Refrigeration cycle apparatus

Abstract

A refrigeration cycle apparatus (10) circulates a mixed refrigerant in which an adsorbent that adsorbs and desorbs a refrigerant is mixed with the refrigerant. The refrigeration cycle apparatus has a mixed refrigerant storage part (30) that stores the adsorbent in a refrigerant-adsorbed state. The refrigeration cycle apparatus adjusts the amount of refrigerant circulating in a cycle by adjusting the amount of adsorbent in the refrigerant-adsorbed state inside the mixed refrigerant storage part. The mixed refrigerant storage part is connected to allow for inflow and outflow of the refrigerant, and has an accommodation space (30b) for accommodating the adsorbent. The mixed refrigerant storage part causes inflowing refrigerant to be adsorbed onto the adsorbent by making the interior of the accommodation space a high-pressure environment of higher pressure than the adsorption pressure of the adsorbent. The mixed refrigerant storage part causes refrigerant to be desorbed from the adsorbent in the refrigerant-adsorbed state by making the interior of the accommodation space a low-pressure environment of lower pressure than the desorption pressure of the adsorbent.

Description

Refrigeration cycle equipment CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Japanese Patent Application No. 2024-084845 filed on May 24, 2024, the contents of which are incorporated herein by reference.

[0002] The present disclosure relates to a refrigeration cycle device.

[0003] A so-called hybrid refrigeration cycle apparatus has been disclosed in Patent Document 1. The hybrid refrigeration cycle apparatus is a vapor compression refrigeration cycle apparatus that circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent.

[0004] In this type of refrigeration cycle device, the heat of adsorption generated when the refrigerant is adsorbed by the adsorbent can be dissipated to a heat dissipation object. Also, the heat of desorption generated when the refrigerant is desorbed from the adsorbent can be absorbed from a heat absorption object. This allows the hybrid refrigeration cycle device to reduce the pressure of the high-pressure refrigerant and improve the cycle operating efficiency compared to a conventional vapor compression refrigeration cycle device that does not mix the refrigerant with an adsorbent.

[0005] International Publication No. 2024 / 004971

[0006] Here, since a vapor compression refrigeration cycle is used with various loads and various combinations of heat exchangers, the amount of refrigerant required varies depending on the system circuit configuration. Since an excess or deficiency of the refrigerant amount compared to the required amount has a significant impact on the capacity of the refrigeration cycle, it is desirable to ensure an appropriate amount of refrigerant.

[0007] In general refrigeration cycles, receivers and accumulators are used as refrigerant storage mechanisms to accommodate fluctuations in the amount of refrigerant required depending on the load and the circuit configuration of the cycle.Since receivers and accumulators are based on the premise that the refrigeration cycle is a gas-liquid two-phase cycle, they are thought to be inapplicable to refrigeration cycle devices that use a mixed refrigerant containing an adsorbent.

[0008] In view of the above, an object of the present disclosure is to provide a refrigeration cycle device that can respond to fluctuations in the amount of refrigerant required, in a refrigeration cycle that circulates a mixed refrigerant in which an adsorbent is mixed with the refrigerant.

[0009] A refrigeration cycle device according to a first aspect of the present disclosure circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent that adsorbs and desorbs the refrigerant. The refrigeration cycle device has a mixed refrigerant reservoir that stores the adsorbent in a state in which the refrigerant has been adsorbed, and adjusts the amount of refrigerant circulating through the cycle by adjusting the amount of the adsorbent in the mixed refrigerant reservoir.

[0010] The mixed refrigerant reservoir is connected to allow the inflow and outflow of refrigerant and has a storage space for storing the adsorbent. The mixed refrigerant reservoir creates a high-pressure environment inside the storage space that is higher than the adsorption pressure of the adsorbent, causing the refrigerant that has flowed in to be adsorbed by the adsorbent. The mixed refrigerant reservoir creates a low-pressure environment inside the storage space that is lower than the desorption pressure of the adsorbent, causing the refrigerant to be desorbed from the adsorbent that has adsorbed the refrigerant.

[0011] In this refrigeration cycle device, the inside of the storage space is created in a high-pressure environment, allowing the refrigerant that flows into the storage space to be adsorbed by the adsorbent. The refrigerant sealed inside the cycle is composed of the refrigerant circulating through the cycle and the refrigerant adsorbed by the adsorbent inside the storage space. Therefore, by adsorbing the refrigerant to the adsorbent inside the storage space, the amount of refrigerant circulating through the cycle can be reduced. In other words, if the amount of refrigerant circulating through the cycle is in excess of the required amount, the amount can be adjusted to approach the required amount.

[0012] Furthermore, the refrigeration cycle device can desorb the refrigerant from the adsorbent by creating a low-pressure environment inside the storage space. This allows the amount of refrigerant circulating through the cycle to be increased by desorbing the refrigerant from the adsorbent inside the storage space. Therefore, if the amount of refrigerant circulating through the cycle is insufficient, the amount of refrigerant can be adjusted to approach the required amount. In this way, the refrigeration cycle device can adjust the amount of refrigerant circulating through the cycle to approach the required amount by appropriately controlling the internal pressure of the mixed refrigerant reservoir to promote adsorption and desorption of the refrigerant to the adsorbent inside the storage space.

[0013] A refrigeration cycle device according to a second aspect of the present disclosure is a refrigeration cycle device that circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent that adsorbs and desorbs the refrigerant. The refrigeration cycle device has a pressurization unit, a heat dissipation unit, and a mixed refrigerant storage unit, and adjusts the amount of refrigerant circulating through the cycle by adjusting the amount of adsorbent that has adsorbed the refrigerant inside the mixed refrigerant storage unit. The pressurization unit pressurizes the mixed refrigerant. The heat dissipation unit dissipates heat from the mixed refrigerant that has been pressurized in the pressurization unit. The mixed refrigerant storage unit stores the adsorbent that has adsorbed the refrigerant.

[0014] The mixed refrigerant storage section has an extraction section, a refrigerant outlet section, and a mixed refrigerant outlet section. The extraction section extracts at least a portion of the refrigerant from the mixed refrigerant flowing out from the heat dissipation section. The refrigerant outlet section allows the refrigerant extracted in the extraction section to flow out. The mixed refrigerant outlet section allows the mixed refrigerant from which the refrigerant has been extracted to flow out.

[0015] The refrigeration cycle device further includes a flow rate adjusting unit that adjusts the amount of the mixed refrigerant flowing out from the mixed refrigerant outlet. The refrigeration cycle device adjusts the amount of the adsorbent that adsorbs the refrigerant stored inside the mixed refrigerant reservoir by adjusting the amount of the mixed refrigerant flowing out from the mixed refrigerant outlet using the flow rate adjusting unit.

[0016] In this refrigeration cycle device, the flow rate adjuster adjusts the amount of mixed refrigerant flowing out from the mixed refrigerant outlet. Because the mixed refrigerant is formed by mixing the adsorbent with the refrigerant, the adsorbent that has adsorbed the refrigerant also constitutes part of the mixed refrigerant. Therefore, by adjusting the amount of mixed refrigerant flowing out from the mixed refrigerant outlet, the refrigeration cycle device can adjust the amount of adsorbent that has adsorbed the refrigerant stored inside the mixed refrigerant reservoir.

[0017] The adsorbent stored in the mixed refrigerant storage section and having adsorbed the refrigerant together with the refrigerant circulating through the cycle constitutes the refrigerant sealed inside the cycle. Therefore, according to the refrigeration cycle device, the flow rate of the mixed refrigerant flowing out from the mixed refrigerant outlet can be adjusted by operating the flow rate adjuster, thereby increasing or decreasing the amount of refrigerant circulating through the cycle and adjusting it to approach the required amount of refrigerant.

[0018] The above and other objects, features, and advantages of the present disclosure will become more apparent from the following detailed description with reference to the accompanying drawings.

[0016] Fig. 1 is a schematic overall configuration diagram of a refrigeration cycle device according to a first embodiment. Fig. 2 is an axial cross-sectional view of an ejector according to the first embodiment. Fig. 3 is a schematic configuration diagram of a mixed refrigerant reservoir according to the first embodiment. Fig. 4 is an explanatory diagram showing an example of operation in an excess state in the first embodiment. Fig. 5 is an explanatory diagram showing an example of operation in a shortage state in the first embodiment. Fig. 6 is a schematic overall configuration diagram of a refrigeration cycle device according to a second embodiment. Fig. 7 is an explanatory diagram showing an example of operation in an excess state in the second embodiment. Fig. 8 is an explanatory diagram showing an example of operation in a shortage state in the second embodiment. Fig. 9 is a schematic overall configuration diagram of a refrigeration cycle device according to a third embodiment. Fig. 10 is an explanatory diagram showing an example of operation in an excess state in the third embodiment. Fig. 11 is an explanatory diagram showing an example of operation in a shortage state in the third embodiment.

[0019] Hereinafter, several embodiments for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, parts corresponding to matters described in the preceding embodiment may be assigned the same reference numerals, and duplicate descriptions may be omitted. In each embodiment, when only a part of the configuration is described, other previously described embodiments may be applied to the other parts of the configuration. In addition to combinations of parts that are specifically specified as being combinable in each embodiment, it is also possible to partially combine embodiments even if not specified, as long as there is no particular problem with the combination.

[0020] First Embodiment A first embodiment of the present disclosure will be described with reference to the drawings. In the first embodiment, a refrigeration cycle device 10 shown in the overall configuration diagram of Fig. 1 is applied to an air conditioner 1. The air conditioner 1 includes the refrigeration cycle device 10, a control device 50, and the like. The refrigeration cycle device 10 configures a vapor compression refrigeration cycle in the air conditioner 1 that adjusts the temperature of air blown into a room, which is a space to be air-conditioned.

[0021] The refrigeration cycle apparatus 10 uses carbon dioxide (i.e., R744) as a refrigerant. An adsorbent is mixed with the refrigerant. The adsorbent adsorbs at least the refrigerant in a high-pressure environment and desorbs (in other words, desorbs) the adsorbed refrigerant in a low-pressure environment. Furthermore, when adsorbing the refrigerant, the adsorbent releases heat (i.e., internal energy) contained in the adsorbed refrigerant as heat of adsorption, and when desorbing the refrigerant, it absorbs ambient heat as heat of desorption.

[0022] Specifically, in this embodiment, a metal-organic framework (MOF) is used as the adsorbent. MOF is a porous material obtained by reacting metal ions with organic ligands. MOF is a polymer structure that has numerous openings inside by linking metal ions with organic ligands.

[0023] The pore size of MOFs can be optimized by combining metal ions and organic ligands. By adjusting the pore size, MOFs can selectively adsorb the target substance. In this embodiment, a MOF suitable for adsorption of carbon dioxide, a refrigerant, is used.

[0024] The adsorbent is not dissolved in the refrigerant but is mixed with the refrigerant in a powder or particulate solid state. Furthermore, the amount of adsorbent mixed with the refrigerant in this embodiment is less than the amount that can adsorb all of the refrigerant under normal operating conditions of the refrigeration cycle apparatus 10. Therefore, in the refrigeration cycle apparatus 10, only the adsorbent does not circulate within the cycle.

[0025] In the following description, for clarity, a refrigerant mixed with an adsorbent will be referred to as a mixed refrigerant, and a refrigerant not mixed with an adsorbent will be referred to as a refrigerant, a discharge refrigerant, a discharge side injection refrigerant, a pressure reduction side injection refrigerant, etc., without using the term "mixed." In the refrigeration cycle according to this embodiment, the refrigerant circulates through the cycle in a gas phase.

[0026] As shown in FIG. 1 , the refrigeration cycle device 10 according to the first embodiment includes a compressor 11, an ejector 12, a heat dissipation heat exchanger 13, a high-pressure side extraction section 14, a first expansion valve 15, an outdoor heat exchanger 16, a solenoid valve 17, a second expansion valve 18, a heat absorption heat exchanger 19, and a low-pressure side extraction section 20.

[0027] The compressor 11 is a refrigerant compression unit in the refrigeration cycle apparatus 10 that draws in, compresses, and discharges refrigerant extracted by a low-pressure side extraction unit 20 (described later). The compressor 11 is an electric compressor that uses an electric motor to rotate a fixed-displacement compression mechanism with a fixed discharge capacity. The compression mechanism may be a rotary compression mechanism, a scroll compression mechanism, or the like. The rotation speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the control device 50.

[0028] The inlet side of a nozzle portion 12a of the ejector 12 is connected to the discharge port of the compressor 11. The ejector 12 draws the mixed refrigerant flowing out from the low-pressure side extraction portion 20 through a suction port 12c formed in a body portion 12b by the suction action of the discharge-side injected refrigerant sprayed from the nozzle portion 12a. Furthermore, the ejector 12 converts the velocity energy (i.e., expansion energy) of the mixed refrigerant, in which the adsorbent is mixed with the sprayed refrigerant, into pressure energy, thereby increasing the pressure of the mixed refrigerant.

[0029] Here, a specific configuration of the ejector 12 used in the refrigeration cycle apparatus 10 will be described in detail with reference to Fig. 2. As shown in Fig. 2, the ejector 12 has a nozzle portion 12a and a body portion 12b.

[0030] The nozzle portion 12a is a nozzle that converts pressure energy of the refrigerant discharged from the compressor 11 into velocity energy and sprays the refrigerant. The nozzle portion 12a is formed of a substantially cylindrical member made of metal (stainless steel in this embodiment) that gradually tapers in the direction of the refrigerant flow.

[0031] The nozzle portion 12a isentropically reduces the pressure of the discharged refrigerant, accelerates the refrigerant to a supersonic speed, and injects the refrigerant into a mixing portion 12e formed in the body portion 12b. A so-called Laval nozzle or a convergent nozzle can be used as the nozzle portion 12a.

[0032] The body portion 12b supports and fixes the nozzle portion 12a and forms the outer shell of the ejector 12. The body portion 12b is formed of a substantially cylindrical member made of metal (aluminum alloy in this embodiment). The nozzle portion 12a is fixed inside one longitudinal end of the body portion 12b by means of press-fitting or the like. The body portion 12b may be formed of resin.

[0033] The cylindrical wall of the body 12b is formed at a location corresponding to the outer periphery of the nozzle 12a with a suction port 12c penetrating the body 12b from the inside to the outside and communicating with the refrigerant injection port of the nozzle 12a. The suction port 12c is a through-hole that draws the mixed refrigerant flowing out from the low-pressure extraction section 20 into the body 12b by the suction action of the refrigerant injected from the nozzle 12a.

[0034] The body portion 12b is provided with a suction passage 12d, a mixing portion 12e, and a pressurizing portion 12f. The suction passage 12d guides the mixed refrigerant drawn through the suction port 12c to the mixing portion 12e. The mixing portion 12e is a space for mixing the mixed refrigerant drawn through the suction port 12c with the sprayed refrigerant. The mixing portion 12e is formed in a substantially cylindrical shape.

[0035] The pressure-increasing section 12f is a space for increasing the pressure of the mixed refrigerant sucked through the suction port 12c and the sprayed refrigerant. The pressure-increasing section 12f is formed in a truncated cone shape whose cross-sectional area expands in the direction of the flow of the mixed refrigerant. In the pressure-increasing section 12f, the velocity energy of the mixed refrigerant is converted into pressure energy by the action of shock waves generated by the sprayed refrigerant and the expansion of the passage cross-sectional area.

[0036] Therefore, the ejector 12 is a transport unit that transports the mixed refrigerant that flows out from the low-pressure side extraction unit 20 to the discharged refrigerant side by using the pressure energy of the discharged refrigerant discharged from the compressor 11. In other words, the ejector 12 uses the pressure energy of the discharged refrigerant to mix the mixed refrigerant that flows out from the low-pressure side extraction unit 20 with the injected refrigerant, which is the discharged refrigerant that has consumed the pressure energy.

[0037] Returning to Fig. 1 , the configuration of the refrigeration cycle apparatus 10 will be described. The outlet of the pressure boosting section 12f of the ejector 12 is connected to the mixed refrigerant inlet side of the heat dissipation heat exchanger 13. The heat dissipation heat exchanger 13 is a heat dissipation section that exchanges heat between the mixed refrigerant flowing out of the ejector 12 and the ventilation air blown into the room, which is the space to be air-conditioned, and dissipates heat contained in the mixed refrigerant to the ventilation air. Therefore, one of the objects to be dissipated heat in this embodiment is the ventilation air.

[0038] The mixed refrigerant outlet of the heat dissipation heat exchanger 13 is connected to the mixed refrigerant inlet 14c side of the high-pressure side extraction unit 14. The high-pressure side extraction unit 14 extracts a portion of the gas-phase refrigerant that does not contain adsorbent from the mixed refrigerant that has flowed out of the heat dissipation heat exchanger 13. In other words, the high-pressure side extraction unit 14 can be said to be a high-pressure side separation unit that separates the refrigerant that does not contain adsorbent from the mixed refrigerant.

[0039] The refrigerant not containing the adsorbent extracted by the high-pressure side extraction section 14 is in a gas phase (i.e., gas-phase refrigerant Rg). The remaining mixed refrigerant after the refrigerant has been extracted by the high-pressure side extraction section 14 contains the refrigerant and the adsorbent.

[0040] The high-pressure side extraction section 14 is formed as a hollow, bottomed, cylindrical metal container that defines an internal space. The high-pressure side extraction section 14 is arranged so that its axial direction is vertical. A flat filter 14f is disposed in the internal space of the high-pressure side extraction section 14. The high-pressure side extraction section 14 may be shaped to have a tapered portion that defines a space that tapers downward. This allows the powder or particulate adsorbent to flow out more easily.

[0041] The filter 14f vertically divides the internal space of the high-pressure side extraction section 14 into an upper space 14b and a lower space 14a. The filter 14f has selective permeability that allows the high-pressure side gas phase refrigerant Rg separated from the mixed refrigerant to pass through, but prohibits at least the adsorbent from passing through.

[0042] The lower space 14a is connected to the mixed refrigerant inlet 14c and the mixed refrigerant outlet 14d of the high-pressure side extraction section 14. The lower space 14a is configured to extract gas phase refrigerant Rg from the mixed refrigerant by utilizing the difference in specific gravity between the refrigerant and the adsorbent.

[0043] The volume of the lower space 14a is set so that when the mixed refrigerant in the lower space 14a becomes a mixed refrigerant in which the liquid-phase refrigerant is mixed with the adsorbent, the lower space 14a can be used as a liquid storage section for storing excess refrigerant in the cycle. As a result, in the high-pressure side extraction section 14, gas-phase refrigerant is extracted into the upper space 14b.

[0044] The mixed refrigerant outlet 14d is an outlet through which the mixed refrigerant stored in the lower space 14a (i.e., the remaining mixed refrigerant after the gas phase refrigerant has been extracted) flows out. The mixed refrigerant outlet 14d is formed in the center of the bottom surface of the high-pressure side extraction section 14. The inlet side of the first expansion valve 15 is connected to the mixed refrigerant outlet 14d.

[0045] The upper space 14b is connected to a gas-phase refrigerant outlet 14e of the high-pressure side extraction section 14. The gas-phase refrigerant outlet 14e is an outlet through which the high-pressure side gas-phase refrigerant Rg that has passed through the filter 14f flows out. The gas-phase refrigerant outlet 14e is formed on the top surface of the high-pressure side extraction section 14. The gas-phase refrigerant outlet 14e of the high-pressure side extraction section 14 is connected to a mixed refrigerant reservoir 30 (described later) and the like.

[0046] As described above, the inlet side of the first expansion valve 15 is connected to the mixed refrigerant outlet 14d side of the high-pressure side extraction section 14. The first expansion valve 15 is a pressure reducing section that reduces the pressure of the mixed refrigerant flowing out from the high-pressure side extraction section 14. More specifically, the first expansion valve 15 reduces the pressure of the refrigerant contained in the mixed refrigerant, thereby lowering the pressure of the ambient refrigerant in the adsorbent. Furthermore, the first expansion valve 15 is a flow rate adjusting section that adjusts the flow rate of the mixed refrigerant flowing into the outdoor heat exchanger 16.

[0047] More specifically, the first expansion valve 15 has a valve body and a drive unit. The valve body changes the throttle opening. The drive unit displaces the valve body. An electric actuator such as a stepping motor or a brushless DC motor can be used as the drive unit. In other words, the first expansion valve 15 is a so-called electric expansion valve, and its operation is controlled by a control signal output from the control device 50.

[0048] The first expansion valve 15 is configured as a variable throttle mechanism that has a full opening function that fully opens the refrigerant passage when the throttle opening is fully opened, and a full closing function that closes the refrigerant passage when the throttle opening is fully closed. In other words, the first expansion valve 15 can prevent the refrigerant from decompressing by fully opening the refrigerant passage.

[0049] The first expansion valve 15 blocks the refrigerant passage, thereby blocking the flow of refrigerant into the outdoor heat exchanger 16. That is, the first expansion valve 15 functions both as a pressure reducing unit that reduces the pressure of the refrigerant and as a refrigerant circuit switching unit that switches the refrigerant circuit. The first expansion valve 15 also adjusts the throttle opening of the refrigerant passage, thereby adjusting the flow rate of refrigerant flowing into the outdoor heat exchanger 16.

[0050] An outdoor heat exchanger 16 is connected to the mixed refrigerant outlet side of the first expansion valve 15. The outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the mixed refrigerant flowing therethrough and outside air blown by a blower fan (not shown) outside the room. In a heating mode, the outdoor heat exchanger 16 functions as a heat absorber that evaporates the refrigerant to absorb heat, and in a cooling mode, the outdoor heat exchanger 16 functions as a radiator that radiates heat from the mixed refrigerant.

[0051] A first connection part 25a having a three-way joint structure is disposed on the mixed refrigerant outlet side of the outdoor heat exchanger 16. In the first connection part 25a, one of three inlet / outlet ports is a refrigerant inlet, and the remaining two are refrigerant outlet ports. Furthermore, the refrigeration cycle apparatus 10 according to the first embodiment is provided with a second connection part 25b and a third connection part 25c. The second connection part 25b and the third connection part 25c have the same basic structure as the first connection part 25a, and also employ a three-way joint structure.

[0052] One outlet of the first connection part 25a is connected to the mixed refrigerant inlet side of the second expansion valve 18. The other outlet of the first connection part 25a is connected to one inlet side of the third connection part 25c via a bypass flow path 21. A solenoid valve 17 is arranged in the bypass flow path 21.

[0053] The electromagnetic valve 17 is an on-off valve that opens and closes the bypass flow path 21 that connects the other outlet side of the first connection part 25 a and one inlet side of the third connection part 25 c. The operation of the electromagnetic valve 17 is controlled by a control signal output from the control device 50.

[0054] The second expansion valve 18 is a pressure reducing unit that reduces the pressure of the mixed refrigerant flowing out from the outdoor heat exchanger 16 and adjusts the flow rate (mass flow rate) of the refrigerant flowing downstream at least during an operation mode in which the room is cooled. The second expansion valve 18 has a configuration similar to that of the first expansion valve 15. The second expansion valve 18 is an electric expansion valve and has a fully open function and a fully closed function.

[0055] A three-way joint-shaped second connection part 25b is disposed on the mixed refrigerant outlet side of second expansion valve 18. One inlet of second connection part 25b is connected to the mixed refrigerant outlet of second expansion valve 18. The other inlet of second connection part 25b is connected to a mixed refrigerant reservoir 30 (described later) and the like. The mixed refrigerant inlet side of heat-absorbing heat exchanger 19 is connected to the outlet of second connection part 25b.

[0056] The heat-absorbing heat exchanger 19 exchanges heat between the mixed refrigerant decompressed by the second expansion valve 18 and the blown air blown into the room from a blower (not shown). The heat-absorbing heat exchanger 19 is a heat absorbing unit that cools the blown air by desorbing the refrigerant from the adsorbent contained in the mixed refrigerant to absorb heat. Therefore, an example of an object to be absorbed in this embodiment is the blown air.

[0057] A three-way joint-shaped third connection part 25c is disposed on the mixed refrigerant outlet side of the heat absorption heat exchanger 19. The mixed refrigerant outlet of the heat absorption heat exchanger 19 is connected to one inlet of the third connection part 25c. As described above, the other inlet of the third connection part 25c is connected to the other outlet of the first connection part 25a via the bypass flow path 21. The outlet of the third connection part 25c is connected to the mixed refrigerant inlet 20c of the low-pressure side extraction part 20.

[0058] The low-pressure side extraction unit 20 extracts a portion of the gas-phase refrigerant not containing any adsorbent from the mixed refrigerant flowing out from the third connection unit 25c. The low-pressure side extraction unit 20 can also be referred to as a low-pressure side separation unit that separates the mixed refrigerant from the refrigerant not containing any adsorbent.

[0059] The basic configuration of the low-pressure side extraction section 20 is similar to that of the high-pressure side extraction section 14. Therefore, like the high-pressure side extraction section 14, the low-pressure side extraction section 20 has a lower space 20a, an upper space 20b, a mixed refrigerant inlet 20c, a mixed refrigerant outlet 20d, a gas-phase refrigerant outlet 20e, and a filter 20f.

[0060] The internal space of the low-pressure side extraction section 20 is divided into an upper space 20b and a lower space 20a by a filter 20f. A mixed refrigerant inlet 20c and a mixed refrigerant outlet 20d of the low-pressure side extraction section 20 are arranged in the lower space 20a. The mixed refrigerant outlet 20d of the low-pressure side extraction section 20 is connected to the suction port 12c side of the ejector 12. A gas phase refrigerant outlet 20e of the low-pressure side extraction section 20 is arranged in the upper space 20b. The gas phase refrigerant outlet 20e of the low-pressure side extraction section 20 is connected to the suction port side of the compressor 11.

[0061] Therefore, in this embodiment, the low-pressure side extraction section 20, the compressor 11, and the ejector 12 form a pressure-boosting section that pressurizes the mixed refrigerant flowing out from the heat-absorbing heat exchanger 19 and causes the mixed refrigerant to flow out to the mixed refrigerant inlet side of the heat-dissipating heat exchanger 13, which is a heat-dissipating section. In other words, the pressure-boosting section of this embodiment includes the low-pressure side extraction section 20, the compressor 11, and the ejector 12.

[0062] Here, in the refrigeration cycle device 10 of the first embodiment, a mixed refrigerant storage section 30 or the like is arranged between the gas phase refrigerant outlet 14e of the high-pressure side extraction section 14 and the other inlet at the second connection section 25b to adjust the amount of refrigerant circulating through the cycle.

[0063] The specific configuration of the mixed refrigerant storage unit 30 will be described in detail with reference to Figures 1 and 3. As shown in Figure 3, the mixed refrigerant storage unit 30 according to the first embodiment is configured by filling an adsorbent into a storage container 30a having an internal storage space 30b.

[0064] The adsorbent filled inside the mixed refrigerant reservoir 30 is configured to be able to adsorb and desorb the refrigerant circulating through the cycle of the refrigeration cycle device 10. In this embodiment, a metal-organic framework (MOF) is used as the adsorbent filled inside the mixed refrigerant reservoir 30.

[0065] The adsorbent filled in the mixed refrigerant storage section 30 is set so that the adsorption start pressure is lower than the refrigerant pressure on the high-pressure side in the cycle, when the pressure at which the MOF starts adsorption is defined as the adsorption start pressure.

[0066] Therefore, when the refrigerant flows into the storage space 30b in an environment with a higher pressure than the adsorption start pressure, the refrigerant is adsorbed by the adsorbent filled in the storage space 30b. As a result, the refrigerant is stored inside the mixed refrigerant storage section 30 in a state where it is adsorbed by the adsorbent.

[0067] Furthermore, the adsorbent filled in the storage space 30b is set so that the desorption start pressure, when the pressure at which the MOF starts desorption, is defined as the desorption start pressure, is higher than the refrigerant pressure on the low-pressure side of the cycle.

[0068] Therefore, when the pressure environment becomes lower than the desorption start pressure, the refrigerant is desorbed from the adsorbent that has adsorbed the refrigerant, and becomes available for supply to the outside of the mixed refrigerant storage section 30. This makes it possible to supply the refrigerant from the mixed refrigerant storage section 30 to the cycle.

[0069] As shown in Figure 3, the storage container 30a is formed with an inlet 30c and an outlet 30d. The inlet 30c communicates between the interior of the storage space 30b and the outside of the mixed refrigerant storage section 30, and is connected to the gas phase refrigerant outlet 14e of the high pressure side extraction section 14 via a high pressure side adjustment valve 31. The high pressure side adjustment valve 31 is an electromagnetic valve that adjusts the opening of the refrigerant flow path that connects the gas phase refrigerant outlet 14e of the high pressure side extraction section 14 and the inlet 30c of the mixed refrigerant storage section 30. The operation of the high pressure side adjustment valve 31 is controlled in accordance with a control signal from the control device 50.

[0070] The outlet 30d communicates between the interior of the storage space 30b and the outside of the mixed refrigerant storage portion 30, and is connected to the other inlet side of the second connection portion 25b via a low-pressure side adjustment valve 32. The low-pressure side adjustment valve 32 is an electromagnetic valve for adjusting the degree of opening of the refrigerant flow connecting the outlet 30d of the mixed refrigerant storage portion 30 and the other inlet of the second connection portion 25b. The operation of the low-pressure side adjustment valve 32 is controlled in accordance with a control signal output from the control device 50.

[0071] 3, two filters 30e are disposed inside the mixed refrigerant reservoir 30. Each filter 30e has selective permeability that allows the gas-phase refrigerant circulating in the cycle and the gas-phase refrigerant desorbed in the storage space 30b to pass through, but prohibits at least the adsorbent circulating in the cycle and the adsorbent filled in the storage space 30b from passing through.

[0072] One filter 30e is disposed on the inlet 30c side of the storage space 30b, and the other filter 30e is disposed on the outlet 30d side of the storage space 30b. Inside the storage space 30b, the adsorbent is filled in a state sandwiched between the filters 30e disposed opposite each other.

[0073] Therefore, in the refrigeration cycle apparatus 10 according to the first embodiment, by opening the high-pressure side regulating valve 31, it is possible to allow the high-pressure side gas-phase refrigerant to flow into the storage space 30b of the mixed refrigerant storage unit 30. Furthermore, by opening the low-pressure side regulating valve 32, the refrigeration cycle apparatus 10 can desorb the refrigerant from the adsorbent inside the mixed refrigerant storage unit 30 and supply it as the refrigerant circulating in the cycle.

[0074] Next, the control system of the air conditioner 1 according to the first embodiment will be described. The control device 50 has a well-known microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuits. The control device 50 performs various calculations and processes based on control programs stored in the ROM. The control device 50 then controls the operation of various control target devices connected to the output side based on the results of the calculations and processes.

[0075] As shown in FIG. 1, in the first embodiment, the output side of the control device 50 is connected to the compressor 11, the first expansion valve 15, the solenoid valve 17, the second expansion valve 18, the high-pressure side regulating valve 31, and the low-pressure side regulating valve 32 as controlled devices.

[0076] A group of various control sensors is connected to the input side of the control device 50. The group of control sensors includes air conditioning sensors such as an inside air temperature sensor, an outside air temperature sensor, a high-pressure pressure sensor, a high-pressure temperature sensor, an evaporator pressure sensor, and an evaporator temperature sensor (not shown).

[0077] The inside air temperature sensor is an inside air temperature detector that detects the indoor air temperature (i.e., the inside air temperature) Tr. The outside air temperature sensor is an outside air temperature detector that detects the outside air temperature (i.e., the outside air temperature) Tam.

[0078] The high-pressure pressure sensor is a high-pressure pressure detection unit that detects a high-pressure pressure Pd, which is the pressure of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13. The high-pressure temperature sensor is a high-pressure temperature detection unit that detects a high-pressure temperature Td, which is the temperature of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13.

[0079] The evaporator pressure sensor is an evaporator pressure detection unit that detects the evaporator pressure Pe, which is the pressure of the mixed refrigerant flowing out from the heat absorption heat exchanger 19. The evaporator temperature sensor is an evaporator temperature detection unit that detects the evaporator temperature Te, which is the temperature of the mixed refrigerant flowing out from the heat absorption heat exchanger 19.

[0080] An operation panel (not shown) is connected to the input side of the control device 50 by wire or wirelessly. Operation signals from various operation switches provided on the operation panel are input to the control device 50. The various operation switches provided on the operation panel include an activation switch, a temperature setting switch, an air volume setting switch, etc.

[0081] The control device 50 is an integrated unit that controls various controlled devices connected to the output side. Therefore, the components (hardware and software) that control the operation of each controlled device constitute the control unit that controls the operation of the controlled device. For example, the component in the control device 50 that controls the refrigerant discharge capacity of the compressor 11 constitutes a discharge capacity control unit. Furthermore, the component in the control device 50 that controls the operation of the high-pressure side regulating valve 31 and the low-pressure side regulating valve 32 constitutes a storage amount control unit that adjusts the amount of refrigerant stored in the mixed refrigerant storage unit 30.

[0082] The air conditioner 1 according to the first embodiment configured as described above can operate in a cooling mode for cooling the room and a heating mode for heating the room. The cooling mode and the heating mode have different refrigeration cycle circuit configurations and require different amounts of refrigerant. Furthermore, the fluctuations in the air conditioning load also differ between the cooling mode and the heating mode, which can also cause fluctuations in the amount of refrigerant required.

[0083] Here, the operation of the heating mode will be described as an operation mode in which an excess state in which the amount of refrigerant circulating through the cycle of the refrigeration cycle device 10 is more likely to occur than the required amount of refrigerant, and the operation of the mixed refrigerant storage unit 30 in the excess state will be described with reference to Fig. 4. In the heating mode, the required amount of refrigerant is likely to be small, and the excess state is likely to occur.

[0084] When the air conditioner 1 according to the first embodiment is in the heating mode, the control device 50 controls the compressor 11 to achieve a predetermined refrigerant discharge capacity. The control device 50 also controls the first expansion valve 15 to a predetermined throttle opening, and the second expansion valve 18 to a fully closed state. The control device 50 also controls the solenoid valve 17 to a fully open state.

[0085] When the normal heating mode is performed without controlling the mixed refrigerant storage unit 30, the control device 50 controls both the high-pressure side regulating valve 31 and the low-pressure side regulating valve 32 to be fully closed. In the following description and drawings, the mixed refrigerant in the refrigeration cycle device 10 is referred to as mixed refrigerant Rm, and a portion of the refrigerant extracted from the mixed refrigerant is referred to as gas-phase refrigerant Rg.

[0086] When the heating mode is executed, the gas-phase refrigerant Rg discharged from the compressor 11 flows into the nozzle portion 12a of the ejector 12. The gas-phase refrigerant Rg that flows into the nozzle portion 12a is isentropically decompressed and injected into the mixing portion 12e of the body portion 12b. Then, due to the suction effect of the refrigerant injected from the nozzle portion 12a, the mixed refrigerant Rm that flows out from the mixed refrigerant outlet 20d of the low-pressure side extraction portion 20 is sucked through the suction port 12c.

[0087] The mixed refrigerant Rm sucked through the suction port 12c flows into the mixing section 12e via the suction passage 12d. In the mixing section 12e, the sprayed refrigerant and the mixed refrigerant Rm sucked through the suction port 12c are mixed to form the mixed refrigerant Rm, which then flows into the pressure increasing section 12f.

[0088] In the pressure-boosting section 12f, the velocity energy of the mixed refrigerant Rm is converted into pressure energy by the action of shock waves generated by the discharge-side injected refrigerant and the expansion of the passage cross-sectional area. This increases the pressure of the mixed refrigerant Rm. As the pressure of the mixed refrigerant Rm increases in the pressure-boosting section 12f, the adsorbent adsorbs the refrigerant.

[0089] The mixed refrigerant Rm flowing out from the pressure boosting section 12f of the ejector 12 flows into the heat dissipation heat exchanger 13. The mixed refrigerant Rm that flows into the heat dissipation heat exchanger 13 dissipates heat to the ventilation air that is blown into the room by the blower. More specifically, when the refrigerant contained in the mixed refrigerant Rm that flows into the heat dissipation heat exchanger 13 is adsorbed into the adsorbent, it dissipates the internal energy stored in the adsorbent to the ventilation air as heat of adsorption. This heats the ventilation air that is supplied to the space to be air-conditioned, thereby achieving heating of the room.

[0090] The mixed refrigerant Rm flowing out of the heat dissipation heat exchanger 13 flows into the lower space 14a through the mixed refrigerant inlet 14c of the high-pressure side extraction section 14. The refrigerant contained in the mixed refrigerant Rm that has flowed into the lower space 14a flows into the upper space 14b through the filter 14f. The gas-phase refrigerant Rg that has flowed out of the upper space 14b flows out through the gas-phase refrigerant outlet 14e. The mixed refrigerant Rm that has flowed out of the lower space 14a flows out through the mixed refrigerant outlet 14d.

[0091] In the normal heating mode, the high-pressure side regulating valve 31 is fully closed, so that the gas phase refrigerant Rg does not flow out from the gas phase refrigerant outlet 14e, and the mixed refrigerant Rm flows out from the mixed refrigerant outlet 14d.

[0092] The mixed refrigerant Rm flowing out from the mixed refrigerant outlet 14d flows into the first expansion valve 15 and is decompressed. More specifically, the refrigerant contained in the mixed refrigerant Rm flowing out from the high-pressure side extraction section 14 flows into the first expansion valve 15 and is decompressed. The mixed refrigerant Rm decompressed by the first expansion valve 15 flows into the outdoor heat exchanger 16.

[0093] The mixed refrigerant Rm that has flowed into the outdoor heat exchanger 16 absorbs heat from the outside air blown by a blower fan (not shown). More specifically, the refrigerant contained in the mixed refrigerant Rm that has flowed into the outdoor heat exchanger 16 is desorbed from the adsorbent as the pressure drops. At this time, the adsorbent absorbs heat from the outside air as heat of desorption.

[0094] The mixed refrigerant Rm flowing out of the outdoor heat exchanger 16 flows into the bypass passage 21 via the first connection part 25a. The mixed refrigerant Rm that has flowed into the bypass passage 21 flows through the solenoid valve 17 and the third connection part 25c, and then through the mixed refrigerant inlet 20c of the low-pressure side extraction part 20 into the lower space 20a.

[0095] A portion of the refrigerant contained in the mixed refrigerant Rm that has flowed into the lower space 20a flows into the upper space 20b via the filter 20f. The gas-phase refrigerant Rg that has flowed out of the upper space 20b is drawn into the compressor 11 and compressed again. The mixed refrigerant Rm that has flowed out of the lower space 20a is drawn through the suction port 12c of the ejector 12.

[0096] In this way, in the refrigeration cycle apparatus 10 according to the first embodiment, heat absorbed from outside air in the outdoor heat exchanger 16 can be used to heat the blown air in the heat dissipation heat exchanger 13. That is, the air conditioner 1 according to the first embodiment can heat the room, which is the space to be air-conditioned, by using outside air as a heat source.

[0097] In the refrigeration cycle device 10, when the amount of refrigerant in the cycle exceeds the required amount determined by the air conditioning load and the circuit configuration of the cycle, the amount of refrigerant in the cycle can be adjusted to approach the required amount by utilizing the mixed refrigerant reservoir 30. The adjustment operation for the amount of refrigerant in the cycle in an excess state will be described with reference to FIG.

[0098] In the adjustment operation in the case of an excess state, the control device 50 fully closes the low-pressure side adjustment valve 32 and opens the high-pressure side adjustment valve 31. As a result, the gas phase refrigerant Rg extracted from the mixed refrigerant Rm in the high-pressure side extraction unit 14 flows into the storage space 30b of the mixed refrigerant storage unit 30 via the gas phase refrigerant outlet 14e of the high-pressure side extraction unit 14 and the high-pressure side adjustment valve 31.

[0099] In the heating mode, the refrigerant flow path from the downstream side of the ejector 12 to the upstream side of the first expansion valve 15 constitutes a high-pressure side flow path. As shown in Fig. 4, the high-pressure side extraction unit 14 is disposed between the downstream side of the ejector 12 and the upstream side of the first expansion valve 15, and therefore constitutes part of the high-pressure side flow path.

[0100] Therefore, by opening the high-pressure side regulating valve 31 and connecting to the high-pressure side flow path, the inside of the storage space 30b of the mixed refrigerant storage unit 30 can be changed to a high-pressure environment showing a pressure higher than the adsorption pressure of the adsorbent. In other words, by creating a high-pressure environment in the storage space 30b, the gas-phase refrigerant Rg that has flowed in can be adsorbed by the adsorbent filled inside the storage space 30b.

[0101] By controlling the opening degree of the high-pressure side regulating valve 31, the amount of refrigerant adsorbed by the adsorbent can be increased, thereby storing the excess refrigerant in the cycle inside the storage space 30b. As a result, in the refrigeration cycle device 10 in an excess state, the amount of refrigerant circulating in the cycle can be made closer to the required amount, and the refrigerant amount can be adjusted to an appropriate amount.

[0102] Next, the operation of the cooling mode will be described as an operation mode in which a shortage state, in which the amount of refrigerant circulating through the cycle of the refrigeration cycle device 10 is less than the required amount, is likely to occur, and the operation of the mixed refrigerant storage unit 30 in the shortage state will be described with reference to Figure 5. In the cooling mode, the required amount of refrigerant is likely to be large, and it is thought that a shortage state is likely to occur.

[0103] When the air conditioner 1 according to the first embodiment is in the cooling mode, the control device 50 controls the compressor 11 to achieve a predetermined refrigerant discharge capacity. The control device 50 also controls the second expansion valve 18 to a predetermined throttle opening, and the first expansion valve 15 to a fully open state. The control device 50 also controls the solenoid valve 17 to a fully closed state.

[0104] In addition, when the normal cooling mode is performed without controlling the mixed refrigerant storage section 30, the control device 50 controls both the high-pressure side regulating valve 31 and the low-pressure side regulating valve 32 to be fully closed.

[0105] When the cooling mode is executed, the gas-phase refrigerant Rg discharged from the compressor 11 flows into the nozzle portion 12a of the ejector 12. The gas-phase refrigerant Rg that flows into the nozzle portion 12a is isentropically decompressed and injected into the mixing portion 12e of the body portion 12b. Then, due to the suction effect of the refrigerant injected from the nozzle portion 12a, the mixed refrigerant Rm that flows out from the mixed refrigerant outlet 20d of the low-pressure side extraction portion 20 is sucked through the suction port 12c.

[0106] The mixed refrigerant Rm sucked through the suction port 12c flows into the mixing section 12e via the suction passage 12d. In the mixing section 12e, the sprayed refrigerant and the mixed refrigerant Rm sucked through the suction port 12c are mixed to form the mixed refrigerant Rm, which then flows into the pressure increasing section 12f.

[0107] In the pressure-boosting section 12f, the velocity energy of the mixed refrigerant Rm is converted into pressure energy by the action of shock waves generated by the discharge-side injected refrigerant and the expansion of the passage cross-sectional area. This increases the pressure of the mixed refrigerant Rm. As the pressure of the mixed refrigerant Rm increases in the pressure-boosting section 12f, the adsorbent adsorbs the refrigerant.

[0108] The mixed refrigerant Rm flowing out from the pressure boosting section 12f of the ejector 12 flows into the heat dissipation heat exchanger 13. Here, in the cooling mode, operational control such as changing the blowing air path is performed to reduce the amount of blowing air supplied to the heat dissipation heat exchanger 13. For example, the blowing air path may be changed so as to bypass the heat dissipation heat exchanger 13. As a result, the mixed refrigerant Rm that has flowed into the heat dissipation heat exchanger 13 flows out of the heat dissipation heat exchanger 13 without dissipating heat to the blowing air.

[0109] The mixed refrigerant Rm flowing out of the heat dissipation heat exchanger 13 flows into the lower space 14a through the mixed refrigerant inlet 14c of the high-pressure side extraction section 14. The refrigerant contained in the mixed refrigerant Rm that has flowed into the lower space 14a flows into the upper space 14b through the filter 14f. The gas-phase refrigerant Rg that has flowed out of the upper space 14b flows out through the gas-phase refrigerant outlet 14e. The mixed refrigerant Rm that has flowed out of the lower space 14a flows out through the mixed refrigerant outlet 14d.

[0110] In the normal cooling mode, since the high-pressure side regulating valve 31 is fully closed, the gas phase refrigerant Rg does not flow out from the gas phase refrigerant outlet 14e, and the mixed refrigerant Rm flows out from the mixed refrigerant outlet 14d.

[0111] The mixed refrigerant Rm flowing out from the mixed refrigerant outlet 14d flows into the first expansion valve 15. Because the first expansion valve 15 is fully open, the mixed refrigerant Rm flows into the outdoor heat exchanger 16 without being reduced in pressure. The mixed refrigerant Rm that has flowed into the outdoor heat exchanger 16 releases heat to outside air blown by a blower fan (not shown). More specifically, when the refrigerant contained in the mixed refrigerant Rm that has flowed into the outdoor heat exchanger 16 is adsorbed into the adsorbent, it releases the internal energy stored in the adsorbent to the blown air as heat of adsorption.

[0112] 5, the mixed refrigerant Rm flowing out from the outdoor heat exchanger 16 flows into the second expansion valve 18 via the first connection part 25a and is decompressed, and the refrigerant contained in the mixed refrigerant Rm flowing out from the first connection part 25a flows into the second expansion valve 18 and is decompressed.

[0113] The mixed refrigerant Rm decompressed by the second expansion valve 18 flows into the heat-absorbing heat exchanger 19 via the second connection part 25b. The mixed refrigerant Rm decompressed by the second expansion valve 18 absorbs heat from the blown air blown into the room by the blower. More specifically, the refrigerant contained in the mixed refrigerant Rm that flows into the heat-absorbing heat exchanger 19 is desorbed from the adsorbent as the pressure drops. At this time, the adsorbent absorbs the heat of the blown air as desorption heat. This makes it possible to cool the blown air supplied to the room, which is the space to be air-conditioned.

[0114] The mixed refrigerant Rm flowing out of the endothermic heat exchanger 19 flows through the third connection portion 25c and the mixed refrigerant inlet 20c of the low-pressure side extraction portion 20 into the lower space 20a. A portion of the refrigerant contained in the mixed refrigerant Rm that has flowed into the lower space 20a flows into the upper space 20b via the filter 20f. The gas-phase refrigerant Rg that has flowed out of the upper space 20b is drawn into the compressor 11 and compressed again. The mixed refrigerant Rm that has flowed out of the lower space 20a is drawn through the suction port 12c of the ejector 12.

[0115] In this way, in the refrigeration cycle apparatus 10 according to the first embodiment, heat can be dissipated to the outside air by the outdoor heat exchanger 16, and the blown air can be cooled by the heat absorption heat exchanger 19. That is, the air conditioner 1 according to the first embodiment can cool the room, which is the space to be air-conditioned.

[0116] In the refrigeration cycle device 10, when the amount of refrigerant in the cycle is less than the required amount determined by the air conditioning load and the circuit configuration of the cycle, the amount of refrigerant in the cycle can be adjusted to approach the required amount by utilizing the mixed refrigerant reservoir 30. The adjustment operation for the amount of refrigerant in the cycle when there is a shortage will be described with reference to FIG.

[0117] In the adjustment operation in the case of a shortage state, the control device 50 opens the low-pressure-side adjustment valve 32 while keeping the high-pressure-side adjustment valve 31 fully closed. As a result, the storage space 30b of the mixed refrigerant storage unit 30 communicates with the second connection unit 25b of the refrigeration cycle apparatus 10. Here, in the cooling mode, the refrigerant flow path from the outlet side of the second expansion valve 18 to the mixed refrigerant inlet 20c of the low-pressure-side extraction unit 20 forms a low-pressure-side flow path.

[0118] Therefore, by opening the low-pressure side regulating valve 32 and connecting it to the second connection part 25b, the interior of the mixed refrigerant storage part 30 can be connected to the low-pressure side flow path. This changes the interior of the storage space 30b of the mixed refrigerant storage part 30 to a low-pressure environment that exhibits a pressure lower than the desorption pressure of the adsorbent. In other words, by creating a low-pressure environment in the storage space 30b, the gas-phase refrigerant Rg can be desorbed from the adsorbent filled inside the storage space 30b. Then, inside the storage space 30b, the gas-phase refrigerant Rg desorbed from the adsorbent merges with the flow of refrigerant circulating in the cycle via the low-pressure side regulating valve 32 and the second connection part 25b.

[0119] That is, according to the refrigeration cycle apparatus 10 of the first embodiment, the refrigerant stored inside the mixed refrigerant storage section 30 can be added as refrigerant circulating through the cycle by reducing the amount of adsorbent that adsorbs the refrigerant through control of the aperture of the low-pressure side regulating valve 32. As a result, in the refrigeration cycle apparatus 10 in a shortage state, the amount of refrigerant circulating through the cycle can be brought closer to the required amount of refrigerant, and the refrigerant amount can be adjusted to an appropriate amount.

[0120] In the refrigeration cycle device 10 according to the first embodiment, when an excessive condition such as heating mode occurs, the opening degree of the high-pressure side regulating valve 31 is controlled to allow the gas phase refrigerant flowing through the high-pressure side flow path to flow in, and the storage space 30b of the mixed refrigerant storage section 30 can be made into a high-pressure environment.

[0121] This allows the adsorbent filled in the storage space 30b in a high-pressure environment to adsorb the gas-phase refrigerant Rg that has flowed in, and allows the excess refrigerant in the cycle to be stored in a state adsorbed by the adsorbent. By storing the excess refrigerant in the cycle in the mixed refrigerant storage section 30, the refrigeration cycle device 10 can adjust the amount of refrigerant circulating in the cycle to approach the required amount of refrigerant.

[0122] Furthermore, in the refrigeration cycle device 10 according to the first embodiment, when a shortage state such as in the cooling mode occurs, the storage space 30b can be connected to the low-pressure side flow path by controlling the opening degree of the low-pressure side adjustment valve 32, thereby creating a low-pressure environment inside the storage space 30b.

[0123] This allows the refrigerant to be desorbed from the adsorbent in the low-pressure environment of the storage space 30b, and the desorbed gas-phase refrigerant to be merged with the flow of refrigerant circulating through the cycle. The refrigeration cycle device 10 can adjust the amount of refrigerant circulating through the cycle to approach the required amount by using the refrigerant flowing out of the mixed refrigerant storage section 30.

[0124] 4 and 5 , the inlet 30c of the mixed refrigerant storage section 30 is connected to the gas phase refrigerant outlet 14e side of the high pressure side extraction section 14. In the high pressure side extraction section 14, the gas phase refrigerant Rg that is partially extracted from the mixed refrigerant Rm that contains the adsorbent flows into the mixed refrigerant storage section 30, so that excess refrigerant can be reliably stored inside the mixed refrigerant storage section 30.

[0125] When stopping operation in heating mode or cooling mode, if the refrigerant circulation is simply stopped, as in the case of a gas-liquid two-phase cycle, it is expected that the refrigerant pressure in the cycle will increase due to changes in the environment during the shutdown period. If there is a large amount of refrigerant in the cycle, it is expected that the amount will exceed the limit that can be adsorbed by the circulating adsorbent, and the refrigerant pressure in the cycle will increase to a temperature equivalent to the saturation temperature of the charged refrigerant at the outside air temperature.

[0126] Therefore, when stopping operation in the heating mode or the cooling mode and stopping the circulation of the mixed refrigerant, the control device 50 first fully closes the low-pressure side regulating valve 32 and then opens the high-pressure side regulating valve 31. As a result, the gas phase refrigerant Rg extracted from the mixed refrigerant Rm in the high-pressure side extraction unit 14 flows into the storage space 30b of the mixed refrigerant storage unit 30 via the gas phase refrigerant outlet 14e of the high-pressure side extraction unit 14 and the high-pressure side regulating valve 31.

[0127] In both the heating mode and the cooling mode, the refrigerant flow path from the downstream side of the ejector 12 to the upstream side of the first expansion valve 15 constitutes the high-pressure side flow path. Therefore, by opening the high-pressure side regulating valve 31 and connecting it to the high-pressure side flow path, the interior of the storage space 30b of the mixed refrigerant storage unit 30 can be changed to a high-pressure environment showing a pressure higher than the adsorption pressure of the adsorbent. In other words, by creating a high-pressure environment in the storage space 30b, the inflowing gas-phase refrigerant Rg can be adsorbed by the adsorbent filled inside the storage space 30b. Then, before transitioning to a completely stopped state, the control device 50 fully closes the high-pressure side regulating valve 31.

[0128] In this way, when the operation is stopped, as much of the refrigerant sealed in the cycle as possible is stored in a state where it is adsorbed in the adsorption material filled in the storage space 30b, thereby suppressing an increase in refrigerant pressure in the cycle when the operation is stopped.

[0129] Furthermore, with this configuration, it is not necessary to improve the pressure resistance of the entire cycle as long as the pressure resistance around the mixed refrigerant reservoir 30, the high-pressure side regulating valve 31, and the low-pressure side regulating valve 32 is improved. In other words, it is possible to efficiently take measures against the rise in refrigerant pressure in the cycle when operation is stopped.

[0130] As described above, the refrigeration cycle apparatus 10 according to the first embodiment creates a high-pressure environment inside the storage space 30b of the mixed refrigerant reservoir 30, allowing the refrigerant flowing into the storage space 30b to be adsorbed by the adsorbent. The refrigerant sealed inside the cycle is composed of the refrigerant circulating through the cycle and the refrigerant adsorbed to the adsorbent inside the storage space 30b. Therefore, by adsorbing the refrigerant to the adsorbent inside the storage space 30b, the amount of refrigerant circulating through the cycle can be reduced. In other words, when the amount of refrigerant circulating through the cycle is in excess of the required amount, the refrigeration cycle apparatus 10 can adjust the amount of refrigerant circulating through the cycle to bring it closer to the required amount.

[0131] Furthermore, the refrigeration cycle apparatus 10 can desorb the refrigerant from the adsorbent by creating a low-pressure environment inside the storage space 30b. This allows the amount of refrigerant circulating through the cycle to be increased by desorbing the refrigerant from the adsorbent inside the storage space 30b. Therefore, when the amount of refrigerant is insufficient for the required amount, the refrigeration cycle apparatus 10 can adjust the amount of refrigerant circulating through the cycle to approach the required amount.

[0132] In this way, according to the refrigeration cycle device 10, by appropriately controlling the internal pressure of the mixed refrigerant storage section 30 and promoting the adsorption and desorption of the refrigerant to the adsorbent inside the storage space 30b, the amount of refrigerant circulating through the cycle can be adjusted to approach the required amount of refrigerant.

[0133] 4, in the refrigeration cycle apparatus 10 according to the first embodiment, the high-pressure side regulating valve 31 disposed on the inlet 30c side of the mixed refrigerant storage unit 30 is opened as an adjustment operation in an excess state. This allows the high-pressure side flow path of the cycle to communicate with the storage space 30b of the mixed refrigerant storage unit 30, and high-pressure refrigerant flowing through the high-pressure side flow path flows into the storage space 30b. This allows the refrigerant to be adsorbed by the adsorbent to flow into the storage space 30b, and the high-pressure refrigerant to transition the storage space 30b to a high-pressure environment, making it easy to perform the adjustment operation in an excess state.

[0134] 5, the refrigeration cycle apparatus 10 performs an adjustment operation in a shortage state by opening the low-pressure-side adjustment valve 32 disposed on the outlet 30d side of the mixed refrigerant storage section 30. This connects the interior of the storage space 30b to the low-pressure flow path of the cycle, transitioning the interior of the storage space 30b to a low-pressure environment and promoting desorption of the refrigerant from the adsorbent filled in the storage space 30b. Furthermore, since the refrigerant desorbed from the adsorbent inside the storage space 30b can be merged into the flow of refrigerant circulating through the cycle, the amount of refrigerant circulating through the cycle can be adjusted to approach the required amount in a shortage state.

[0135] Furthermore, when stopping the circulation of the mixed refrigerant in the cycle, the refrigeration cycle apparatus 10 opens the high-pressure side regulating valve 31 while fully closing the low-pressure side regulating valve 32 in advance, thereby connecting the high-pressure side flow path of the cycle with the storage space 30b of the mixed refrigerant storage unit 30. As a result, the gas-phase refrigerant Rg extracted from the mixed refrigerant Rm in the high-pressure side extraction unit 14 flows into the storage space 30b of the mixed refrigerant storage unit 30 via the gas-phase refrigerant outlet 14e of the high-pressure side extraction unit 14 and the high-pressure side regulating valve 31.

[0136] That is, when the operation of the cycle is stopped, the storage space 30b is brought into a high-pressure environment in advance, so that the gas-phase refrigerant Rg that has flowed in can be adsorbed by the adsorbent filled inside the storage space 30b. As a result, in the refrigeration cycle device 10, when the operation is stopped, as much of the refrigerant sealed in the cycle as possible is stored in a state in which it is adsorbed by the adsorbent filled inside the storage space 30b, thereby suppressing an increase in refrigerant pressure in the cycle when the operation is stopped.

[0137] 1 and other figures, the inlet 30c of the mixed refrigerant storage section 30 is connected to the gas phase refrigerant outlet 14e side of the high pressure side extraction section 14. In the high pressure side extraction section 14, the gas phase refrigerant Rg that is partially extracted from the mixed refrigerant Rm that contains the adsorbent flows into the mixed refrigerant storage section 30, so that excess refrigerant can be reliably stored inside the mixed refrigerant storage section 30.

[0138] Second Embodiment Next, a second embodiment, which differs from the above-described embodiment, will be described with reference to Figures 6 to 8. The air conditioner 1 according to the second embodiment includes a heat medium circuit 40 corresponding to a temperature adjustment unit in addition to a refrigeration cycle unit 10 and a control device 50.

[0139] The air conditioner 1 according to the second embodiment has the same configuration as that of the first embodiment, except for the configuration and operation of the heat medium circuit 40, which corresponds to the temperature adjustment unit. Therefore, other configurations of the air conditioner 1 and the refrigeration cycle device 10 according to the second embodiment (e.g., the mixed refrigerant storage unit 30, the control device 50, etc.) are the same as those of the first embodiment described above, and therefore will not be described again.

[0140] 6, the air conditioner 1 according to the second embodiment is provided with a heat medium circuit 40 for circulating a heat medium. The heat medium circuit 40 has a heat medium-refrigerant heat exchanger 41, a temperature adjustment heat exchange unit 42, and a heat medium pump 43, and adjusts the temperature of the mixed refrigerant reservoir 30 by utilizing the heat of the refrigerant circulating through the cycle in the refrigeration cycle device 10. The heat medium in the heat medium circuit 40 can be, for example, a solution containing ethylene glycol, antifreeze, or the like.

[0141] The heat medium-refrigerant heat exchanger 41 has a heat medium passage through which the heat medium of the heat medium circuit 40 flows and a refrigerant passage through which the refrigerant (i.e., the mixed refrigerant) of the refrigeration cycle apparatus 10 flows. The heat medium-refrigerant heat exchanger 41 is formed of the same type of metal (e.g., aluminum alloy) that has excellent heat conductivity, and each component is integrated by brazing. As a result, in the heat medium-refrigerant heat exchanger 41, the mixed refrigerant flowing through the refrigerant passage and the heat medium flowing through the heat medium passage can exchange heat with each other.

[0142] The inlet side of the heat medium passage of the heat medium refrigerant heat exchanger 41 is connected to the discharge port of the heat medium pump 43, and the outlet side of the heat medium passage is connected to the inlet side of the temperature adjustment heat exchanger 42. As shown in Figure 6, the inlet side of the refrigerant passage of the heat medium refrigerant heat exchanger 41 is connected to the outlet side of the first expansion valve 15, and the outlet side of the refrigerant passage is connected to the mixed refrigerant inlet side of the outdoor heat exchanger 16.

[0143] The temperature-regulating heat exchange unit 42 is a heat exchange unit that exchanges heat between the heat medium circulating through the heat medium circuit 40 and the adsorbent filled in the storage space 30b of the mixed refrigerant storage unit 30. The temperature-regulating heat exchange unit 42 is configured by forming a flow path through which the heat medium flows within a case that stores the mixed refrigerant storage unit 30. The heat medium outlet of the temperature-regulating heat exchange unit 42 is connected to the suction port side of the heat medium pump 43.

[0144] In addition, since the storage container 30a of the mixed refrigerant storage section 30 in the second embodiment is made of a material with good thermal conductivity, heat exchange can be performed between the heat medium flowing through the heat medium flow path of the temperature adjustment heat exchange section 42 and the adsorbent filled in the storage space 30b.

[0145] The heat medium pump 43 is a pump that pumps the heat medium to circulate it in the heat medium circuit 40. The heat medium pump 43 is an electric pump whose rotation speed (i.e., pumping capacity) is controlled by a control voltage output from the control device 50. The discharge port of the heat medium pump 43 is connected to the inlet side of the heat medium passage of the heat medium-refrigerant heat exchanger 41.

[0146] The air conditioner 1 according to the second embodiment can operate in a cooling mode and a heating mode, similar to the first embodiment. In the second embodiment, the heating mode can also be cited as an operation mode in which an excessive state is likely to occur.

[0147] The heating mode in the second embodiment is similar to the heating mode in the first embodiment, except that the circulation of the heat medium in the heat medium circuit 40 is stopped. Therefore, a description of the operation of the air conditioner 1 in the heating mode in the second embodiment will be omitted. The behavior of the mixed refrigerant Rm in the heating mode in the second embodiment is similar to that in the first embodiment.

[0148] Here, the refrigeration cycle apparatus 10 according to the second embodiment can also perform an adjustment operation in an excess state. Unlike the first embodiment, the adjustment operation in an excess state in the second embodiment includes control of the heat medium circuit 40, which is a temperature adjustment unit. Therefore, the adjustment operation in an excess state in the refrigeration cycle apparatus 10 according to the second embodiment will be described with reference to Fig. 7 .

[0149] In the adjustment operation for the excess state in the second embodiment, the control device 50 fully closes the low-pressure side adjustment valve 32 and opens the high-pressure side adjustment valve 31. As a result, the gas phase refrigerant Rg extracted from the mixed refrigerant Rm in the high-pressure side extraction unit 14 flows into the storage space 30b of the mixed refrigerant storage unit 30 via the gas phase refrigerant outlet 14e of the high-pressure side extraction unit 14 and the high-pressure side adjustment valve 31.

[0150] In the heating mode, the refrigerant flow path from the downstream side of the ejector 12 to the upstream side of the first expansion valve 15 constitutes a high-pressure side flow path. As shown in Fig. 7, the high-pressure side extraction unit 14 is disposed between the downstream side of the ejector 12 and the upstream side of the first expansion valve 15, and therefore constitutes part of the high-pressure side flow path.

[0151] Therefore, by opening the high-pressure side regulating valve 31 and connecting to the high-pressure side flow path, the inside of the storage space 30b of the mixed refrigerant storage unit 30 can be changed to a high-pressure environment showing a pressure higher than the adsorption pressure of the adsorbent. In other words, by creating a high-pressure environment in the storage space 30b, the gas-phase refrigerant Rg that has flowed in can be adsorbed by the adsorbent filled inside the storage space 30b.

[0152] That is, in the second embodiment, too, the excess refrigerant in the cycle can be stored inside the storage space 30b by increasing the number of adsorbents that adsorb the refrigerant through control of the aperture of the high-pressure side regulating valve 31. As a result, in the refrigeration cycle device 10 in an excess state, the amount of refrigerant circulating in the cycle can be brought closer to the required amount of refrigerant, and the refrigerant amount can be adjusted to an appropriate amount.

[0153] In the adjustment operation in the case of an excess state according to the second embodiment, the control device 50 operates the heat medium pump 43 to circulate the heat medium in the heat medium circuit 40. In the heating mode according to the second embodiment, the first expansion valve 15 is controlled to a throttle state, and therefore the low-pressure mixed refrigerant Rm flows through the refrigerant passage of the heat medium-refrigerant heat exchanger 41. Therefore, the heat of the heat medium flowing through the heat medium passage of the heat medium-refrigerant heat exchanger 41 is absorbed by the low-pressure mixed refrigerant Rm flowing through the refrigerant passage, and is cooled.

[0154] As described above, in the storage space 30b of the mixed refrigerant storage unit 30, as the high-pressure gas-phase refrigerant Rg flows in, the refrigerant is adsorbed by the adsorbent filled therein. As the refrigerant is adsorbed into the adsorbent, heat (i.e., internal energy) possessed by the adsorbed refrigerant is released as heat of adsorption. Therefore, in the temperature control heat exchange unit 42, the heat of adsorption generated inside the mixed refrigerant storage unit 30 is released to the heat medium.

[0155] That is, in the refrigeration cycle apparatus 10 of the second embodiment, the heat of adsorption generated inside the mixed refrigerant storage section 30 during the adjustment operation in the excess state is dissipated to the mixed refrigerant circulating in the cycle via the heat medium in the heat medium circuit 40. As a result, the refrigeration cycle apparatus 10 of the second embodiment can suppress temperature changes caused by the heat of adsorption generated inside the mixed refrigerant storage section 30 during the adjustment operation in the excess state.

[0156] In the refrigeration cycle apparatus 10 according to the second embodiment, the cooling mode can also be cited as an operation mode in which a shortage state is likely to occur. The cooling mode according to the second embodiment is similar to the cooling mode according to the first embodiment, except that the circulation of the heat medium in the heat medium circuit 40 is stopped. Therefore, a description of the operation of the air conditioner 1 in the cooling mode according to the second embodiment will be omitted. The behavior of the mixed refrigerant Rm in the cooling mode according to the second embodiment is similar to that of the first embodiment.

[0157] Here, the refrigeration cycle apparatus 10 according to the second embodiment can also perform an adjustment operation in a shortage state. Unlike the first embodiment, the adjustment operation in a shortage state in the second embodiment includes control of the heat medium circuit 40, which is a temperature adjustment unit. Therefore, the adjustment operation in a shortage state in the refrigeration cycle apparatus 10 according to the second embodiment will be described with reference to Fig. 8 .

[0158] In the adjustment operation in the case of a shortage state, the control device 50 opens the low-pressure-side adjustment valve 32 while keeping the high-pressure-side adjustment valve 31 fully closed. This causes the storage space 30b of the mixed refrigerant storage unit 30 to communicate with the second connection unit 25b of the refrigeration cycle apparatus 10. In the cooling mode, the refrigerant flow path from the outlet side of the second expansion valve 18 to the mixed refrigerant inlet 20c of the low-pressure-side extraction unit 20 forms a low-pressure-side flow path.

[0159] Therefore, by opening the low-pressure side adjustment valve 32 and connecting to the second connection part 25b, the interior of the mixed refrigerant storage part 30 can be connected to the low-pressure side flow path. This changes the interior of the storage space 30b of the mixed refrigerant storage part 30 to a low-pressure environment that exhibits a pressure lower than the desorption pressure of the adsorbent. In other words, by creating a low-pressure environment in the storage space 30b, the gas-phase refrigerant Rg can be desorbed from the adsorbent that has filled the storage space 30b. Then, inside the storage space 30b, the gas-phase refrigerant Rg desorbed from the adsorbent merges with the flow of refrigerant circulating in the cycle via the low-pressure side adjustment valve 32 and the second connection part 25b.

[0160] That is, according to the refrigeration cycle apparatus 10 of the first embodiment, the refrigerant stored inside the mixed refrigerant storage section 30 can be added as refrigerant circulating through the cycle by reducing the amount of adsorbent that adsorbs the refrigerant through control of the aperture of the low-pressure side regulating valve 32. As a result, in the refrigeration cycle apparatus 10 in a shortage state, the amount of refrigerant circulating through the cycle can be brought closer to the required amount of refrigerant, and the refrigerant amount can be adjusted to an appropriate amount.

[0161] In the adjustment operation in the case of a shortage state according to the second embodiment, the control device 50 operates the heat medium pump 43 to circulate the heat medium in the heat medium circuit 40. In the cooling mode according to the second embodiment, the first expansion valve 15 is controlled to a fully open state, and therefore the mixed refrigerant Rm in a high-pressure state flows through the refrigerant passage of the heat medium-refrigerant heat exchanger 41. Therefore, the heat medium flowing through the heat medium passage of the heat medium-refrigerant heat exchanger 41 is heated by the heat released from the mixed refrigerant Rm in a high-pressure state flowing through the refrigerant passage.

[0162] As described above, in the storage space 30b of the mixed refrigerant storage unit 30, the low-pressure side adjustment valve 32 opens, creating a low-pressure environment inside the storage space 30b, causing the adsorbed refrigerant to be desorbed from the adsorbent filled therein. As the refrigerant is desorbed from the adsorbent, ambient heat is absorbed as desorption heat, decreasing the temperature inside the storage space 30b of the mixed refrigerant storage unit 30. As a result, in the temperature adjustment heat exchange unit 42, heat is exchanged between the heat medium in the heat medium circuit 40 and the heat absorber filled in the storage space 30b of the mixed refrigerant storage unit 30, and the heat of the heat medium is used as a heat source for desorption heat.

[0163] That is, in the refrigeration cycle apparatus 10 of the second embodiment, in the adjustment operation in the shortage state, the heat of the mixed refrigerant circulating in the cycle can be used as a heat source for desorption heat inside the mixed refrigerant storage section 30 via the heat medium of the heat medium circuit 40. As a result, according to the refrigeration cycle apparatus 10 of the second embodiment, in the adjustment operation in the shortage state, it is possible to suppress temperature changes caused by desorption inside the mixed refrigerant storage section 30.

[0164] As described above, according to the refrigeration cycle device 10 of the second embodiment, even when the heat medium circuit 40 is provided as a temperature adjustment unit during adjustment operation using the mixed refrigerant storage unit 30, it is possible to obtain the same effects as those of the above-described embodiment due to the configuration and operation.

[0165] 7, during the adjustment operation in the excess state, the refrigeration cycle apparatus 10 uses the heat medium circuit 40, which is a temperature adjustment unit, to cool the storage space 30b of the mixed refrigerant storage unit 30. This makes it possible to suppress temperature changes caused by heat of adsorption that occurs when the refrigerant is adsorbed by the heat absorber in the storage space 30b during the adjustment operation in the excess state.

[0166] 8, during the adjustment operation in the shortage state, the refrigeration cycle apparatus 10 uses the heat medium circuit 40, which is a temperature adjustment unit, to heat the storage space 30b of the mixed refrigerant storage unit 30. As a result, the adjustment operation in the shortage state can suppress temperature changes caused by desorption heat generated when the refrigerant is desorbed from the adsorbent in the storage space 30b.

[0167] In the refrigeration cycle apparatus 10 according to the second embodiment, during the operation for adjusting the excess state, the heat medium circuit 40 absorbs heat resulting from the heat of adsorption generated in the storage space 30b of the mixed refrigerant storage section 30, via the heat medium, into the refrigerant flowing through the low-pressure side flow path in the heating mode cycle. This allows the refrigeration cycle apparatus 10 to suppress temperature changes resulting from the heat of adsorption generated during the operation for adjusting the excess state by utilizing the circulation of the refrigerant in the cycle.

[0168] In the refrigeration cycle apparatus 10 according to the second embodiment, during the operation for adjusting the shortage state, the heat medium circuit 40 uses the heat of the refrigerant flowing through the high-pressure side flow path in the cycle in the cooling mode as a heat source to heat the storage space 30b of the mixed refrigerant storage section 30, where desorption heat is generated. As a result, the refrigeration cycle apparatus 10 can suppress temperature changes caused by desorption heat generated during the operation for adjusting the shortage state by utilizing the circulation of the refrigerant in the cycle.

[0169] Third Embodiment Next, a third embodiment, which differs from the above-described embodiments, will be described with reference to Figures 9 to 11. Similar to the above-described embodiments, the refrigeration cycle device 10 according to the third embodiment is applied to an air conditioner 1. The air conditioner 1 according to the third embodiment includes the refrigeration cycle device 10 and a control device 50.

[0170] As shown in Fig. 9, the configuration of the refrigeration cycle apparatus 10 according to the third embodiment is different from that of the above-described embodiment in terms of the circuit configuration. In this respect, the components of the refrigeration cycle apparatus 10 according to the third embodiment are common to the components of the refrigeration cycle apparatus 10 in the above-described embodiment. Therefore, for the components that have already been described in the above-described embodiment, a description of the common technical matters will be omitted, and only differences from the above-described embodiment will be described.

[0171] The overall configuration of a refrigeration cycle apparatus 10 according to the third embodiment will be described with reference to Fig. 9. As shown in Fig. 9, the refrigeration cycle apparatus 10 according to the third embodiment, like the above-described embodiments, includes a compressor 11, an ejector 12, a heat-dissipation heat exchanger 13, an outdoor heat exchanger 16, a solenoid valve 17, a heat-absorption heat exchanger 19, and a low-pressure-side extraction section 20. Furthermore, the refrigeration cycle apparatus 10 according to the third embodiment includes a first three-way valve 22, an expansion valve 23, and a second three-way valve 24, and is also provided with a mixed refrigerant reservoir 30, a first flow control valve 36, and a second flow control valve 37.

[0172] 9, the compressor 11 of the refrigeration cycle apparatus 10 according to the third embodiment is a refrigerant compression unit that draws in, compresses, and discharges the refrigerant extracted by the low-pressure side extraction unit 20, as in the above-described embodiments. As the compressor 11 according to the third embodiment, for example, an electric compressor can be used, as in the above-described embodiments.

[0173] The inlet side of a nozzle portion 12a of an ejector 12 is connected to the discharge port of the compressor 11. The ejector 12 according to the third embodiment includes the nozzle portion 12a, the body portion 12b, the suction port 12c, the suction passage 12d, the mixing portion 12e, and the pressure increasing portion 12f, similar to the above-described embodiments.

[0174] The ejector 12 transports the mixed refrigerant flowing out from the low-pressure side extraction section 20 to the discharged refrigerant side by using the pressure energy of the discharged refrigerant discharged from the compressor 11. Then, the ejector 12 uses the pressure energy of the discharged refrigerant to mix the mixed refrigerant flowing out from the low-pressure side extraction section 20 with the injected refrigerant, which is the discharged refrigerant that has consumed the pressure energy.

[0175] The outlet of the pressure increasing section 12f of the ejector 12 is connected to the mixed refrigerant inlet side of the heat dissipation heat exchanger 13. The heat dissipation heat exchanger 13 exchanges heat between the mixed refrigerant flowing out from the ejector 12 and the ventilation air sent into the room, which is the space to be air-conditioned, and dissipates the heat of the mixed refrigerant to the ventilation air.

[0176] The mixed refrigerant outlet of the heat dissipation heat exchanger 13 is connected to one of the inlet and outlet sides of a first three-way valve 22. The first three-way valve 22 is a multi-way valve that has three inlet and outlet ports and can switch flow paths by selectively connecting at least two of the inlet and outlet ports. The operation of the first three-way valve 22 is controlled by a control signal output from the control device 50.

[0177] One of the inlet / outlet ports of the fourth connection part 25d in the form of a three-way joint is connected to the other inlet / outlet port of the first three-way valve 22. The other of the inlet / outlet ports of the first three-way valve 22 is connected to the other inlet / outlet port of the second connection part 25b.

[0178] The fourth connection portion 25d is configured as a three-way joint and has three inlet and outlet ports. As described above, one of the inlet and outlet ports of the fourth connection portion 25d is connected to the other inlet and outlet port of the first three-way valve 22. The other of the inlet and outlet ports of the fourth connection portion 25d is connected to one of the inlet and outlet ports of the fifth connection portion 25e via the first flow control valve 36 (described later). The other of the inlet and outlet ports of the fourth connection portion 25d is connected to the other of the inlet and outlet ports of the sixth connection portion 25f via the first flow path 26.

[0179] The refrigeration cycle apparatus 10 according to the third embodiment has a fourth connection portion 25d to a seventh connection portion 25g, which are configured similarly to the first connection portion 25a to the third connection portion 25c of the above-described embodiment.

[0180] The first flow control valve 36 is one of the flow control valves for adjusting the amount of adsorbent stored inside the mixed refrigerant storage unit 30 of the third embodiment. The first flow control valve 36 adjusts the opening degree of the refrigerant flow path connecting the fourth connection part 25 d and the fifth connection part 25 e. The operation of the first flow control valve 36 is controlled in accordance with a control signal output from the control device 50.

[0181] As described above, one of the inlet / outlet ports of the fifth connection part 25e is connected to the outlet side of the first flow control valve 36. The other of the inlet / outlet port of the three-way joint-shaped fifth connection part 25e is connected to the mixed refrigerant inlet side of the outdoor heat exchanger 16. The other of the inlet / outlet port of the fifth connection part 25e is connected to the other of the inlet / outlet port of the seventh connection part 25g via the second flow path 27.

[0182] The outdoor heat exchanger 16 has the same configuration as in the above-described embodiment. The outdoor heat exchanger 16 exchanges heat between the mixed refrigerant flowing therethrough and outside air blown outside by a blower fan (not shown). An inlet of a first connection part 25a is connected to a mixed refrigerant outlet of the outdoor heat exchanger 16. One outlet of the three-way joint-shaped first connection part 25a is connected to one inlet / outlet of the second connection part 25b. One inlet side of a third connection part 25c is connected to the other outlet of the first connection part 25a via a bypass flow path 21.

[0183] A solenoid valve 17 is disposed in the bypass flow path 21. The solenoid valve 17 is the same as in the above-described embodiment, and its operation is controlled in accordance with a control signal output from the control device 50.

[0184] The second connection part 25b according to the third embodiment is formed as a three-way joint, and as described above, the other inlet / outlet of the second connection part 25b is connected to the other inlet / outlet of the first three-way valve 22. The other inlet / outlet of the second connection part 25b is connected to the mixed refrigerant inlet 35c of the mixed refrigerant reservoir 30 according to the third embodiment.

[0185] The mixed refrigerant storage section 30 according to the third embodiment is formed by a hollow, bottomed, cylindrical metallic container that defines a space inside, and has a lower space 35a, an upper space 35b, a mixed refrigerant inlet 35c, a mixed refrigerant outlet 35d, a gas-phase refrigerant outlet 35e, and a filter 35f.

[0186] In the third embodiment, the mixed refrigerant reservoir 30 is disposed so that its axial direction is vertical. A flat filter 35f is disposed in the internal space of the mixed refrigerant reservoir 30.

[0187] The filter 35f vertically divides the internal space of the mixed refrigerant storage section 30 into an upper space 35b and a lower space 35a. The filter 35f has selective permeability that allows the high-pressure gas phase refrigerant Rg separated from the mixed refrigerant to pass through, but prohibits at least the adsorbent from passing through.

[0188] The lower space 35a is connected to a mixed refrigerant inlet 35c and a mixed refrigerant outlet 35d of the mixed refrigerant storage section 30. The lower space 35a is configured to extract gas phase refrigerant Rg from the mixed refrigerant by utilizing the difference in specific gravity between the refrigerant and the adsorbent.

[0189] The volume of the lower space 35a is set so that when the mixed refrigerant in the lower space 35a becomes a mixed refrigerant in which liquid-phase refrigerant is mixed with the adsorbent, the lower space 35a can be used as a liquid storage section for storing surplus refrigerant in the cycle. As a result, in the mixed refrigerant storage section 30 according to the third embodiment, gas-phase refrigerant is extracted into the upper space 35b.

[0190] The mixed refrigerant outlet 35d is an outlet for discharging the mixed refrigerant stored in the lower space 35a (i.e., the remaining mixed refrigerant after the gas phase refrigerant has been extracted). The mixed refrigerant outlet 35d is formed in the center of the bottom surface of the mixed refrigerant storage section 30. One of the inlet / outlet ports of the sixth connection part 25f is connected to the mixed refrigerant outlet 35d.

[0191] The upper space 35b is connected to a gas phase refrigerant outlet 35e of the mixed refrigerant storage section 30. The gas phase refrigerant outlet 35e is an outlet through which the high-pressure side gas phase refrigerant Rg that has passed through the filter 35f flows out. The gas phase refrigerant outlet 35e is formed on the top surface of the mixed refrigerant storage section 30. The gas phase refrigerant outlet 35e of the mixed refrigerant storage section 30 is connected to the inlet side of the expansion valve 23.

[0192] As described above, the other inlet / outlet of the three-way joint-like sixth connection part 25f is connected to the other inlet / outlet of the fourth connection part 25d via the first flow path 26. The other inlet / outlet of the sixth connection part 25f is connected to one of the inlet / outlets of the seventh connection part 25g via the second flow control valve 37.

[0193] The second flow control valve 37 is one of the flow control valves for adjusting the amount of adsorbent stored inside the mixed refrigerant storage unit 30 of the third embodiment. The second flow control valve 37 adjusts the opening degree of the refrigerant flow path connecting the sixth connection part 25 f and the seventh connection part 25 g. The operation of the second flow control valve 37 is controlled in accordance with a control signal output from the control device 50.

[0194] As described above, the expansion valve 23 is connected to the gas phase refrigerant outlet 35e of the mixed refrigerant storage section 30 according to the third embodiment. The expansion valve 23 is configured similarly to the first expansion valve 15 and the second expansion valve 18 according to the above-described embodiments. The expansion valve 23 according to the third embodiment depressurizes the gas phase refrigerant extracted in the mixed refrigerant storage section 30. Furthermore, the expansion valve 23 is a flow rate adjustment section that adjusts the flow rates of the gas phase refrigerant and adsorbent flowing from the mixed refrigerant storage section 30 to the second three-way valve 24. The operation of the expansion valve 23 is controlled in accordance with a control signal output from the control device 50.

[0195] A second three-way valve 24 is connected to the refrigerant outlet side of the expansion valve 23. Like the first three-way valve 22, the second three-way valve 24 has three inlet and outlet ports and is a multi-way valve that can switch flow paths by selectively connecting at least two of the inlet and outlet ports. The operation of the second three-way valve 24 is controlled by a control signal output from the control device 50.

[0196] The other inlet / outlet of the seventh connection part 25g in the form of a three-way joint is connected to the other inlet / outlet of the second three-way valve 24. The other inlet / outlet of the second three-way valve 24 is connected to the other inlet / outlet side of the seventh connection part 25g via a second flow path 27.

[0197] The seventh connection part 25g is formed as a three-way joint having three inlet and outlet ports. As described above, the second flow control valve 37 is connected to one of the inlet and outlet ports of the seventh connection part 25g, and the second three-way valve 24 is connected to the other of the inlet and outlet ports of the seventh connection part 25g. The mixed refrigerant inlet side of the heat-absorbing heat exchanger 19 is connected to the other of the inlet and outlet ports of the seventh connection part 25g.

[0198] The heat-absorbing heat exchanger 19 exchanges heat between a mixed refrigerant containing the refrigerant decompressed by the expansion valve 23 and the blown air blown into the room from a blower (not shown). The heat-absorbing heat exchanger 19 is a heat-absorbing part that cools the blown air by desorbing the refrigerant from an adsorbent contained in the mixed refrigerant to exert a heat absorption effect.

[0199] A three-way joint-shaped third connection part 25c is disposed on the mixed refrigerant outlet side of the heat absorption heat exchanger 19. The mixed refrigerant outlet of the heat absorption heat exchanger 19 is connected to one inlet of the third connection part 25c. The other inlet of the third connection part 25c is connected to the other outlet of the first connection part 25a via the bypass flow path 21. The outlet of the third connection part 25c is connected to the mixed refrigerant inlet 20c of the low-pressure side extraction part 20.

[0200] The low-pressure side extraction unit 20 extracts a portion of the gas-phase refrigerant not containing any adsorbent from the mixed refrigerant flowing out from the third connection unit 25c. The low-pressure side extraction unit 20 can also be referred to as a low-pressure side separation unit that separates the mixed refrigerant from the refrigerant not containing any adsorbent.

[0201] The basic configuration of the low-pressure side extraction section 20 according to the third embodiment is the same as that of the low-pressure side extraction section 20 according to the above-described embodiment. Accordingly, the low-pressure side extraction section 20 includes a lower space 20a, an upper space 20b, a mixed refrigerant inlet 20c, a mixed refrigerant outlet 20d, a gas-phase refrigerant outlet 20e, and a filter 20f. The mixed refrigerant outlet 20d of the low-pressure side extraction section 20 is connected to the suction port 12c side of the ejector 12. The gas-phase refrigerant outlet 20e of the low-pressure side extraction section 20 is connected to the suction port side of the compressor 11.

[0202] The control system of the air conditioner 1 according to the third embodiment will now be described. The air conditioner 1 according to the third embodiment has a control device 50. The control device 50 has a well-known microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuits. As in the above-described embodiments, the control device 50 controls the operation of various control target devices connected to the output side based on the results of calculations and processing.

[0203] 9, in the first embodiment, the output side of the control device 50 is connected to the compressor 11, the solenoid valve 17, the first three-way valve 22, the expansion valve 23, the second three-way valve 24, the first flow control valve 36, and the second flow control valve 37 as controlled devices. The input side of the control device 50 is connected to a group of various control sensors similar to those in the above-described embodiments.

[0204] The air conditioner 1 according to the third embodiment can operate in a cooling mode and a heating mode, similar to the above-described embodiments. In the third embodiment, the heating mode can also be cited as an operation mode in which an excessive state is likely to occur.

[0205] When the air conditioner 1 according to the third embodiment operates in the heating mode, the control device 50 controls the compressor 11 to achieve a predetermined refrigerant discharge capacity. The control device 50 also controls the expansion valve 23 to a predetermined throttle opening for the heating mode. The control device 50 then controls the solenoid valve 17 to be fully open.

[0206] The control device 50 controls the operation of the first three-way valve 22 to communicate the inlet / outlet on the heat dissipation heat exchanger 13 side with the inlet / outlet on the second connection part 25b side and to close the inlet / outlet on the fourth connection part 25d side. The control device 50 also controls the operation of the second three-way valve 24 to communicate the inlet / outlet on the expansion valve 23 side with the inlet / outlet on the fifth connection part 25e side and to close the inlet / outlet on the seventh connection part 25g side.

[0207] In the refrigeration cycle device 10 according to the third embodiment, the apertures of the first flow control valve 36 and the second flow control valve 37 are adjusted to adjust the amount of the adsorbent that has adsorbed the refrigerant and is stored inside the mixed refrigerant storage section 30. In the normal heating mode, the aperture of the first flow control valve 36 is controlled to a predetermined aperture, and the aperture of the second flow control valve 37 is controlled to be in a fully closed state.

[0208] When the heating mode is executed, the gas-phase refrigerant Rg discharged from the compressor 11 flows into the nozzle portion 12a of the ejector 12. The ejector 12 according to the third embodiment functions in the same manner as the above-described embodiments. In the pressure-boosting portion 12f of the ejector 12, the velocity energy of the mixed refrigerant Rm is converted into pressure energy by the action of shock waves generated by the discharge-side injected refrigerant and the expansion of the passage cross-sectional area. This increases the pressure of the mixed refrigerant Rm. Then, as the pressure of the mixed refrigerant Rm increases in the pressure-boosting portion 12f, the adsorbent adsorbs the refrigerant.

[0209] The mixed refrigerant Rm flowing out from the pressure boosting section 12f of the ejector 12 flows into the heat dissipation heat exchanger 13. The mixed refrigerant Rm that flows into the heat dissipation heat exchanger 13 dissipates heat to the ventilation air that is blown into the room by the blower. More specifically, when the refrigerant contained in the mixed refrigerant Rm that flows into the heat dissipation heat exchanger 13 is adsorbed into the adsorbent, it dissipates the internal energy stored in the adsorbent to the ventilation air as heat of adsorption. This heats the ventilation air that is supplied to the space to be air-conditioned, thereby achieving heating of the room.

[0210] The mixed refrigerant flowing out of the heat dissipation heat exchanger 13 flows through the first three-way valve 22 and the second connection part 25b to the mixed refrigerant inlet 35c of the mixed refrigerant storage part 30, and then flows into the lower space 35a through the mixed refrigerant inlet 35c. The refrigerant contained in the mixed refrigerant Rm that has flowed into the lower space 35a flows into the upper space 35b through the filter 35f. The gas-phase refrigerant Rg that has flowed out of the upper space 35b flows out through the gas-phase refrigerant outlet 35e. The mixed refrigerant Rm that has flowed out of the lower space 35a flows out through the mixed refrigerant outlet 35d.

[0211] The gas-phase refrigerant Rg flowing out from the gas-phase refrigerant outlet 35e flows into the expansion valve 23 and is depressurized. More specifically, the gas-phase refrigerant Rg flowing out from the mixed refrigerant storage section 30 and depressurized by the expansion valve 23 flows into the second flow path 27 via the second three-way valve 24. After flowing through the second flow path 27, the gas-phase refrigerant Rg flows into the fifth connection section 25e.

[0212] Because the second flow control valve 37 is controlled to a fully closed state, the mixed refrigerant Rm that flows out from the mixed refrigerant outlet 35d flows into the first flow path 26 via the sixth connection part 25f. Because the first flow control valve 36 is opened at a predetermined aperture, the mixed refrigerant Rm that has circulated through the first flow path 26 flows into the fifth connection part 25e via the fourth connection part 25d and the first flow control valve 36. Therefore, the flow rate of the mixed refrigerant Rm that flows out of the mixed refrigerant storage part 30 is adjusted according to the aperture of the first flow control valve 36.

[0213] At the fifth connection portion 25e, the mixed refrigerant Rm that has flowed through the first flow path 26 and the gas-phase refrigerant Rg that has flowed through the second flow path 27 join together to form the mixed refrigerant Rm. The mixed refrigerant Rm that flows out of the fifth connection portion 25e flows into the outdoor heat exchanger 16.

[0214] The mixed refrigerant Rm that has flowed into the outdoor heat exchanger 16 absorbs heat from the outside air blown by a blower fan (not shown). More specifically, the refrigerant contained in the mixed refrigerant Rm that has flowed into the outdoor heat exchanger 16 is desorbed from the adsorbent as the pressure drops. At this time, the adsorbent absorbs heat from the outside air as heat of desorption.

[0215] The mixed refrigerant Rm flowing out of the outdoor heat exchanger 16 flows into the bypass passage 21 via the first connection part 25a. The mixed refrigerant Rm that has flowed into the bypass passage 21 flows through the solenoid valve 17 and the third connection part 25c, and then through the mixed refrigerant inlet 20c of the low-pressure side extraction part 20 into the lower space 20a.

[0216] A portion of the refrigerant contained in the mixed refrigerant Rm that has flowed into the lower space 20a flows into the upper space 20b via the filter 20f. The gas-phase refrigerant Rg that has flowed out of the upper space 20b is drawn into the compressor 11 and compressed again. The mixed refrigerant Rm that has flowed out of the lower space 20a is drawn through the suction port 12c of the ejector 12.

[0217] In this way, in the refrigeration cycle apparatus 10 according to the third embodiment, heat absorbed from outside air in the outdoor heat exchanger 16 can be used to heat the blown air in the heat dissipation heat exchanger 13. That is, the air conditioner 1 according to the third embodiment can heat the room, which is the space to be air-conditioned, by using outside air as a heat source.

[0218] In the refrigeration cycle device 10, when the amount of refrigerant in the cycle exceeds the required amount determined by the air conditioning load and the circuit configuration of the cycle, the amount of refrigerant in the cycle can be adjusted to approach the required amount by utilizing the mixed refrigerant reservoir 30. The adjustment operation for the amount of refrigerant in the cycle in an excess state will be described with reference to FIG.

[0219] In the adjustment operation for the excess state, the control device 50 controls the aperture of the first flow control valve 36 to adjust the amount of adsorbent in a state in which the refrigerant is adsorbed inside the mixed refrigerant storage unit 30. Specifically, the control device 50 controls the aperture of the first flow control valve 36 to become smaller. As a result, the mixed refrigerant Rm containing the adsorbent in a state in which the refrigerant is adsorbed is stored inside the mixed refrigerant storage unit 30, and the amount of refrigerant circulating in the cycle is reduced to approach the required amount of refrigerant, thereby adjusting to an appropriate amount of refrigerant.

[0220] Next, the operation of the cooling mode, which is an operation mode in which a shortage state is likely to occur, will be described, and the operation of the mixed refrigerant storage unit 30 in a shortage state will be described with reference to Fig. 11. In the cooling mode, the required amount of refrigerant is likely to be large, and a shortage state is likely to occur.

[0221] When the air conditioner 1 according to the third embodiment operates in the cooling mode, the control device 50 controls the compressor 11 to achieve a predetermined refrigerant discharge capacity. The control device 50 also controls the expansion valve 23 to a predetermined opening for the cooling mode. The control device 50 then controls the solenoid valve 17 to be fully closed.

[0222] The control device 50 controls the operation of the first three-way valve 22 so that the inlet / outlet on the heat dissipation heat exchanger 13 side communicates with the inlet / outlet on the fourth connection part 25d side, and closes the inlet / outlet on the second connection part 25b side. The control device 50 also controls the operation of the second three-way valve 24 so that the inlet / outlet on the expansion valve 23 side communicates with the inlet / outlet on the seventh connection part 25g side, and closes the inlet / outlet on the fifth connection part 25e side.

[0223] In the refrigeration cycle device 10 according to the third embodiment, the apertures of the first flow control valve 36 and the second flow control valve 37 are adjusted to adjust the amount of the adsorbent that has adsorbed the refrigerant and is stored inside the mixed refrigerant storage section 30. In the normal heating mode, the first flow control valve 36 is controlled to be fully open, and the aperture of the second flow control valve 37 is controlled to be a predetermined aperture.

[0224] When the cooling mode is executed, the gas-phase refrigerant Rg discharged from the compressor 11 flows into the nozzle portion 12a of the ejector 12. The ejector 12 according to the third embodiment functions similarly to the above-described embodiments. In the pressure-boosting portion 12f of the ejector 12, the velocity energy of the mixed refrigerant Rm is converted into pressure energy by the action of shock waves generated by the discharge-side injected refrigerant and the expansion of the passage cross-sectional area. This increases the pressure of the mixed refrigerant Rm. Then, as the pressure of the mixed refrigerant Rm increases in the pressure-boosting portion 12f, the adsorbent adsorbs the refrigerant.

[0225] The mixed refrigerant Rm flowing out from the pressure boosting section 12f of the ejector 12 flows into the heat dissipation heat exchanger 13. Here, in the cooling mode, operational control such as changing the blowing air path is performed to reduce the amount of blowing air supplied to the heat dissipation heat exchanger 13. For example, the blowing air path may be changed so as to bypass the heat dissipation heat exchanger 13. As a result, the mixed refrigerant Rm that has flowed into the heat dissipation heat exchanger 13 flows out of the heat dissipation heat exchanger 13 without dissipating heat to the blowing air.

[0226] In the cooling mode, the first three-way valve 22 has an inlet / outlet on the heat dissipation heat exchanger 13 side and an inlet / outlet on the fourth connection part 25d side connected to each other, and the first flow control valve 36 is controlled to a fully open state. Therefore, the mixed refrigerant Rm flowing out of the heat dissipation heat exchanger 13 flows into the outdoor heat exchanger 16 via the first three-way valve 22, the fourth connection part 25d, the first flow control valve 36, and the fifth connection part 25e.

[0227] The mixed refrigerant Rm that has flowed into the outdoor heat exchanger 16 releases heat to the outside air blown by a blower fan (not shown). More specifically, when the refrigerant contained in the mixed refrigerant Rm that has flowed into the outdoor heat exchanger 16 is adsorbed by the adsorbent, the refrigerant releases the internal energy stored in the adsorbent to the blown air as heat of adsorption.

[0228] Because the solenoid valve 17 is fully closed, the mixed refrigerant Rm flowing out of the heat dissipation heat exchanger 13 flows through the first connection portion 25a and the second connection portion 25b to the mixed refrigerant inlet 35c of the mixed refrigerant storage portion 30, and then flows from the mixed refrigerant inlet 35c into the lower space 35a. The refrigerant contained in the mixed refrigerant Rm that has flowed into the lower space 35a flows into the upper space 35b via the filter 35f. The gas-phase refrigerant Rg that has flowed out of the upper space 35b flows out through the gas-phase refrigerant outlet 35e. The mixed refrigerant Rm that has flowed out of the lower space 35a flows out through the mixed refrigerant outlet 35d.

[0229] The gas-phase refrigerant Rg flowing out from the gas-phase refrigerant outlet 35e flows into the expansion valve 23 and is depressurized. More specifically, the gas-phase refrigerant Rg flowing out from the mixed refrigerant storage section 30 and depressurized by the expansion valve 23 flows into the seventh connection section 25g via the second three-way valve 24.

[0230] The mixed refrigerant Rm flowing out from the mixed refrigerant outlet 35d flows into the seventh connection portion 25g via the sixth connection portion 25f and the second flow control valve 37, because the second flow control valve 37 is controlled to open at a degree of opening predetermined for the cooling mode. Therefore, the flow rate of the mixed refrigerant Rm flowing out from the mixed refrigerant storage portion 30 is adjusted according to the degree of opening of the second flow control valve 37.

[0231] At the seventh connection portion 25g, the mixed refrigerant Rm flowing from the sixth connection portion 25f and the gas phase refrigerant Rg flowing out from the expansion valve 23 join together to form the mixed refrigerant Rm. The mixed refrigerant Rm flowing out from the seventh connection portion 25g flows into the endothermic heat exchanger 19.

[0232] The mixed refrigerant Rm that flows into the heat absorption heat exchanger 19 absorbs heat from the blown air that is blown into the room by the blower. More specifically, the refrigerant contained in the mixed refrigerant Rm that flows into the heat absorption heat exchanger 19 is desorbed from the adsorbent as the pressure drops. At this time, the adsorbent absorbs the heat of the blown air as desorption heat. This allows the blown air that is supplied to the room, which is the space to be air-conditioned, to be cooled.

[0233] The mixed refrigerant Rm flowing out of the endothermic heat exchanger 19 flows through the third connection portion 25c and the mixed refrigerant inlet 20c of the low-pressure side extraction portion 20 into the lower space 20a. A portion of the refrigerant contained in the mixed refrigerant Rm that has flowed into the lower space 20a flows into the upper space 20b via the filter 20f. The gas-phase refrigerant Rg that has flowed out of the upper space 20b is drawn into the compressor 11 and compressed again. The mixed refrigerant Rm that has flowed out of the lower space 20a is drawn through the suction port 12c of the ejector 12.

[0234] In this way, in the refrigeration cycle apparatus 10 according to the third embodiment, heat can be dissipated to the outside air by the outdoor heat exchanger 16, and the blown air can be cooled by the heat absorption heat exchanger 19. That is, the air conditioner 1 according to the third embodiment can cool the room, which is the space to be air-conditioned.

[0235] In the refrigeration cycle device 10, when the amount of refrigerant in the cycle is less than the required amount determined by the air conditioning load and the circuit configuration of the cycle, the amount of refrigerant in the cycle can be adjusted to approach the required amount by utilizing the mixed refrigerant reservoir 30. The adjustment operation for the amount of refrigerant in the cycle in a shortage state will be described with reference to FIG.

[0236] In the adjustment operation in the case of a shortage, the control device 50 controls the aperture of the second flow control valve 37 to adjust the amount of adsorbent in which refrigerant is adsorbed inside the mixed refrigerant storage unit 30. Specifically, the control device 50 controls the aperture of the second flow control valve 37 to become larger. This actively causes the mixed refrigerant Rm containing the adsorbent in which refrigerant is adsorbed to flow out of the mixed refrigerant storage unit 30, thereby increasing the amount of refrigerant circulating in the cycle and bringing it closer to the required amount of refrigerant, thereby adjusting the amount of refrigerant to an appropriate level.

[0237] As described above, in the refrigeration cycle apparatus 10 according to the third embodiment, the amount of mixed refrigerant Rm flowing out from the mixed refrigerant outlet 35d of the mixed refrigerant storage section 30 is adjusted by controlling the operation of the first flow control valve 36 and the second flow control valve 37. Because the mixed refrigerant Rm is formed by mixing an adsorbent with a refrigerant, the adsorbent in a state in which the refrigerant is adsorbed also constitutes part of the mixed refrigerant Rm. Therefore, the refrigeration cycle apparatus 10 can adjust the amount of adsorbent in a state in which the refrigerant is adsorbed, stored in the mixed refrigerant storage section 30, by adjusting the amount of mixed refrigerant Rm flowing out from the mixed refrigerant outlet 35d.

[0238] The adsorbent stored inside the mixed refrigerant reservoir 30 and having adsorbed the refrigerant, together with the refrigerant circulating through the cycle, constitutes the refrigerant sealed inside the cycle. Therefore, according to the refrigeration cycle device 10, the amount of refrigerant circulating through the cycle can be increased or decreased by adjusting the amount of mixed refrigerant Rm flowing out from the mixed refrigerant outlet 35d through operation control of the first flow control valve 36 and the second flow control valve 37, thereby adjusting the amount of refrigerant circulating through the cycle to approach the required amount of refrigerant.

[0239] In the case of an excess state, the refrigeration cycle device 10 reduces the amount of mixed refrigerant Rm flowing out from the mixed refrigerant outlet 35d by controlling the operation of the first flow control valve 36 and the second flow control valve 37. This increases the amount of adsorbent that has adsorbed the refrigerant stored inside the mixed refrigerant reservoir 30, thereby reducing the amount of refrigerant circulating in the cycle and bringing it closer to the required amount of refrigerant.

[0240] Furthermore, in the event of a shortage, the refrigeration cycle device 10 controls the operation of the first flow control valve 36 and the second flow control valve 37 to increase the amount of adsorbent that has adsorbed the refrigerant stored inside the mixed refrigerant storage unit 30. This reduces the amount of adsorbent that has adsorbed the refrigerant stored inside the mixed refrigerant storage unit 30, and increases the amount of refrigerant circulating in the cycle, making it possible to approach the required amount of refrigerant.

[0241] The present disclosure is not limited to the above-described embodiments, and various modifications can be made as follows within the scope of the present disclosure.

[0242] In the above embodiment, an example in which the refrigeration cycle device 10 according to the present disclosure is applied to an air conditioner has been described, but the application of the refrigeration cycle device 10 according to the present disclosure is not limited to this. For example, the refrigeration cycle device 10 may be applied to a vehicle air conditioner, a freezing device, a refrigerator, etc.

[0243] In the above-described embodiment, the refrigerant used is R744 and the adsorbent is MOF. However, the present invention is not limited to this. As the refrigerant, other refrigerants such as R1234yf, R134a, R600a, R410A, R404A, R32, R407C, R290, ammonia, R1234ze, or a mixture thereof may be used as long as the conditions are met.

[0244] In addition to MOFs, zeolites, activated carbons, and hydrates may also be used as adsorbents in the present disclosure, as long as they satisfy the conditions.

[0245] Furthermore, in an adsorbent having pores formed therein, when the representative opening diameter of the pores on the surface of the adsorbent is defined as the average opening diameter, it is desirable that the representative diameter of the molecules constituting the refrigerant be smaller than the average opening diameter.

[0246] The representative opening diameter of a pore can be defined as the diameter of a circle having the average opening area of ​​the pore. The representative diameter of a refrigerant molecule can be defined as the diameter of a sphere having the average volume of the refrigerant molecule. The average volume of one molecule can be calculated by dividing the molecular weight of the refrigerant by the density of the refrigerant in the liquid phase at a predetermined reference temperature and Avogadro's constant.

[0247] In the first and second embodiments described above, the adsorbent stored inside the mixed refrigerant storage unit 30 may be any adsorbent capable of adsorbing and desorbing the refrigerant circulating through the cycle. For example, the adsorbent's adsorption start pressure and desorption start pressure may correspond to the high-pressure and low-pressure conditions of the refrigerant constituting the cycle. That is, the adsorbent stored inside the mixed refrigerant storage unit 30 may be of the same type as the adsorbent constituting the mixed refrigerant, or a different type of adsorbent may be used as long as it satisfies the above-mentioned conditions.

[0248] The features of the refrigeration cycle device disclosed in this specification are as follows: (Item 1) A refrigeration cycle device that circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent that adsorbs and desorbs the refrigerant, the refrigeration cycle device having a mixed refrigerant reservoir (30) connected to allow inflow and outflow of the refrigerant and storing the adsorbents in a state in which the refrigerant has been adsorbed, the amount of refrigerant circulating through the cycle is adjusted by adjusting the amount of the adsorbents in a state in which the refrigerant has been adsorbed within the mixed refrigerant reservoir, the mixed refrigerant reservoir has a storage space (30b) for storing the adsorbents, the mixed refrigerant reservoir creates a high-pressure environment within the storage space that is higher than the adsorption pressure of the adsorbents, thereby adsorbing the refrigerant that has flowed into the adsorbents, and the refrigerant is desorbed from the adsorbents in a state in which the refrigerant has been adsorbed, by creating a low-pressure environment within the storage space that is lower than the desorption pressure of the adsorbents. (Item 2) The refrigeration cycle device according to item 1, comprising: a pressure-boosting section (11, 12, 20) that pressurizes the mixed refrigerant; and a pressure-reducing section (15, 18) that depressurizes the mixed refrigerant pressurized by the pressure-boosting section, wherein the mixed refrigerant storage section connects a high-pressure side flow path, through which the refrigerant flows, from an outlet of the pressure-boosting section to an inlet of the pressure-reducing section, with the interior of the storage space, thereby creating the high-pressure environment inside the storage space and causing the refrigerant to be adsorbed by the adsorbent; and a low-pressure side flow path, through which the refrigerant flows, from the outlet side of the pressure-reducing section to the inlet side of the pressure-boosting section, with the interior of the storage space, thereby creating the low-pressure environment inside the storage space and causing the refrigerant to be desorbed from the adsorbent in a state in which the refrigerant has been adsorbed. (Item 3) The refrigeration cycle device according to item 2, further comprising a refrigerant extraction unit (14) that extracts the refrigerant from the mixed refrigerant, and the mixed refrigerant storage unit stores the refrigerant extracted by the refrigerant extraction unit, by connecting the high-pressure side flow path and the interior of the storage space in the mixed refrigerant storage unit when the circulation of the mixed refrigerant in the cycle is stopped.(Item 5) The refrigeration cycle device according to any one of items 1 to 4, wherein the mixed refrigerant storage unit has the storage space (30b) that stores the adsorbent, and has a temperature adjustment unit (40, 41, 42, 43) that adjusts the temperature inside the storage space, and wherein the mixed refrigerant storage unit lowers the temperature inside the storage space by the temperature adjustment unit when causing the refrigerant to be adsorbed by the adsorbent stored inside the storage space, and raises the temperature inside the storage space by the temperature adjustment unit when desorbing the refrigerant from the adsorbent that has adsorbed the refrigerant. (Item 6) The refrigeration cycle device according to Item 5, comprising: a pressure-boosting section (11, 12, 20) that pressurizes the mixed refrigerant; and a pressure-reducing section (15, 18) that depressurizes the mixed refrigerant pressurized by the pressure-boosting section, wherein the temperature adjustment section, when causing the adsorbent to adsorb the refrigerant that has flowed into the storage space, exchanges heat with the refrigerant flowing through a low-pressure side flow path from an outlet side of the pressure-reducing section to an inlet side of the pressure-boosting section; and, when desorbing the refrigerant from the adsorbent that has adsorbed the refrigerant, exchanges heat with the refrigerant flowing through a high-pressure side flow path from the outlet side of the pressure-boosting section to the inlet side of the pressure-reducing section.(Item 7) A refrigeration cycle device that circulates a mixed refrigerant obtained by mixing an adsorbent that adsorbs and desorbs a refrigerant with the refrigerant, the device comprising: a pressure-increasing section (11, 12, 20) that increases the pressure of the mixed refrigerant; a heat-dissipating section (13, 16) that dissipates heat from the mixed refrigerant pressurized by the pressure-increasing section; and a mixed refrigerant reservoir (30) that stores the adsorbent in a state in which the refrigerant has been adsorbed. The amount of refrigerant circulating in the cycle is adjusted by adjusting the amount of the adsorbent in a state in which the refrigerant has been adsorbed inside the mixed refrigerant reservoir. The mixed refrigerant reservoir has an extraction section (35a, 35b, 35f) that extracts at least a portion of the refrigerant from the mixed refrigerant flowing out from the heat-dissipating section, a refrigerant outlet section (35e) through which the refrigerant extracted in the extraction section flows out, and a mixed refrigerant outlet section (35d) through which the mixed refrigerant from which the refrigerant has been extracted flows out. Item 8. A refrigeration cycle apparatus comprising a flow rate adjusting unit (36, 37) for adjusting the amount of the mixed refrigerant flowing out from the mixed refrigerant outlet, wherein the flow rate adjusting unit adjusts the amount of the adsorbent that has adsorbed the refrigerant stored inside the mixed refrigerant storage unit by adjusting the amount of the mixed refrigerant flowing out from the mixed refrigerant outlet. (Item 8) The refrigeration cycle apparatus according to Item 7, wherein the flow rate adjusting unit increases the amount of the adsorbent that has adsorbed the refrigerant stored inside the mixed refrigerant storage unit by reducing the amount of the mixed refrigerant flowing out from the mixed refrigerant outlet, and decreases the amount of the adsorbent that has adsorbed the refrigerant stored inside the mixed refrigerant storage unit by increasing the amount of the mixed refrigerant flowing out from the mixed refrigerant outlet.

[0249] Although the present disclosure has been described with reference to the embodiments, it is understood that the present disclosure is not limited to the embodiments or structures. The present disclosure also encompasses various modifications and equivalent modifications. In addition, various combinations and forms, including only one element, more than one element, or less than one element, are also within the scope and spirit of the present disclosure.

Claims

1. A refrigeration cycle device that circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent that adsorbs and desorbs the refrigerant, the device having a mixed refrigerant storage section (30) that is connected to allow the refrigerant to flow in and out and that stores the adsorbents in a state where the refrigerant has been adsorbed, the amount of refrigerant circulating through the cycle is adjusted by adjusting the amount of the adsorbents in a state where the refrigerant has been adsorbed inside the mixed refrigerant storage section, the mixed refrigerant storage section has a storage space (30b) that stores the adsorbents, the mixed refrigerant storage section creates a high-pressure environment inside the storage space that is higher than the adsorption pressure of the adsorbents, thereby adsorbing the refrigerant that has flowed in to the adsorbents, and the device desorbs the refrigerant from the adsorbents in a state where the refrigerant has been adsorbed by creating a low-pressure environment inside the storage space that is lower than the desorption pressure of the adsorbents.

2. A refrigeration cycle device as described in claim 1, comprising: a pressure-boosting section (11, 12, 20) that pressurizes the mixed refrigerant; and a pressure-reducing section (15, 18) that depressurizes the mixed refrigerant pressurized by the pressure-boosting section, wherein the mixed refrigerant storage section connects a high-pressure side flow path through which the refrigerant flows from the outlet of the pressure-boosting section to the inlet of the pressure-reducing section with the interior of the storage space, thereby creating the high-pressure environment inside the storage space and allowing the refrigerant to be adsorbed by the adsorbent; and a low-pressure side flow path through which the refrigerant flows from the outlet side of the pressure-reducing section to the inlet side of the pressure-boosting section with the interior of the storage space, thereby creating the low-pressure environment inside the storage space and allowing the refrigerant to be desorbed from the adsorbent in a state in which the refrigerant has been adsorbed.

3. A refrigeration cycle device as described in claim 2, wherein when the circulation of the mixed refrigerant in the cycle is stopped, the mixed refrigerant storage section connects the high-pressure side flow path with the inside of the storage space, thereby creating a high-pressure environment inside the storage space and causing the refrigerant to be adsorbed onto the adsorbent.

4. A refrigeration cycle device according to any one of claims 1 to 3, further comprising a refrigerant extraction section (14) that extracts the refrigerant from the mixed refrigerant, and the mixed refrigerant storage section stores the refrigerant extracted by the refrigerant extraction section.

5. The refrigeration cycle device of claim 1, wherein the mixed refrigerant storage section has the storage space (30b) that stores the adsorbent, and has a temperature adjustment section (40, 41, 42, 43) that adjusts the temperature inside the storage space, and wherein the mixed refrigerant storage section, when causing the refrigerant to be adsorbed by the adsorbent stored inside the storage space, lowers the temperature inside the storage space using the temperature adjustment section, and when desorbing the refrigerant from the adsorbent that has adsorbed the refrigerant, raises the temperature inside the storage space using the temperature adjustment section.

6. A refrigeration cycle device as described in claim 5, comprising a pressure-boosting section (11, 12, 20) that pressurizes the mixed refrigerant, and a pressure-reducing section (15, 18) that depressurizes the mixed refrigerant pressurized by the pressure-boosting section, wherein the temperature adjustment section, when adsorbing the refrigerant that has flowed into the storage space into the adsorbent, exchanges heat with the refrigerant flowing through a low-pressure side flow path from the outlet side of the pressure-reducing section to the inlet side of the pressure-boosting section, and when desorbing the refrigerant from the adsorbent in a state in which the refrigerant has been adsorbed, exchanges heat with the refrigerant flowing through a high-pressure side flow path from the outlet side of the pressure-boosting section to the inlet side of the pressure-reducing section.

7. A refrigeration cycle device that circulates a mixed refrigerant obtained by mixing an adsorbent that adsorbs and desorbs a refrigerant with the refrigerant, the device comprising: a pressure-increasing section (11, 12, 20) that increases the pressure of the mixed refrigerant; a heat-dissipating section (13, 16) that dissipates heat from the mixed refrigerant pressurized by the pressure-increasing section; and a mixed refrigerant storage section (30) that stores the adsorbent in a state in which the refrigerant has been adsorbed. The amount of refrigerant circulating in the cycle is adjusted by adjusting the amount of the adsorbent in a state in which the refrigerant has been adsorbed inside the mixed refrigerant storage section. The mixed refrigerant storage section comprises an extraction section (35a, 35b, 35f) that extracts at least a portion of the refrigerant from the mixed refrigerant that has flowed out from the heat-dissipating section; a refrigerant outlet section (35e) through which the refrigerant extracted in the extraction section flows out; and a mixed refrigerant outlet section (35d) through which the mixed refrigerant from which the refrigerant has been extracted flows out. The refrigeration cycle device includes a flow rate adjusting unit (36, 37) for adjusting the amount of the mixed refrigerant flowing out from the mixed refrigerant outlet, and the amount of the adsorbent that has adsorbed the refrigerant stored inside the mixed refrigerant storage unit is adjusted by adjusting the amount of the mixed refrigerant flowing out from the mixed refrigerant outlet with the flow rate adjusting unit.

8. The refrigeration cycle device of claim 7, wherein the flow rate control unit increases the amount of the adsorbent that has adsorbed the refrigerant stored inside the mixed refrigerant storage unit by reducing the amount of the mixed refrigerant flowing out from the mixed refrigerant outlet, and decreases the amount of the adsorbent that has adsorbed the refrigerant stored inside the mixed refrigerant storage unit by increasing the amount of the mixed refrigerant flowing out from the mixed refrigerant outlet.

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