 and the second groove portion 72 have substantially the same groove depth (groove depth), but different groove widths. Thereby, the first groove portion 71 and the second groove portion 72 have different groove cross-sectional areas. In the example shown in FIGS. 8 and 9, the groove width (dimension indicated by W1 in FIG. 9) of the first groove portion 71 is smaller than the groove width W2 of the second groove portion 72 (W1 < W2). For example, the groove depth of the first groove portion 71 and the second groove portion 72 is equivalent to the groove depth D of the blade grooves 61, 62 of the first embodiment. Also, for example, the groove width W1 of the first groove portion 71 is smaller than the groove width W of the blade grooves 61, 62 of the first embodiment, and the groove width W2 of the second groove portion 72 is larger than the groove width W of the blade grooves 61, 62 of the first embodiment. Therefore, the groove cross-sectional area (W1 × D) of the first groove portion 71 is smaller than the groove cross-sectional area (W × D) of the blade grooves 61, 62, and the groove cross-sectional area (W2 × D) of the second groove portion 72 is larger than the groove cross-sectional area of the blade grooves 61, 62. That is, the blade grooves 63, 64 form a tapered shape in the advancing direction of the blades 18, 19 into the cylinder chambers 23, 24.

[0091] In this embodiment, the groove length of the blade grooves 63 and 64 (the dimension indicated by La in Figure 9) may be the same as or different from the groove length L of the blade grooves 61 and 62 in the first embodiment. For example, the groove length La of the blade grooves 63 and 64 should be set such that, when the blades 18 and 19 are in their most retracted state relative to the cylinder chambers 23 and 24, the retracted end, i.e., the end 72a of the second groove portion 72, does not overlap with the spring insertion holes 13c and 14c in the circumferential direction. In the example shown in Figures 8 and 9, the groove length La of the blade grooves 63 and 64 is set to be the same as the groove length L of the blade grooves 61 and 62.

[0092] Figures 10A to 10F schematically show the state transitions of the injection mechanism in cylinders 13 and 14 during the refrigerant compression process. In this embodiment, the first eccentric portion 28a and the first roller 16 of the first cylinder 13 and the second eccentric portion 28b and the second roller 17 of the second cylinder 14 are positioned on the rotation axis 15 with a phase difference of 180°. Therefore, for example, if the position of the first blade 18 when the rotation angle of the eccentric portions 28a, 28b and rollers 16, 17 is 0° is taken as the top dead center, then the position of the second blade 19 at that time is the bottom dead center. Consequently, although the injection state at the start differs depending on this phase difference, the cycle of state transitions in the injection mechanism of cylinders 13 and 14 is equivalent.

[0093] As shown in Figure 10A, for example, when the rotation angle of the eccentric portion 28a and the roller 16 is 0°, the first blade 18 is positioned at top dead center. At this time, the first blade groove 63 is not in communication with either the compression chamber 23b or the injection hole 54. In other words, the first cylinder 13 is in the injection closed state. At this time, the second blade groove 64 is in communication with either the compression chamber 24b or the injection hole 56. In other words, the second cylinder 14 is in the injection open state.

[0094] As shown in Figure 10B, the injection closed state in the first cylinder 13 continues from 0° to a predetermined rotation angle of the eccentric portion 28a and the roller 16. In contrast, the injection open state continues in the second cylinder 14.

[0095] As shown in Figure 10C, when the rotation angle of the eccentric portion 28a and the roller 16 becomes, for example, 135°, the first blade groove 63 communicates with the injection hole 54 and begins to communicate with the compression chamber 23b. That is, the first cylinder 13 enters the injection open state. At this time, the first blade groove 63 communicates with the compression chamber 23b at the first groove portion 71, but not at the second groove portion 72. In other words, the first blade groove 63 communicates with the compression chamber 23b only at the first groove portion 71, which has a smaller groove cross-sectional area than the second groove portion 72.

[0096] In contrast, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 90°, the second blade groove 64 becomes disconnected from both the compression chamber 24b and the injection hole 56. That is, the second cylinder 14 is in an injection-closed state. Therefore, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 90°, both the first cylinder 13 and the second cylinder 14 are in an injection-closed state. Furthermore, even when the rotation angle of the eccentric portion 28a and the roller 16 reaches 91°, the second cylinder 14 remains in an injection-closed state.

[0097] As shown in Figure 10D, when the rotation angle of the eccentric portion 28a and the roller 16 is 180°, the first blade 18 is positioned at the bottom dead center. At this time, the blade groove 63 continues to communicate with both the compression chamber 23b and the injection hole 54. That is, the first cylinder 13 continues to have the injection open state. At this time, the first blade groove 63 communicates with the compression chamber 23b at the first groove portion 71 and also at the second groove portion 72. The second cylinder 14 continues to have the injection closed state.

[0098] As shown in Figure 10E, the injection open state in the first cylinder 13 continues when the rotation angle of the eccentric portion 28a and the roller 16 is from 180° to a predetermined rotation angle. In contrast, the injection closed state continues in the second cylinder 14.

[0099] As shown in Figure 10F, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 270°, the first blade groove 63 communicates with the injection hole 54 but not with the compression chamber 23b. In other words, the first cylinder 13 is in an injection-closed state. In contrast, the second cylinder 14 continues to be in an injection-closed state. Therefore, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 270°, both the first cylinder 13 and the second cylinder 14 are in an injection-closed state. Subsequently, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 271°, the first cylinder 13 continues to be in an injection-closed state, but the second cylinder 14 communicates with the injection hole 56 and has also begun to communicate with the compression chamber 24b. In other words, the second cylinder 14 transitions to an injection-open state. When the rotation angle of the eccentric portion 28a and the roller 16 becomes 360° and they complete one rotation, the first cylinder 13 remains in the injection closed state, and the second cylinder 14 remains in the injection open state.

[0100] In other words, during one rotation of the eccentric parts 28a, 28b and rollers 16, 17, there are two instances, specifically when the rotation angles are 90° and 270°, in which case both cylinders 13 and 14 are in the injection closed state. When the rotation angle is otherwise, one of the cylinders 13 or 14 is in the injection closed state, and the other is in the injection open state. Therefore, the first cylinder 13 and the second cylinder 14 do not communicate with each other via the injection mechanism (flow paths 40, 50, 60).

[0101] Thereafter, in the first cylinder 13 and the second cylinder 14, the injection open state and the injection closed state described above are repeated according to the rotation angles of the eccentric portions 28a and 28b and the rollers 16 and 17.

[0102] Figure 11 shows the trajectory of the relationship between the rotation angle, the compression load ratio, and the groove cross-sectional area ratio. Figure 12 shows the relationship between the injection state, the rotation angle, and the groove cross-sectional area ratio. The rotation angle is the rotation angle from the eccentric part and the top dead center of the roller. The compression load ratio is the trajectory shown by the dashed line in Figure 11, and is a value shown with 0 representing the state in which the refrigerant is not compressed in the compression chamber of the cylinder. The groove cross-sectional area ratio is the trajectory shown by the solid line in Figure 11, and is the ratio of the groove cross-sectional areas of the blade grooves 63 and 64 in this embodiment when the groove cross-sectional area of ​​the blade grooves 61 and 62 in the first embodiment is set to 1. The injection state is either the injection open state or the injection closed state in the compression chamber of the cylinder.

[0103] In the example shown in Figure 11, the compression load ratio is 0 when the rotation angle is 0°, gradually increases from there, peaks at around 200°, gradually decreases, and becomes 0 again at 360°. As shown in Figures 11 and 12, the injection is closed from 0° to 135°, so the groove cross-sectional area ratio is 0.

[0104] The injection mechanism remains open until the rotation angle reaches 135° and then 160°. At this time, for example, the first blade groove 63 communicates with the compression chamber 23b only at the first groove 71, which has a smaller groove cross-sectional area than the second groove 72. Therefore, the groove cross-sectional area ratio is less than 1, in this case 0.9.

[0105] The injection opening state continues until the rotation angle reaches 160° and then 200°. At this time, for example, the first blade groove 63 communicates with the compression chamber 23b at the first groove portion 71 and also at the second groove portion 72. In other words, the first blade groove 63 communicates with the compression chamber 23b at the second groove portion 72, which has a larger groove cross-sectional area than the blade grooves 61 and 62. Therefore, the groove cross-sectional area ratio is greater than 1, in this case 1.8.

[0106] The injection opening state continues until the rotation angle reaches 200° and then 225°. At this time, for example, the first blade groove 63 does not communicate with the second groove 72, but communicates with the compression chamber 23b only at the first groove 71. Therefore, the groove cross-sectional area ratio is a value less than 1, in this case 0.9.

[0107] Then, the injection mechanism closes again until the rotation angle reaches 225° and then 360°. Consequently, the groove cross-sectional area ratio becomes 0 again.

[0108] As described above, when the blade grooves 63 and 64 begin to communicate with the compression chambers 23b and 24b and the injection holes 54 and 56, the injection is open at the cross-sectional area of ​​the first groove 71. As the rotation angle increases from this state, the second groove 72, which has a larger cross-sectional area than the first groove 71, communicates with the compression chambers 23b and 24b, resulting in an injection open state. When the rotation angle exceeds 180° and increases further, the injection open state in which the second groove 72 communicates with the compression chambers 23b and 24b ends. Meanwhile, the first groove 71 remains in communication with the compression chambers 23b and 24b, and the injection remains open at the cross-sectional area of ​​the first groove 71. As the rotation angle increases further, the first groove 71 also loses communication with the compression chambers 23b and 24b, resulting in an injection closed state. When the blade grooves 63 and 64 begin to communicate with the compression chambers 23b and 24b and the injection holes 54 and 56 from this state, the injection opening state is restored to the groove cross-sectional area of ​​the first groove 71. Thereafter, this transition between the injection opening state and the injection closing state is repeated.

[0109] According to this embodiment, by making the cross-sectional areas of the first groove 71 and the second groove 72 different, the cross-sectional area of ​​the blade grooves 63 and 64 can be expanded from the cross-sectional area of ​​the first groove 71 to the cross-sectional area of ​​the second groove 72 before the pressure in the compression chambers 23b and 24b rises to the refrigerant discharge pressure. In other words, the amount of injected refrigerant injected into the compression chambers 23b and 24b can be reduced at the start and end of refrigerant compression, and the amount of injected refrigerant injected can be increased as compression progresses. That is, the amount of injected refrigerant injected can be increased during the compression progression, when cooling is required more than at the start and end of compression. Furthermore, the cross-sectional area of ​​the blade grooves 63 and 64 can be expanded in a short section corresponding to the total length of the groove. This makes it possible to set the flow rate of the injected refrigerant in the compression process to an appropriate amount, and improve the cooling performance of the compressor 2a using the heat of vaporization (latent heat and sensible heat) of the injected refrigerant.

[0110] Furthermore, the switching time between the open and closed states of the injection can be shortened, and the pressure in the compression chambers 23b and 24b is greater than the pressure in the injection flow path 7a, thus shortening the time the injection is in the open state.

[0111] Furthermore, when the pressure in the compression chambers 23b and 24b is greater than the pressure in the injection passage 7a, and the injection is open, the cross-sectional area of ​​the blade grooves 63 and 64 can be made smaller than the cross-sectional area of ​​the blade grooves 61 and 62. As a result, backflow of refrigerant into the injection passage 7a during compression can be suppressed. Therefore, the decrease in the cooling effect of the compressor 2a can be suppressed, and reliability can be improved. In addition, backflow of refrigerant can be prevented, performance degradation can be suppressed, and a high COP can be maintained.

[0112] (Third embodiment) In the first and second embodiments described above, the first blade 18 and the second blade 19 each have one blade groove 61 and 62. However, each blade may have multiple blade grooves. This groove configuration will be described below as the third embodiment. In the third embodiment, the basic configuration of the compressor 2b is the same as that of the compressor 2 in the first embodiment shown in Figure 2. Therefore, in the third embodiment, for each component of the compressor 2b that is the same as or similar to that of the compressor 2, the configuration of the compressor 2 shown in Figure 2 will be referred to, and the same reference numerals will be used, omitting further explanation. Furthermore, the compressor 2b, like the compressor 2, can be applied as one of the components of the air conditioner 1 (Figure 1) in the first embodiment.

[0113] Figure 13 is a longitudinal cross-sectional view schematically showing an enlarged portion of the compressor 2b. As shown in Figure 13, in this embodiment, the first blade 18 has two blade grooves 651 and 652, and the second blade 19 has two blade grooves 661 and 662. However, the number of blade grooves may be three or more, and may differ between the first blade 18 and the second blade 19. In this embodiment, the configurations of blade grooves 651 and 661, and blade grooves 652 and 662 are substantially the same.

[0114] Figure 14 is a schematic diagram showing a blade according to the third embodiment from the circumferential direction. As shown in Figures 13 and 14, the blade grooves 651, 661 and blade grooves 652, 662 have different groove lengths. In the illustrated example, the groove length L1 of blade grooves 651, 661 is longer than the groove length L2 of blade grooves 652, 662 (L1 > L2). In blades 18 and 19, blade grooves 651, 661 are located on one side (lower side) in the direction along the central axis O1, and blade grooves 652, 662 are located on the other side (upper side) in the same direction. Hereinafter, blade grooves 651, 661 will be referred to as lower blade grooves 651, 661, and blade grooves 652, 662 will be referred to as upper blade grooves 652, 662.

[0115] In the forward and backward directions of the blades 18 and 19, the positions of the backward-side ends 651a, 661a and 652a, 662a of the lower blade grooves 651 and 661 and the upper blade grooves 652 and 662 are the same, while the positions of the forward-side ends 651b, 661b and 652b, 662b are different. In the illustrated example, the forward-side ends 651b, 661b of the lower blade grooves 651 and 661 are located closer to the central axis O1 (to the left in Figure 14) than the forward-side ends 652b, 662b of the upper blade grooves 652 and 662.

[0116] The groove lengths L1 of the lower blade grooves 651 and 661 and L2 of the upper blade grooves 652 and 662 should be set such that, when the blades 18 and 19 are in their most retracted state relative to the cylinder chambers 23 and 24, the retracted ends 651a, 661a, 652a, and 662a do not overlap circumferentially with the spring insertion holes 13c and 14c.

[0117] As described above, in the examples shown in Figures 13 and 14, the groove length L1 of the lower blade grooves 651 and 661 is longer than the groove length L2 of the upper blade grooves 652 and 662. However, the order of groove lengths may be reversed from the illustrated examples. The groove lengths may differ between the first blade 18 and the second blade 19, but within a single blade, the groove lengths of the upper blade groove and the lower blade groove may differ.

[0118] In this embodiment, the groove widths of the lower blade grooves 651 and 661 and the groove widths of the upper blade grooves 652 and 662 are approximately the same. The groove depths of the lower blade grooves 651 and 661 and the groove depths of the upper blade grooves 652 and 662 are approximately the same. Therefore, the groove cross-sectional areas of the lower blade grooves 651 and 661 and the groove cross-sectional areas of the upper blade grooves 652 and 662 are approximately the same. However, the groove widths and groove depths of the lower blade grooves 651 and 661 and the groove widths and groove depths of the upper blade grooves 652 and 662 may be different. Also, in this embodiment, the groove cross-sectional areas of the lower blade grooves 651 and 661 and the groove cross-sectional areas of the upper blade grooves 652 and 662 are smaller than the groove cross-sectional areas (W × D) of the blade grooves 61 and 62 in the first embodiment. On the other hand, the sum of the groove cross-sectional areas of the lower blade grooves 651, 661 and the upper blade grooves 652, 662 is greater than the groove cross-sectional area (W × D) of blade grooves 61, 62.

[0119] Furthermore, similar to the first embodiment (Figure 3), the first cylinder passage 51 is configured with an inlet passage (vertical passage) 51a and two outlet passages 511b and 512b in a continuous manner. That is, the inlet passage 51a is branched into two outlet passages 511b and 512b. One outlet passage 511b communicates with an opening (injection hole 54a) in the side wall 13e of the first blade hole 13a. The other outlet passage 512b communicates with an opening (injection hole 54b) in the side wall 13e of the first blade hole 13a. The injection holes 54a and 54b open at different locations in the side wall 13e. After the injected refrigerant flows into the inlet passage 51a, it is divided into the two outlet passages 511b and 512b and guided to the injection holes 54a and 54b, respectively. The injection hole 54a is in communication with the lower blade groove 651 of the first blade 18, and the injection hole 54b is in communication with the upper blade groove 652 of the first blade 18.

[0120] The second cylinder passage 52 consists of an inlet passage (vertical passage) 52a and two outlet passages 521b and 522b in a continuous manner. That is, the inlet passage 52a is branched into two outlet passages 521b and 522b. One outlet passage 521b communicates with an opening (injection hole 56a) in the side wall 14e of the second blade hole 14a. The other outlet passage 512b communicates with an opening (injection hole 56b) in the side wall 14e of the second blade hole 14a. The injection holes 56a and 56b open at different locations in the side wall 14e. After the injected refrigerant flows into the inlet passage 52a, it is divided into the two outlet passages 521b and 522b and guided to the injection holes 56a and 56b, respectively. The injection hole 56a is in communication with the lower blade groove 661 of the second blade 19, and the injection hole 56b is in communication with the upper blade groove 662 of the second blade 19.

[0121] Figures 15A to 15F schematically show the state transitions of the injection mechanism in cylinders 13 and 14 during the refrigerant compression process. In this embodiment, the first eccentric portion 28a and the first roller 16 of the first cylinder 13 and the second eccentric portion 28b and the second roller 17 of the second cylinder 14 are positioned on the rotation axis 15 with a phase difference of 180°. Therefore, for example, if the position of the first blade 18 when the rotation angle of the eccentric portions 28a, 28b and rollers 16, 17 is 0° is taken as the top dead center, then the position of the second blade 19 at that time is the bottom dead center. Consequently, although the injection state at the start differs depending on this phase difference, the cycle of state transitions in the injection mechanism of cylinders 13 and 14 is equivalent.

[0122] As shown in Figure 15A, for example, when the rotation angle of the eccentric portion 28a and the roller 16 is 0°, the first blade 18 is positioned at top dead center. At this time, the lower blade groove 651 is not in communication with either the compression chamber 23b or the injection hole 54a. Similarly, the upper blade groove 652 is not in communication with either the compression chamber 23b or the injection hole 54b. In other words, the first cylinder 13 is in the injection closed state.

[0123] As shown in Figure 15B, from 0° to a predetermined rotation angle of the eccentric portion 28a and roller 16, the lower blade groove 651 remains disconnected from both the compression chamber 23b and the injection hole 54a. Similarly, the upper blade groove 652 remains disconnected from both the compression chamber 23b and the injection hole 54b. Therefore, the injection remains closed in the first cylinder 13.

[0124] As shown in Figure 15C, when the rotation angle of the eccentric portion 28a and the roller 16 becomes, for example, 135°, the lower blade groove 651 communicates with the injection hole 54a and begins to communicate with the compression chamber 23b. In other words, the first cylinder 13 enters the injection open state. In contrast, the upper blade groove 652 remains in a state where it does not communicate with either the compression chamber 23b or the injection hole 54b.

[0125] As shown in Figure 15D, when the rotation angle of the eccentric portion 28a and the roller 16 is 180°, the first blade 18 is positioned at bottom dead center. At this time, the lower blade groove 651 continues to communicate with both the compression chamber 23b and the injection hole 54a. In contrast, when the rotation angle of the eccentric portion 28a and the roller 16 becomes, for example, 160°, the upper blade groove 652 communicates with the injection hole 54b and then begins to communicate with the compression chamber 23b. Even when the rotation angle of the eccentric portion 28a and the roller 16 becomes 180°, the upper blade groove 652 continues to communicate with both the compression chamber 23b and the injection hole 54b. In other words, the first cylinder 13 continues to be in the injection open state.

[0126] As shown in Figure 15E, when the rotation angle of the eccentric portion 28a and roller 16 is from 180° to a predetermined rotation angle, the lower blade groove 651 remains in communication with both the compression chamber 23b and the injection hole 54a. In other words, the first cylinder 13 remains in an open injection state. In contrast, when the rotation angle of the eccentric portion 28a and roller 16 becomes, for example, 200°, the upper blade groove 652 communicates with the injection hole 54b but not with the compression chamber 23b. At the rotation angle shown in Figure 15E, the upper blade groove 652 remains in this state.

[0127] Subsequently, for example, when the rotation angle of the eccentric portion 28a and the roller 16 reaches 225°, the lower blade groove 651 communicates with the injection hole 54a but not with the compression chamber 23b. In other words, the first cylinder 13 transitions to the injection closed state.

[0128] As shown in Figure 15F, even when the rotation angle of the eccentric portion 28a and the roller 16 reaches 270°, the lower blade groove 651 remains in communication with the injection hole 54a but not with the compression chamber 23b. At this time, the upper blade groove 652 is not in communication with either the compression chamber 23b or the injection hole 54b. In other words, the first cylinder 13 remains in a closed injection state.

[0129] Then, when the rotation angle of the eccentric portion 28a and the roller 16 becomes 360° and they complete one rotation, the lower blade groove 651 is no longer in communication with either the compression chamber 23b or the injection hole 54a. The upper blade groove 652 also remains no longer in communication with either the compression chamber 23b or the injection hole 54b.

[0130] Thereafter, in the first cylinder 13, the injection open state and the injection closed state described above are repeated according to the rotation angle of the eccentric portion 28a and the roller 16.

[0131] Figure 16 shows the relationship between the injection state, rotation angle, and groove cross-sectional area ratio. The injection state is either the injection open state or the injection closed state in the compression chamber of the cylinder. The rotation angle is the rotation angle from the top dead center of the eccentric part and the roller. The compression load ratio is a value shown with 0 representing the state in the compression chamber of the cylinder where the refrigerant is not compressed. The groove cross-sectional area ratio is the sum of the upper groove cross-sectional area ratio and the lower groove cross-sectional area ratio. The upper groove cross-sectional area ratio is the ratio of the groove cross-sectional areas of the upper blade grooves 652 and 662 in this embodiment, when the groove cross-sectional area of ​​the blade grooves 61 and 62 in the first embodiment is set to 1. The lower groove cross-sectional area ratio is the ratio of the groove cross-sectional areas of the lower blade grooves 651 and 661 in this embodiment, when the groove cross-sectional area of ​​the blade grooves 61 and 62 in the first embodiment is set to 1.

[0132] In this embodiment, the relationship between the rotation angle, the compression load ratio, and the groove cross-sectional area ratio is substantially the same as that in the second embodiment shown in Figure 11. Therefore, the compression load ratio is 0 when the rotation angle is 0°, gradually increases from there, peaks at around 200°, gradually decreases, and becomes 0 again at 360°. The compression load ratio is a value that represents the state in which the refrigerant is not compressed in the compression chamber of the cylinder, with 0 being the value.

[0133] As shown in Figure 16, the injection is closed from 0° to 135°, so the upper groove cross-sectional area ratio, lower groove cross-sectional area ratio, and groove cross-sectional area ratio are all 0.

[0134] When the rotation angle reaches 135°, the injection port remains open until it reaches 160°. At this time, for example, the compression chamber 23b, the lower blade groove 651, and the injection hole 54a are in communication. The cross-sectional area of ​​the lower blade groove 651 is smaller than the cross-sectional area (W × D) of the blade grooves 61 and 62. Therefore, the ratio of the lower groove cross-sectional area is less than 1, which is 0.9 in this case. In contrast, the compression chamber 23b, the upper blade groove 652, and the injection hole 54b are not in communication. Therefore, the ratio of the upper groove cross-sectional area is 0. Thus, the ratio of the groove cross-sectional area is 0.9. In this way, the first cylinder 13 is in the injection port open state only through the lower blade groove 651.

[0135] The injection opening state continues when the rotation angle reaches 160° until it reaches 200°. At this time, for example, the compression chamber 23b, the lower blade groove 651, and the injection hole 54a remain in communication. Therefore, the ratio of the lower groove cross-sectional area is 0.9. In contrast, the compression chamber 23b, the upper blade groove 652, and the injection hole 54b are in communication. The groove cross-sectional area of ​​the upper blade groove 652 is smaller than the groove cross-sectional area (W×D) of the blade grooves 61 and 62. Therefore, the ratio of the upper groove cross-sectional area is a value less than 1, which is 0.9 in this case. Thus, the groove cross-sectional area ratio is 1.8. In this way, the first cylinder 13 is in an injection opening state via both the upper blade groove 652 and the lower blade groove 651.

[0136] The injection opening state continues until the rotation angle reaches 200° and then 225°. At this time, for example, the compression chamber 23b, the lower blade groove 651, and the injection hole 54a remain in communication. Therefore, the ratio of the lower groove cross-sectional area is 0.9. In contrast, the compression chamber 23b, the upper blade groove 652, and the injection hole 54b are not in communication. Therefore, the ratio of the upper groove cross-sectional area is 0. Thus, the groove cross-sectional area ratio is 0.9. In this way, the first cylinder 13 is in the injection opening state via only the lower blade groove 651.

[0137] Then, the injection mechanism closes again until the rotation angle reaches 225° and then 360°. Consequently, the ratio of the upper groove cross-sectional area, the lower groove cross-sectional area, and the groove cross-sectional area ratio all become 0 again.

[0138] According to this embodiment, by making the groove lengths of the upper blade grooves 652, 662 and the lower blade grooves 651, 661 different (L1 > L2), it is possible to transition from an injection open state via only the lower blade grooves 651, 661 to an injection open state via both the upper blade grooves 652, 662 and the lower blade grooves 651, 661 before the pressure in the compression chambers 23b, 24b rises to the refrigerant discharge pressure. In other words, the amount of injected refrigerant into the compression chambers 23b, 24b can be suppressed at the start and end of refrigerant compression, and the amount of injected refrigerant can be increased as compression progresses. That is, the amount of injected refrigerant can be increased during the compression progression phase, when cooling is required more than at the start or end of compression. Furthermore, the groove cross-sectional area contributing to injection can be expanded in a short section corresponding to the groove length. This makes it possible to improve the cooling performance of the compressor 2b using the heat of vaporization (latent heat and sensible heat) of the injected refrigerant.

[0139] Furthermore, the switching time between the open and closed states of the injection can be shortened, and the pressure in the compression chambers 23b and 24b is greater than the pressure in the injection flow path 7a, thus shortening the time the injection is in the open state.

[0140] Furthermore, when the pressure in the compression chambers 23b and 24b is greater than the pressure in the injection passage 7a, and the injection is open, the groove cross-sectional area contributing to the injection can be made smaller than in other conditions. As a result, backflow of the injected refrigerant into the injection passage 7a can be suppressed. Therefore, the decrease in the cooling effect of the compressor 2b can be suppressed, and reliability can be improved. In addition, backflow of the refrigerant can be prevented, performance degradation can be suppressed, and a high COP can be maintained. Although the second and third embodiments described above have described compressors having two cylinders, this can also be applied to compressors having three cylinders as described in other embodiments of the first embodiment. In this case, as with the first embodiment, it is preferable that the opening and closing timing of the injection passages in each cylinder does not cause multiple cylinders to open simultaneously, but rather that only a single cylinder opens. That is, when the injection passage in the first cylinder is open, the injection passages in the second and third cylinders are closed. Similarly, when the injection passage in the second cylinder is open, the injection passages in the first and third cylinders are closed, and when the injection passage in the third cylinder is open, the injection passages in the first and second cylinders are closed. The shape of the blade groove in the embodiments described above may be various shapes as long as they achieve the effects of the invention. For example, it may be a shape with a gradually tapering cross-sectional area, a round shape, or a combination of these.

[0141] Although several embodiments of the present invention have been described above, these embodiments are presented as examples only and are not intended to limit the scope of the invention. These novel 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 variations are included in the scope and spirit of the invention, as well as in the claims of the invention and its equivalents. [Explanation of symbols]

[0142] 1...Air conditioner, 2...Compressor, 7a...Injection passage, 7b...Connecting pipe, 10...Sealed container, 10a...Peripheral wall, 10b...Discharge pipe, 10c...Oil reservoir, 10d,10e...Suction pipe, 11...Compression mechanism, 12...Electric motor, 13...First cylinder, 13a...Blade hole (first blade hole), 13b...Spring, 13c...Spring insertion hole, 13d...Bottom surface, 13e,13f...Side walls, 14...Second cylinder, 14a...Blade hole (second blade hole), 14b...Spring, 14c...Spring insertion hole, 14d...Top surface, 14e,14f...Side walls, 15...Rotating shaft, 16...Roller (first -ra), 16a...inner surface of the first roller, 16b...outer surface of the first roller, 17...roller (second roller), 17a...inner surface of the second roller, 17b...outer surface of the second roller, 18...blade (first blade), 18a...tip, 18b,18c...side, 18d...end face, 19...blade (second blade), 19a...tip, 19b,19c...side, 19d...end face, 20...partition plate, 20a...outer surface, 20b...top, 20c...bottom, 21...first bearing, 22...second bearing, 23...cylinder chamber (first cylinder chamber), 23a...suction chamber (first suction 23b... Compression chamber (first compression chamber), 23c... Inlet, 24... Cylinder chamber (second cylinder chamber), 24a... Inlet chamber (second suction chamber), 24b... Compression chamber (second compression chamber), 24c... Inlet, 27a... First journal section, 27b... Second journal section, 27c... Extension section, 28a... First eccentric section, 28b... Second eccentric section, 29a... Outer surface of the first eccentric section, 29b... Outer surface of the second eccentric section, 33... Rotor, 34... Stator, 40... Flow path of partition plate (injection communication passage), 40a... Flow path on the partition plate inlet side (lateral flow path), 40b, 40c... Flow path on the partition plate outlet side (longitudinal flow) Pathway), 41, 42a, 42b... Opening, 50... Cylinder passage, 51... First cylinder passage, 51a... Inlet side passage (longitudinal passage), 51b, 511b, 512b... Outlet side passage (lateral passage), 52... Second cylinder passage, 52a... Inlet side passage (longitudinal passage), 52b, 521b, 522b... Outlet side passage (lateral passage), 53, 55... Opening, 54, 54a, 54b, 56, 56a, 56b... Opening (injection hole), 60... Blade passage, 61, 63... First blade groove, 61a... Reverse side end, 61b... Advance side end, 61c, 61d... Groove wall, 61e... Groove bottom, 62,64…Second blade groove, 62a…Reverse end, 62b…Advancing end, 62c,62d…Groove wall, 62e…Groove bottom, 651,661…Lower blade groove, 652,662…Upper blade groove, 651a,661a,652a,662a…Reverse end, 651b,661b,652b,662b…Advancing end, 71…First groove section, 72…Second groove section, 72a…End of second groove section, D…Depth of blade groove, L,La,L1,L2…Total length of blade groove, W,W1,W2…Width of blade groove.

Claims

1. A plurality of annular cylinders, each forming a cylinder chamber having a suction chamber for drawing in refrigerant and a compression chamber for compressing the refrigerant, A rotating shaft having multiple eccentric portions, each of which is arranged one by one in the cylinder chamber of each of the multiple cylinders, A plurality of rollers, each fitted to one of the plurality of eccentric portions, rotate eccentrically with respect to the axis of the rotating shaft within the cylinder chamber, The device comprises a plurality of substantially flattened blades that move back and forth within the cylinder chamber in accordance with the eccentric rotation of each of the plurality of rollers, and which divide the cylinder chamber into an intake chamber and a compression chamber. Each of the plurality of cylinders has a blade hole that opens in the inner circumference and extends outward along the radial direction to accommodate the blade, Each of the multiple blades of the cylinders has a blade groove formed in a groove shape on the side surface facing the compression chamber, among the side surfaces facing the circumferential direction with respect to the axis of the rotation shaft, Each of the plurality of cylinders has an injection hole in the wall facing the surface of the blade that faces the compression chamber, which is open to communicate with the blade groove. In each of the plurality of cylinders, the injection hole and the compression chamber transition between an injection open state in which they communicate via the blade groove and an injection closed state in which they do not communicate. The multiple cylinders may be in one of two states: either all of them are in the injection closed state, or one is in the injection open state and the others are in the injection closed state. Compressor.

2. The rotating shaft has three eccentric portions that are equally spaced in the circumferential direction, spaced apart in the direction of the axis of the rotating shaft. The cylinder comprises three cylinders: a first cylinder, a second cylinder, and a third cylinder. When the blade moving back and forth within the cylinder chamber of the first cylinder is most retracted relative to the cylinder chamber, the rotation angle of the eccentric portion and the roller positioned within the cylinder chamber of the first cylinder with respect to the axis of the rotation shaft is 0°, and when the eccentric portion and the roller rotate two times relative to the axis of the rotation shaft from this state, the rotation angle is 720°, and within the angular range of rotation angle from 0° to 720°, The first cylinder, the second cylinder, and the third cylinder switch six times from a state in which one has the injection open and the other two have the injection closed to a state in which all of them have the injection closed. The compressor according to claim 1.

3. The injection hole and compression chamber of any one of the three cylinders are not in communication with the injection hole of the blade hole of the other cylinder and the blade groove of the blade of that cylinder. The compressor according to claim 1 or 2.

4. A compressor according to claim 1 or 2, A condenser connected to the compressor, An expansion device connected to the condenser, The expansion device is connected to an evaporator, Refrigeration cycle device.

Images