Refrigeration cycle device

Abstract

Provided is a refrigeration cycle device capable of achieving both stable fluidized-bed formation of an adsorbent inside an adsorber / desorber, and suppression of reduction in operational efficiency due to the fluidized-bed formation of the adsorbent. A refrigeration cycle device for circulating a mixed refrigerant having a refrigerant and an adsorbent mixed therein comprises a compressor (11), an adsorber (13), and a desorber (15). The adsorber (13) has a circulation supply unit that comprises a refrigerant circulation passage (34), a turbo fan (35), and the like. The circulation supply unit circulates and supplies the refrigerant that has flowed out of the adsorber (13) so as to cause the adsorbent inside the adsorber to form into a fluidized bed.

Description

Refrigeration cycle device ,

[0007] ,

[0006] Cross-reference to related applications

[0001] This application is based on Japanese Patent Application No. 2025-6586 filed on January 17, 2025, the contents of which are incorporated herein by reference.

[0002] This disclosure relates to a refrigeration cycle device that circulates a mixed refrigerant in which a refrigerant and an adsorbent are mixed.

[0003] Conventionally, Patent Document 1 discloses a so-called hybrid refrigeration cycle device that circulates a mixed refrigerant in which a refrigerant and a solid particle adsorbent are mixed.

[0004] In a hybrid refrigeration cycle device, the adsorbent becomes an adsorbent and the refrigerant becomes an adsorbate. Therefore, in a hybrid refrigeration cycle device, the adsorption heat when the adsorbent adsorbs the refrigerant and the desorption heat when the adsorbent desorbs the refrigerant can be utilized. Thereby, in a hybrid refrigeration cycle device, it is possible to aim to improve the operating efficiency of the cycle by reducing the refrigerant pressure on the high-pressure side compared to a normal vapor compression refrigeration cycle device in which no adsorbent is mixed with the refrigerant.

[0005] Therefore, in order to sufficiently improve the operating efficiency of the hybrid refrigeration cycle device, it is desirable to sufficiently advance the adsorption / desorption reaction between the refrigerant and the adsorbent in the adsorber / desorber such as an adsorber or a desorber so as to approach an equilibrium state.

[0006] In order to sufficiently advance the adsorption / desorption reaction, it is effective to increase the residence time of the adsorbent flowing into the adsorber / desorber until it flows out of the adsorber / desorber. In other words, it is effective to increase the slip ratio of the adsorbent and the refrigerant in the adsorber / desorber. The slip ratio is the ratio of the flow rate of the adsorbent to the flow rate of the refrigerant in the adsorber / desorber. [[ID=2))

[0007] Furthermore, as a means of increasing the slip ratio, it is known that the solid particulate adsorbent in the adsorption / desorption device is made into a fluidized bed. Here, a fluidized bed is a state in which solid particles are suspended in a fluid by ejecting a fluid into the solid particles. In a fluidized bed, the gravitational force acting on the solid particles and the force that the solid particles receive from the fluid are balanced, causing the entire surrounding solid particles to behave like a uniform fluid. A fluidized bed is sometimes also called a fluidized bed.

[0008] International Publication No. 2024 / 004971

[0009] However, forming a fluidized bed requires injecting a large amount of fluid into solid particles. Therefore, in the hybrid refrigeration cycle system described in Patent Document 1, if the adsorbent inside the adsorbent or desorbent is injected with refrigerant to create a fluidized bed, the power consumption of the compressor will increase. As a result, the improvement in operating efficiency achieved by configuring the hybrid refrigeration cycle system may not be fully realized.

[0010] In view of the above, this disclosure aims to provide a refrigeration cycle device that enables both the stable formation of a fluidized bed of the adsorbent inside at least one of the adsorbent and the desorbent, and the suppression of a decrease in operating efficiency caused by the fluidization of the adsorbent.

[0011] To achieve the above objective, a refrigeration cycle device according to one aspect of the present disclosure circulates a mixed refrigerant obtained by mixing a refrigerant and an adsorbent. Furthermore, it comprises a compression unit, an adsorption unit, and a desorption unit.

[0012] The compression unit compresses and discharges the refrigerant. The adsorption unit adsorbs the refrigerant discharged from the compression unit onto an adsorbent. The desorption unit desorbs the refrigerant that is drawn from the adsorbent into the compression unit.

[0013] At least one of the adsorption section and the desorption section has a circulation supply section for circulating and supplying refrigerant. That is, it has at least one of a circulation supply section for the adsorption section that circulates and supplies the refrigerant that has flowed out of the adsorption section back to the adsorption section, and a circulation supply section for the desorption section that circulates and supplies the refrigerant that has flowed out of the desorption section back to the desorption section.

[0014] The circulation supply unit circulates and supplies refrigerant in such a way that the adsorbent inside the adsorption or desorption unit becomes a fluidized bed.

[0015] According to this, because it has a circulation supply unit, the adsorbent inside the adsorption or desorption unit can be stably converted into a fluidized bed. Furthermore, the power consumed by the circulation supply unit to circulate and supply refrigerant to the adsorption or desorption unit is less than the power consumed by the compression unit to pressurize an equivalent amount of refrigerant to the adsorption or desorption unit.

[0016] As a result, stable fluidization of the adsorbent inside at least one of the adsorption and desorption sections can be achieved. Furthermore, the decrease in operating efficiency caused by the fluidization of the adsorbent can be suppressed.

[0017] The above-mentioned and other purposes, features and advantages of this disclosure will become clearer from the following detailed description with reference to the accompanying drawings. A schematic overall diagram of the refrigeration cycle apparatus of the first embodiment. A schematic partial cross-sectional view of the adsorber of the first embodiment. A schematic overall diagram of the refrigeration cycle apparatus of the second embodiment. A schematic overall diagram of the refrigeration cycle apparatus of the third embodiment. An axial cross-sectional view of the ejector of the third embodiment. A schematic overall diagram of the refrigeration cycle apparatus of the fourth embodiment. A schematic partial cross-sectional view of the adsorber of the fourth embodiment. A schematic partial cross-sectional view of the adsorber of the fifth embodiment. A schematic partial cross-sectional view of the adsorber of the sixth embodiment. A schematic overall diagram of the refrigeration cycle apparatus of the seventh embodiment. A schematic overall diagram of the refrigeration cycle apparatus of the eighth embodiment. A schematic overall diagram of the refrigeration cycle apparatus of the ninth embodiment. A schematic partial cross-sectional view of the desorber of the ninth embodiment.

[0018] Several embodiments for implementing this disclosure are described below with reference to the drawings. In each embodiment, parts corresponding to matters described in a prior embodiment are denoted by the same reference numerals, and redundant descriptions may be omitted. If only a part of the configuration is described in each embodiment, other parts of the configuration can be applied to other embodiments described in advance. Not only are combinations of parts that are explicitly shown to be combinable in each embodiment possible, but embodiments can also be partially combined even if not explicitly shown, as long as there are no particular problems with the combination.

[0019] (First Embodiment) A first embodiment of the refrigeration cycle device according to the present disclosure will be described with reference to Figures 1 and 2. In this embodiment, the refrigeration cycle device 10 shown in the overall configuration diagram of Figure 1 is applied to the air conditioning device 1. The air conditioning device 1 includes the refrigeration cycle device 10, a high-temperature side heat transfer medium circuit 20, a control device 40, etc.

[0020] The refrigeration cycle device 10 cools the air supplied to the room, which is the space to be air-conditioned, by the air conditioning system 1. The refrigeration cycle device 10 is a hybrid type refrigeration cycle device that circulates a mixed refrigerant, which is a mixture of a refrigerant and an adsorbent. The refrigeration cycle device 10 uses carbon dioxide (i.e., R744) as the refrigerant.

[0021] Adsorbents adsorb refrigerants under high pressure and desorb them (in other words, detach them) under low pressure. Furthermore, when adsorbing refrigerants, the adsorbent releases heat (i.e., internal energy) from the adsorbed refrigerant as heat of adsorption, and when desorbing refrigerants, it absorbs heat from the surroundings as heat of desorption.

[0022] In the refrigeration cycle device 10, a metal-organic frame (MOF) is used as the adsorbent. MOF is a porous material obtained by reacting metal ions with organic ligands. MOF is a polymeric structure that has countless openings inside due to the linkage of metal ions and organic ligands.

[0023] MOFs allow for optimization of the aperture diameter through the combination of metal ions and organic ligands. By adjusting the aperture diameter, MOFs can selectively adsorb refrigerants. In this embodiment, an MOF suitable for adsorbing carbon dioxide, which is a refrigerant, is used. Specifically, MOF-5 or MOF-200 may be used.

[0024] The adsorbent does not dissolve in the refrigerant, but is mixed with it in the form of a solid powder or solid particles. Therefore, in this embodiment, the MOF, which is the adsorbent, acts as the adsorbent, and the carbon dioxide, which is the refrigerant, acts as the adsorbate. Furthermore, the amount of refrigerant sealed in the refrigeration cycle device 10 is greater than the maximum adsorption capacity of the adsorbent. Therefore, in the refrigeration cycle device 10, only the adsorbent does not circulate within the cycle.

[0025] In the following explanation, for clarity, a refrigerant mixed with an adsorbent will be referred to as a "mixed refrigerant." The adsorbents in a mixed refrigerant include both adsorbents that adsorb the refrigerant and adsorbents that do not. Furthermore, refrigerants without adsorbents will be referred to as refrigerant, discharged refrigerant, circulating refrigerant, etc., rather than using the term "mixed."

[0026] The compressor 11 is a compression unit that draws in the refrigerant flowing out from the gas phase refrigerant outlet 16b of the low-pressure separator 16 (described later), compresses it, and discharges it. The compressor 11 is an electric compressor that rotates a fixed-capacity compression mechanism with a fixed discharge capacity using an electric motor. As the compression mechanism, a rotary type compression mechanism, a scroll type compression mechanism, etc., can be used. The rotational speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the control device 40.

[0027] The adsorbent pump 12 is an adsorbent transport unit that transports the mixed refrigerant that has flowed out from the mixed refrigerant outlet 16c of the low-pressure separator 16. The adsorbent pump 12 can be a rotary positive displacement single-screw eccentric pump, a rotary pump, a diaphragm pump, or other powder pump. The rotational speed (i.e., adsorbent pumping capacity) of the adsorbent pump 12 is controlled by a control signal output from the control device 40.

[0028] The refrigerant inlet 13a side of the adsorbent 13 is connected to the discharge port of the compressor 11. The adsorbent inlet 13b side of the adsorbent 13 is connected to the discharge port of the adsorbent pump 12. The adsorbent 13 is an adsorption unit that adsorbs refrigerant onto an adsorbent. The adsorbent 13 is a heat exchange unit for heat dissipation that exchanges heat between the mixed refrigerant and the heat transfer medium circulating in the heat transfer circuit 20, thereby releasing the heat of adsorption to the heat transfer medium. The detailed configuration of the adsorbent 13 will be described later.

[0029] The inlet side of the expansion valve 14 is connected to the adsorbent outlet 13d of the adsorbent 13. The expansion valve 14 is a mixed refrigerant pressure reduction unit that reduces the pressure of the mixed refrigerant flowing out of the adsorbent 13. More specifically, the expansion valve 14 reduces the pressure of the refrigerant contained in the mixed refrigerant, thereby lowering the pressure of the atmospheric refrigerant on the adsorbent. Furthermore, the expansion valve 14 is a mixed refrigerant flow rate adjustment unit that adjusts the flow rate of the mixed refrigerant flowing into the desorber 15.

[0030] The expansion valve 14 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. The operation of the expansion valve 14 is controlled by a control signal output from the control device 40.

[0031] The outlet of the expansion valve 14 is connected to the mixed refrigerant inlet side of the desorber 15. The desorber 15 is a desorbing unit that desorbs refrigerant from the adsorbent that has flowed into its interior. The desorber 15 is a heat exchange unit that absorbs heat from the blown air by exchanging heat between the mixed refrigerant and the blown air blown into the room from a blower (not shown), thereby absorbing the heat of desorption from the blown air. As the desorber 15, a heat exchanger or the like can be used, in which an air passage for the blown air is formed around the refrigerant piping through which the mixed refrigerant flows.

[0032] The mixed refrigerant outlet of the desorber 15 is connected to the mixed refrigerant inlet 16a side of the low-pressure separator 16. The low-pressure separator 16 is a low-pressure extraction unit that extracts a portion of the mixed refrigerant that does not contain adsorbents from the mixed refrigerant flowing out of the desorber 15 and discharges it to the suction side of the compressor 11.

[0033] Here, the mixed refrigerant separated by the low-pressure separator 16 is affected by the pressure of the mixed refrigerant, the ambient temperature at the location where the low-pressure separator 16 is installed, the type of refrigerant, the amount of refrigerant charged, etc. The mixed refrigerant separated by the low-pressure separator 16 can be a mixed refrigerant obtained by mixing the adsorbent with a gaseous refrigerant, a mixed refrigerant obtained by mixing the adsorbent with a gaseous two-phase refrigerant, or a mixed refrigerant obtained by mixing the adsorbent with a liquid refrigerant.

[0034] The low-pressure separator 16 is formed by a metal, bottomed cylindrical container that forms a space inside. The low-pressure separator 16 is positioned so that its central axis is vertical. A flat adsorbent filter 16f is placed inside the internal space of the low-pressure separator 16.

[0035] The adsorbent filter 16f divides the internal space of the low-pressure separator 16 into an upper space 16d and a lower space 16e in the vertical direction. The adsorbent filter 16f is an adsorbent filtration section that has selective permeability that allows gaseous refrigerant to pass through but at least prevents the adsorbent from passing through. Therefore, the adsorbent filter 16f can employ a wire mesh filter or the like with a mesh opening smaller than the representative diameter of the adsorbent.

[0036] The lower space 16e is connected to the mixed refrigerant inlet 16a and the mixed refrigerant outlet 16c of the low-pressure side separator 16. In the lower space 16e, the refrigerant is extracted from the mixed refrigerant due to the difference in specific gravity between the refrigerant and the adsorbent.

[0037] Furthermore, if the remaining mixed refrigerant is a mixed refrigerant in which an adsorbent is mixed with the liquid phase refrigerant, the volume of the lower space 16e is set so that the lower space 16e becomes a storage section for storing the excess refrigerant of the cycle as saturated liquid phase refrigerant. As a result, in the low-pressure side separator 16, only the gaseous phase refrigerant is extracted into the upper space 16d.

[0038] The mixed refrigerant outlet 16c is an outlet for discharging the mixed refrigerant stored in the lower space 16e, that is, the remaining mixed refrigerant after the gas phase refrigerant has been extracted. The mixed refrigerant outlet 16c is formed on the bottom side of the low-pressure separator 16. The suction port side of the adsorbent pump 12 is connected to the mixed refrigerant outlet 16c. The lower space 16e may be formed in a frustoconical shape that tapers downwards.

[0039] In this configuration, it is preferable that the low-pressure separator 16 is positioned above the adsorbent pump 12. This allows the refrigerant mixture separated by the low-pressure separator 16 to be moved towards the suction port of the adsorbent pump 12 by utilizing gravity.

[0040] The gas phase refrigerant outlet 16b of the low-pressure separator 16 is connected to the upper space 16d. The gas phase refrigerant outlet 16b is an outlet that discharges the low-pressure gas phase refrigerant that has passed through the adsorbent filter 16f. The gas phase refrigerant outlet 16b is formed on the upper surface side of the low-pressure separator 16. The suction port side of the compressor 11 is connected to the gas phase refrigerant outlet 16b.

[0041] Next, the detailed configuration of the adsorber 13 of this embodiment will be described using Figure 2. The adsorber 13 includes a main body 31, a dispersion plate 32, a powder nozzle 33, a refrigerant circulation passage 34, a turbo fan 35, and the like.

[0042] The main body 31 is a metal container with a bottom, either a rectangular prism or a cylindrical shape, that forms a space inside. The main body 31 is positioned so that its central axis is vertical. A flat metal dispersion plate 32 is placed inside the main body 31. The dispersion plate 32 divides the internal space of the main body 31 into a fluidized bed space 31a and a duct space 31b in the vertical direction. Therefore, the dispersion plate 32 forms the bottom surface of the fluidized bed space 31a.

[0043] The dispersion plate 32 has multiple ejection holes 32a that penetrate through both its front and back surfaces. The ejection holes 32a are through-holes for ejecting gaseous refrigerant from the duct space 31b side to the fluidized bed space 31a side. The diameter of the ejection holes 32a is set to be smaller than the representative diameter of the adsorbent. This prevents the adsorbent from flowing from the fluidized bed space 31a side to the duct space 31b side through the ejection holes 32a.

[0044] In the fluidized bed space 31a, the adsorbent inlet 13b, the refrigerant outlet 13c, and the adsorbent outlet 13d of the adsorber 13 communicate with each other. The adsorbent inlet 13b is an adsorbent inlet section that allows the adsorbent transported by the adsorbent pump 12 to flow into the fluidized bed space 31a. The adsorbent inlet 13b is disposed on the upper side of the fluidized bed space 31a. In other words, the adsorbent inlet 13b is disposed closer to the upper surface than the bottom surface of the main body 31.

[0045] As will be described later, the fluidized bed space 31a is a space for fluidizing the adsorbent. Therefore, the adsorbent inlet 13b is disposed on the upper side of the adsorbent fluidized in the fluidized bed space 31a. Further, the adsorbent transported by the adsorbent pump 12 is guided to the upper side of the adsorbent fluidized inside the fluidized bed space 31a.

[0046] A powder nozzle 33 is disposed on the upper side of the fluidized bed space 31a. The powder nozzle 33 is a nozzle for injecting the adsorbent that has flowed in through the adsorbent inlet 13b into the fluidized bed space 31a. The adsorbent inlet 13b is connected to the inlet section of the powder nozzle 33. The powder nozzle 33 is disposed at approximately the same height as the adsorbent inlet 13b.

[0047] More specifically, the powder nozzle 33 of the present embodiment is formed by providing a plurality of injection holes at equal intervals in a plurality of adsorbent pipes extending in the horizontal direction. Thereby, the powder nozzle 33 can uniformly inject the adsorbent pumped from the adsorbent pump 12 into the fluidized bed space 31a. Further, the adsorbent injected from the powder nozzle 33 moves in the fluidized bed space 31a from the upper side to the lower side.

[0048] The adsorbent outlet 13d is an adsorbent outlet section that allows the adsorbent that has adsorbed the refrigerant in the fluidized bed space 31a to flow out. The adsorbent outlet 13d is disposed on the lower side of the adsorbent inlet 13b of the fluidized bed space 31a. In other words, the adsorbent outlet 13d is disposed closer to the bottom surface than the upper surface of the main body 31.

[0049] In the fluidized bed space 31a, the adsorbent, which has increased in mass by adsorbing the refrigerant, tends to fall downwards. Therefore, by positioning the adsorbent outlet 13d at the lower side of the fluidized bed space 31a, the adsorbent containing the refrigerant can be easily discharged. Preferably, the adsorbent outlet 13d should be positioned at the lowest part of the fluidized bed space 31a.

[0050] The refrigerant outlet 13c is a refrigerant outlet that allows refrigerant to flow out of the fluidized bed space 31a. The refrigerant outlet 13c is formed on the upper surface of the main body 31. The inlet of the refrigerant circulation passage 34 is connected to the refrigerant outlet 13c. The refrigerant circulation passage 34 is a refrigerant passage that circulates and supplies the refrigerant that has flowed out of the refrigerant outlet 13c back into the main body 31.

[0051] A circulation-side adsorbent filter 34a is positioned in the refrigerant circulation passage 34. The circulation-side adsorbent filter 34a is an adsorbent intrusion suppression unit that prevents adsorbents from entering the refrigerant circulation passage 34. The basic configuration of the circulation-side adsorbent filter 34a is the same as that of the adsorbent filter 16f positioned in the low-pressure separator 16.

[0052] The outlet of the refrigerant circulation passage 34 is connected to the intake port of the turbo fan 35. The turbo fan 35 is a circulating air blower that draws in the refrigerant flowing out from the refrigerant outlet 13c and through the refrigerant circulation passage 34, and pressurizes and sends it to the duct space 31b side of the main body 31. As the circulating air blower, a blower capable of increasing the static pressure of the refrigerant, such as a turbo fan or a sirocco fan, can be used. The rotation speed (i.e., the blowing capacity) of the turbo fan 35 is controlled by a control signal output from the control device 40.

[0053] The duct space 31b side of the main body 31 is connected to the discharge port of the turbo fan 35. The duct space 31b is shaped to increase the cross-sectional area of ​​the passage toward the downstream side (i.e., upward side) in the direction of refrigerant flow, so that the refrigerant can be distributed to the entire area of ​​the dispersion plate 32.

[0054] Therefore, the adsorbent 13 of this embodiment has a circulation supply unit for the adsorption section that circulates and supplies the refrigerant that has flowed out of the adsorbent 13 back to the adsorbent 13. The circulation supply unit for the adsorption section of this embodiment is composed of a refrigerant circulation passage 34, a circulation-side adsorbent filter 34a, a turbo fan 35, and the like.

[0055] Furthermore, the refrigerant inlet 13a of the adsorbent 13 is connected to the duct space 31b. The refrigerant inlet 13a is the part that allows the refrigerant discharged from the compressor 11 to flow into the fluidized bed space 31a. As a result, the refrigerant discharged from the compressor 11 is guided below the adsorbent which is in a fluidized bed state inside the fluidized bed space 31a.

[0056] Furthermore, multiple heat transfer tubes 22 are arranged within the fluidized bed space 31a. The heat transfer tubes 22 are heat exchange passages that exchange heat between the heat transfer medium circulating in the high-temperature side heat transfer medium circuit 20 and the mixed refrigerant flowing within the fluidized bed space 31a. The heat transfer tubes 22 are heat transfer medium passages that release the heat of adsorption released by the adsorbent to the high-temperature side heat transfer medium.

[0057] The diameter, number, and arrangement of the multiple heat transfer tubes 22 are determined so as not to obstruct the flow of refrigerant and adsorbent in the fluidized bed space 31a. Heat exchange promoting fins to facilitate heat exchange between the heat transfer medium and the mixed refrigerant, guide fins to direct the flow direction of the refrigerant and adsorbent in the fluidized bed space 31a from downward to upward, may be formed on the outer circumference of the heat transfer tubes 22.

[0058] Next, the high-temperature side heat transfer medium circuit 20 shown in Figure 1 will be described. The high-temperature side heat transfer medium circuit 20 is a circuit that circulates the high-temperature side heat transfer medium. In this embodiment, an aqueous solution of ethylene glycol is used as the high-temperature side heat transfer medium. The high-temperature side heat transfer medium circuit 20 is equipped with a high-temperature side heat transfer medium pump 21, a plurality of heat transfer tubes 22, a radiator 23, and the like.

[0059] The high-temperature side heat transfer fluid pump 21 is a high-temperature side heat transfer fluid pumping unit that sucks in the high-temperature side heat transfer fluid that has flowed out of the radiator 23 and pumps it to the inlet side of the multiple heat transfer tubes 22. The high-temperature side heat transfer fluid pump 21 is an electric water pump whose rotational speed (i.e., water pumping capacity) is controlled by a control voltage output from the control device 40.

[0060] The discharge port of the high-temperature side heat transfer fluid pump 21 is connected to the inlet side of a plurality of heat transfer tubes 22 via a distribution unit. The outlets of the plurality of heat transfer tubes 22 are connected to the inlet side of the heat transfer fluid of a radiator 23 via a manifold. The radiator 23 is a heat exchanger for heat dissipation that exchanges heat between the high-temperature side heat transfer fluid flowing out of the heat transfer tubes 22 and outside air blown in from an outside air fan (not shown). The outlet of the heat transfer fluid of the radiator 23 is connected to the suction port side of the high-temperature side heat transfer fluid pump 21.

[0061] Therefore, in the high-temperature heat transfer medium circuit 20, when the high-temperature heat transfer medium pump 21 is activated, the high-temperature heat transfer medium pumped from the high-temperature heat transfer medium pump 21 circulates in the following order: multiple heat transfer tubes 22, radiator 23, and the suction port side of the high-temperature heat transfer medium pump 21.

[0062] Next, the electrical control unit of the air conditioning unit 1 will be described. The control unit 40 has a well-known microcomputer including a CPU, ROM, and RAM, and peripheral circuits. The control unit 40 performs various calculations and processes based on the control program stored in the ROM. Then, based on the calculation and processing results, the control unit 40 controls the operation of various controlled devices connected to the output side.

[0063] Various control sensors are connected to the input side of the control device 40. The control sensors include an internal temperature sensor, an external temperature sensor, a high-pressure sensor, a high-pressure temperature sensor, an evaporator pressure sensor, an evaporator temperature sensor, an adsorbent level sensor 41a, an inlet pressure sensor 41b, an outlet pressure sensor 41c, and the like (not shown).

[0064] The indoor temperature sensor is an indoor temperature detection unit that detects the indoor air temperature (i.e., indoor temperature) Tr. The outdoor temperature sensor is an outdoor temperature detection unit that detects the outdoor air temperature (i.e., outdoor temperature) Tam.

[0065] The high-pressure sensor is a high-pressure detection unit that detects the high-pressure pressure Pd, which is the pressure of the mixed refrigerant discharged from the adsorber 13. The high-pressure temperature sensor is a high-pressure temperature detection unit that detects the high-pressure temperature Td, which is the temperature of the mixed refrigerant discharged from the adsorber 13.

[0066] 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 decoupling unit 15. 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 decoupling unit 15.

[0067] The adsorbent level sensor 41a detects the fluidized bed height Hf, which is the height of the adsorbent that has become a fluidized bed in the fluidized bed space 31a of the adsorber 13.

[0068] The inlet pressure sensor 41b detects the inlet pressure Pfin, which is the pressure of the refrigerant in the duct space 31b. Therefore, the inlet pressure sensor 41b is an inlet pressure detection unit that detects the inlet pressure Pfin of the refrigerant supplied to the adsorbent which is in a fluidized bed in the fluidized bed space 31a.

[0069] The outlet pressure sensor 41c detects the outlet pressure Pfout, which is the pressure of the refrigerant flowing from the duct space 31b into the refrigerant circulation passage 34. Therefore, the outlet pressure sensor 41c is an outlet pressure detection unit that detects the outlet pressure Pfout of the refrigerant that has flowed out from the adsorbent that has become a fluidized bed in the fluidized bed space 31a.

[0070] Furthermore, an operation panel (not shown) is connected to the input side of the control device 40 by wire or wireless connection. The control device 40 receives operation signals from various operation switches provided on the operation panel. The various operation switches provided on the operation panel include an operation switch, a temperature setting switch, an airflow setting switch, and so on.

[0071] The activation switch is a cooling operation request unit that requests the detachable device 15 to cool the blown air. The temperature setting switch is a temperature setting unit that sets the set temperature Tset of the space to be air-conditioned. The airflow setting switch is an airflow setting unit that sets the airflow rate of the blown air that is blown into the space to be air-conditioned.

[0072] The control device 40 is configured as an integrated unit that controls various controlled devices connected to the output side. Therefore, the configuration (hardware and software) that controls the operation of each controlled device constitutes a control unit that independently controls the operation of each controlled device.

[0073] For example, the configuration of the control device 40 that controls the refrigerant discharge capacity of the compressor 11 constitutes a discharge capacity control unit. For example, the configuration of the control device 40 that controls the blowing capacity of the turbo fan 35 constitutes a blowing capacity control unit.

[0074] Next, the operation of the air conditioning unit 1 in the above configuration will be described. When the operating switch of the air conditioning unit 1 is turned on, the control device 40 executes a control program. The control program reads the detection signals from the control sensor group described above and the operation signals from the operation panel.

[0075] Then, based on the read detection signals and operation signals, the operation of various controlled devices is controlled. Subsequently, until the termination condition of the control program is met, the control routine of reading the detection signals and operation signals, and controlling various controlled devices based on the detection signals and operation signals is repeated at predetermined control cycles.

[0076] More specifically, in this embodiment, the control program controls the rotational speed of the compressor 11 so that the evaporator temperature Te detected by the evaporator temperature sensor approaches the target evaporator temperature TEO. The target evaporator temperature TEO is calculated based on the internal temperature Tr detected by the internal temperature sensor, the external temperature Tam detected by the external temperature sensor, the set temperature Tset set by the temperature setting switch, etc.

[0077] Furthermore, the control program controls the rotation speed of the adsorption pump 12 by referring to a control map pre-stored in the control device 40 based on the rotation speed of the compressor 11.

[0078] Furthermore, the control program controls the throttle opening of the expansion valve 14 so that the high-pressure Pd detected by the high-pressure sensor approaches the target high-pressure PDO. The target high-pressure PDO is determined based on the high-pressure temperature Td detected by the high-pressure temperature sensor so that the cycle's operating efficiency approaches its maximum value.

[0079] Furthermore, the control program determines the rotational speed of the turbofan 35 so that the pressure loss ΔPf approaches the target pressure loss ΔPFO. The pressure loss ΔPf is the pressure difference obtained by subtracting the outlet pressure Pfout detected by the outlet pressure sensor 41c from the inlet pressure Pfin detected by the inlet pressure sensor 41b. The target pressure loss ΔPFO is calculated based on the fluidized bed height Hf detected by the adsorbent level sensor 41a.

[0080] More specifically, the target pressure loss ΔPFO is calculated based on the following equations F1 and F2: ΔPFO = Mf × g / Af + Cf …(F1) Mf = Hf × Af × ρf …(F2) Here, Mf is the mass of the adsorbent that is in a fluidized bed in the fluidized bed space 31a. g is the acceleration due to gravity. Af is the axial perpendicular cross-sectional area Af of the fluidized bed space 31a. Cf is an experimentally obtained correction term. ρf is the density of the adsorbent.

[0081] As is clear from the above formula F2, the control device 40 calculates the mass of the adsorbent in the fluidized bed by integrating the fluidized bed height Hf, the axially perpendicular cross-sectional area Af of the fluidized bed space 31a, and the density ρf of the adsorbent. Therefore, the adsorbent level sensor 41a constitutes a mass detection unit that detects the adsorbent mass Mf. Furthermore, the control device 40 determines the target pressure loss ΔPFO such that the pressure loss ΔPf increases as the adsorbent mass Mf increases.

[0082] Therefore, in the refrigeration cycle device 10, the compressor 11 draws in the low-pressure gaseous refrigerant that flows out from the gaseous refrigerant outlet 16b of the low-pressure separator 16, compresses it, and discharges it. The discharged refrigerant from the compressor 11 flows into the duct space 31b from the refrigerant inlet 13a of the adsorber 13.

[0083] Furthermore, the adsorbent pump 12 transports the mixed refrigerant that has flowed out of the mixed refrigerant outlet 16c of the low-pressure separator 16. The mixed refrigerant transported by the adsorbent pump 12 flows into the fluidized bed space 31a from the adsorbent inlet 13b of the adsorbent 13. The mixed refrigerant that has flowed into the fluidized bed space 31a is ejected from the powder nozzle 33. The adsorbent ejected from the powder nozzle 33 moves from the top to the bottom within the fluidized bed space 31a due to the action of gravity.

[0084] The discharged refrigerant flowing into the duct space 31b merges with the circulating refrigerant pumped from the turbo fan 35 and is ejected into the fluidized bed space 31a from the ejection holes 32a of the dispersion plate 32. The refrigerant ejected into the fluidized bed space 31a exerts an upward drag force on the adsorbents. Then, the gravitational force acting on the adsorbents in the fluidized bed space 31a balances out, causing the adsorbents in the fluidized bed space 31a to suspend and become a fluidized bed. The fluidized adsorbents behave as a uniform fluid together with the surrounding adsorbents.

[0085] When the fluidized bed adsorbent adsorbs the refrigerant, it releases heat of adsorption to the high-temperature heat transfer medium flowing through the heat transfer tube 22. Furthermore, in the fluidized bed space 31a, due to the weight increase and classification phenomenon that accompanies the adsorption reaction, the adsorbent with the largest adsorption capacity moves downward. The adsorbent that has moved downward flows out of the adsorbent outlet 13d of the adsorbent unit 13 along with a small amount of refrigerant.

[0086] Meanwhile, any remaining refrigerant that was not adsorbed by the adsorbent moves to the upper side of the fluidized bed space 31a and flows out from the refrigerant outlet 13c of the adsorbent 13. The refrigerant that flows out from the refrigerant outlet 13c of the adsorbent 13 flows into the refrigerant circulation passage 34. Since a circulation-side adsorbent filter 34a is located in the refrigerant circulation passage 34, the adsorbent does not flow into the refrigerant circulation passage 34 together with the refrigerant.

[0087] The refrigerant flowing into the refrigerant circulation passage 34 is drawn into the turbo fan 35. The circulating refrigerant, pressurized by the turbo fan 35, is then pumped into the duct space 31b. The refrigerant pumped into the duct space 31b merges with the discharged refrigerant discharged from the compressor 11 and is then ejected into the fluidized bed space 31a from the ejection holes 32a of the dispersion plate 32.

[0088] The mixed refrigerant flowing out from the adsorbent outlet 13d of the adsorbent 13 flows into the expansion valve 14 and is depressurized. The depressurized mixed refrigerant in the expansion valve 14 flows into the desorber 15. As the pressure drops in the mixed refrigerant flowing into the desorber 15, the refrigerant is desorbed from the adsorbent. At this time, the adsorbent absorbs heat from the blown air as heat of desorption. Furthermore, if the mixed refrigerant contains a liquid phase refrigerant, the liquid phase refrigerant evaporates and exerts an endothermic effect, thereby cooling the blown air.

[0089] The mixed refrigerant that flows out from the decoupler 15 flows into the lower space 16e of the low-pressure separator 16. A portion of the refrigerant contained in the mixed refrigerant that flows into the lower space 16e flows into the upper space 16d via the adsorbent filter 16f. The low-pressure gaseous refrigerant that flows out from the upper space 16d is drawn into the compressor 11 and compressed again. The mixed refrigerant that flows out from the lower space 16e is drawn into the adsorbent pump 12 and transported again.

[0090] In the high-temperature heat transfer medium circuit 20, the high-temperature heat transfer medium, pumped from the high-temperature heat transfer medium pump 21, flows into the heat transfer tubes 22. The high-temperature heat transfer medium that flows into the heat transfer tubes 22 is heated by absorbing heat of adsorption. The high-temperature heat transfer medium heated in the heat transfer tubes 22 flows into the radiator 23 and dissipates heat into the outside air. This cools the high-temperature heat transfer medium. The high-temperature heat transfer medium cooled in the radiator 23 is drawn into the high-temperature heat transfer medium pump 21 and pumped back into the heat transfer tubes 22.

[0091] As described above, the air conditioning system 1 of this embodiment can cool the room by blowing the cooled air from the detachable device 15 into the room.

[0092] Furthermore, the refrigeration cycle device 10 of this embodiment constitutes a hybrid type refrigeration cycle device. Therefore, in the adsorbent 13 and the high-temperature side heat transfer medium circuit 20, the heat of adsorption from the adsorbent can be released to the outside air via the high-temperature side heat transfer medium. In addition, in the desorption device 15, the heat of desorption that occurs when the adsorbent desorbs the refrigerant can be absorbed from the blown air.

[0093] Therefore, according to the refrigeration cycle device 10 of this embodiment, it is possible to lower the pressure of the discharged refrigerant discharged from the compressor 11 and improve the operating efficiency of the cycle compared to a conventional vapor compression type refrigeration cycle device in which an adsorbent is not mixed with the refrigerant. For this reason, in order to sufficiently improve the operating efficiency of the refrigeration cycle device 10, it is desirable to allow the adsorption reaction between the refrigerant and the adsorbent in the adsorber 13 to proceed sufficiently so as to approach an equilibrium state.

[0094] In contrast, the adsorbent 13 of this embodiment is equipped with a circulation supply unit for the adsorption section. With this, by injecting refrigerant into the fluidized bed space 31a, the adsorbent in the fluidized bed space 31a can be stably converted into a fluidized bed.

[0095] Furthermore, by creating a fluidized bed within the fluidized bed space 31a, the relative velocity between the adsorbent and the refrigerant can be increased, thereby increasing the slip ratio, which is the ratio of the adsorbent's flow velocity to the refrigerant's flow velocity. In other words, the residence time of the adsorbent from the adsorbent 13 until it flows out of the adsorbent 13 can be increased. In addition, the contact area between the adsorbent and the refrigerant can be increased.

[0096] Therefore, according to the refrigeration cycle device 10 of this embodiment, by making the adsorbent in the fluidized bed space 31a a fluidized bed, the adsorption reaction between the refrigerant and the adsorbent can be sufficiently advanced to approach an equilibrium state.

[0097] Furthermore, the circulation supply unit pressurizes the refrigerant that has leaked out of the adsorber 13 and circulates it back to the adsorber 13. Therefore, the amount of pressure increase that the circulation supply unit pressurizes the refrigerant is less than the amount of pressure increase that the compressor 11 pressurizes an equivalent amount of low-pressure refrigerant. In other words, the power consumed by the circulation supply unit to circulate and supply refrigerant to the adsorber 13 is less than the power consumed by the compressor 11 to pressurize an equivalent flow rate of low-pressure refrigerant to the adsorber 13.

[0098] As a result, the refrigeration cycle device 10 of this embodiment can achieve stable fluidization of the adsorbent in the adsorbent 13. Furthermore, it can suppress the decrease in the operating efficiency of the cycle caused by the fluidization of the adsorbent.

[0099] Furthermore, the circulation supply unit for the adsorption unit in this embodiment has a turbo fan 35 which is a circulation blower unit. With this configuration, the static pressure of the refrigerant flowing out of the adsorber 13 can be increased and circulated back to the adsorber 13 with a relatively simple setup.

[0100] In this case, the control device 40 can independently control the refrigerant discharge capacity of the compressor 11 and the blowing capacity of the turbo fan 35. Therefore, the control device 40 can control the refrigerant discharge capacity of the compressor 11 in accordance with load fluctuations to ensure the refrigerant flow rate necessary for the adsorption reaction, and control the blowing capacity of the turbo fan 35 to ensure that the adsorbent inside the adsorbent 13 becomes a fluidized bed.

[0101] Furthermore, in the control device 40 of this embodiment, the target pressure loss ΔPFO is determined so as the mass Mf of the adsorbent increases, the pressure loss ΔPf increases. This makes it possible to control the airflow capacity of the turbo fan 35 to ensure that the adsorbent inside the adsorbent 13 becomes a fluidized bed, even more reliably.

[0102] In addition, in this embodiment, the refrigerant discharged from the compressor 11 is guided below the fluidized bed of the adsorbent. Therefore, in the adsorbent 13 of this embodiment, the fluidized bed of the adsorbent inside the adsorbent 13 is achieved not only by the airflow capacity of the turbo fan 35 but also by the refrigerant discharge capacity of the compressor 11. As a result, the decrease in the operating efficiency of the cycle can be suppressed even further.

[0103] Furthermore, the circulation supply unit for the adsorption unit in this embodiment has a circulation-side adsorbent filter 34a. This further suppresses the decrease in the operating efficiency of the cycle and protects the turbo fan 35.

[0104] More specifically, if the adsorbent moves into the duct space 31b, it will be blocked by the dispersion plate 32 and will not be able to move back into the fluidized bed space 31a. As a result, the amount of adsorbent that can adsorb the refrigerant in the fluidized bed space 31a will decrease, and there is a possibility that sufficient heat of adsorption will not be dissipated.

[0105] In contrast, the circulation supply unit for the adsorption unit in this embodiment has a circulation-side adsorbent filter 34a, which prevents the adsorbent from moving into the duct space 31b via the refrigerant circulation passage 34. Therefore, a decrease in operating efficiency can be suppressed. Furthermore, since it is possible to prevent the turbo fan 35 from sucking in solid particulate adsorbent, wear and foreign matter jamming of the turbo fan 35 can be suppressed, thereby protecting the turbo fan 35.

[0106] Here, an example has been described in which a refrigeration cycle device 10 circulates a mixed refrigerant of refrigerant and adsorbent, but it is not limited to this. Furthermore, a non-adsorbent medium that is not adsorbed by the adsorbent may be mixed with the refrigerant. The circulation supply unit for the adsorption unit may also be configured to circulate and supply the refrigerant and non-adsorbent medium that have flowed out of the adsorbent 13 back to the adsorbent 13.

[0107] According to this, since the non-adsorbent medium is not adsorbed onto the adsorbent, the flow rate of the non-adsorbent medium circulated and supplied by the circulation supply unit becomes less prone to fluctuations. Therefore, the adsorbent in the adsorbent 13 can be made into a fluidized bed more stably. As the non-adsorbent medium, a fluid can be used that is not adsorbed onto the adsorbent and can be sprayed from the ejection holes 32a of the dispersion plate 32. Specifically, inert gases such as helium and neon can be used.

[0108] (Second Embodiment) In this embodiment, an example is described in which the configuration of the adsorbent 13 is modified from that of the refrigeration cycle device 10 of the first embodiment, as shown in Figure 3. Specifically, in the fluidized bed space 31a of the adsorbent 13 of this embodiment, a refrigerant inlet 13a is connected in addition to the adsorbent inlet 13b, etc. Also, in the adsorbent 13 of this embodiment, the powder nozzle 33 is eliminated.

[0109] In this embodiment, the refrigerant inlet 13a is located above the fluidized bed space 31a. In other words, the refrigerant inlet 13a, like the adsorbent inlet 13b, is located closer to the upper surface than the bottom surface of the main body 31. The refrigerant inlet 13a is located above the adsorbent that is in a fluidized bed state in the fluidized bed space 31a.

[0110] Above the fluidized bed space 31a, a refrigerant introduction pipe 33a is arranged to guide the refrigerant flowing in through the refrigerant inlet 13a to a position above the adsorbent that is fluidized within the fluidized bed space 31a. Similarly, above the fluidized bed space 31a, an adsorbent introduction pipe 33b is arranged to guide the adsorbent flowing in through the adsorbent inlet 13b to a position above the adsorbent that is fluidized within the fluidized bed space 31a. The other configurations and operation of the refrigeration cycle device 10 are the same as in the first embodiment.

[0111] Therefore, the air conditioning system 1 of this embodiment can cool the room, just as in the first embodiment. Furthermore, the refrigeration cycle system 10 of this embodiment can also obtain the same effects as in the first embodiment. That is, it is possible to achieve stable fluidization of the adsorbent in the adsorbent 13, and to suppress the decrease in operating efficiency caused by the fluidization of the adsorbent.

[0112] Furthermore, since the adsorbent 13 of this embodiment employs a refrigerant introduction pipe 33a and an adsorbent introduction pipe 33b, the refrigerant discharged from the compressor 11 and the adsorbent transported by the adsorbent pump 12 can be introduced into the fluidized bed space 31a with a simple configuration.

[0113] Furthermore, in this embodiment, the refrigerant discharged from the compressor 11 is guided above the fluidized bed of the adsorbent. Therefore, in the adsorbent 13 of this embodiment, the adsorbent inside the adsorbent 13 is fluidized only by the circulating refrigerant pumped from the turbo fan 35. As a result, even if the refrigerant discharge capacity of the compressor 11 fluctuates due to load fluctuations, etc., there is no need to change the airflow capacity of the turbo fan 35, and the fluidization of the adsorbent inside the adsorbent 13 can be achieved more stably.

[0114] (Third Embodiment) In this embodiment, an example is described in which the refrigeration cycle device 10a shown in the overall configuration diagram of Figure 4 is applied to the air conditioning device 1a. In the refrigeration cycle device 10a, the adsorption pump 12 is eliminated compared to the refrigeration cycle device 10 described in the first embodiment, and a discharge-side ejector 51 and a high-pressure-side separator 52 are adopted.

[0115] In the refrigeration cycle device 10a, the inlet side of the discharge nozzle portion 51a of the discharge ejector 51 is connected to the discharge port of the compressor 11.

[0116] The discharge-side ejector 51 draws in the mixed refrigerant that has flowed out of the mixed refrigerant outlet 16c of the low-pressure-side separator 16 by the suction action of the discharge-side injected refrigerant sprayed from the discharge-side nozzle section 51a. Furthermore, the discharge-side ejector 51 converts the kinetic energy (i.e., expansion energy) of the mixed refrigerant, which is the discharge-side injected refrigerant mixed with an adsorbent, into pressure energy, thereby increasing the pressure of the mixed refrigerant.

[0117] The detailed configuration of the discharge-side ejector 51 will be explained with reference to Figure 5. The discharge-side ejector 51 has a discharge-side nozzle portion 51a and a discharge-side body portion 51b.

[0118] The discharge nozzle section 51a is a nozzle that converts the pressure energy of the discharged refrigerant discharged from the compressor 11 into kinetic energy and injects the refrigerant. The discharge nozzle section 51a is formed of a substantially cylindrical metal member (made of stainless steel in this embodiment) that gradually tapers in the direction of refrigerant flow.

[0119] The discharge nozzle section 51a reduces the discharge refrigerant pressure isentropically and accelerates it to supersonic speed, then injects the discharge-side injected refrigerant into the discharge-side mixing section 51e formed in the discharge-side body section 51b. A so-called Laval nozzle or a tapered nozzle can be used as the discharge-side nozzle section 51a.

[0120] The discharge-side body portion 51b supports and fixes the discharge-side nozzle portion 51a and forms the outer shell of the discharge-side ejector 51. The discharge-side body portion 51b is made of a substantially cylindrical member made of metal (in this embodiment, made of aluminum alloy). The discharge-side nozzle portion 51a is fixed inside the discharge-side body portion 51b at one end in the longitudinal direction by means of press-fitting or the like. The discharge-side body portion 51b may be made of resin.

[0121] On the cylindrical wall surface of the discharge-side body portion 51b, a discharge-side suction port 51c is formed in the portion corresponding to the outer circumference of the discharge-side nozzle portion 51a. This port penetrates the inside and outside of the discharge-side body portion 51b and communicates with the refrigerant injection port of the discharge-side nozzle portion 51a. The discharge-side suction port 51c is a through-hole that draws the mixed refrigerant that has flowed out of the low-pressure separator 16 into the interior of the discharge-side body portion 51b due to the suction action of the discharge-side injected refrigerant sprayed from the discharge-side nozzle portion 51a.

[0122] Furthermore, a discharge-side suction passage 51d, a discharge-side mixing section 51e, and a discharge-side pressure boosting section 51f are formed inside the discharge-side body section 51b. The discharge-side suction passage 51d is a passage that guides the mixed refrigerant sucked in from the discharge-side suction port 51c to the discharge-side mixing section 51e. The discharge-side mixing section 51e is a space for mixing the mixed refrigerant sucked in from the discharge-side suction port 51c with the discharge-side injected refrigerant. The discharge-side mixing section 51e is formed in a substantially cylindrical shape.

[0123] The discharge-side pressure boosting section 51f is a space for increasing the pressure of the mixed refrigerant, which is drawn in from the discharge-side suction port 51c and the discharge-side injected refrigerant. The discharge-side pressure boosting section 51f is formed in a frustoconical shape, with its cross-sectional area expanding in the direction of the mixed refrigerant flow. In the discharge-side pressure boosting section 51f, the kinetic energy of the mixed refrigerant is converted into pressure energy by the action of the shock wave generated by the discharge-side injected refrigerant and the expansion of the passage cross-sectional area.

[0124] Therefore, the discharge-side ejector 51 is a discharge-side transport unit that uses the pressure energy of the discharged refrigerant discharged from the compressor 11 to transport the mixed refrigerant that has flowed out of the low-pressure-side separator 16 to the discharged refrigerant side. In other words, the discharge-side ejector 51 uses the pressure energy of the discharged refrigerant to mix the mixed refrigerant that has flowed out of the low-pressure-side separator 16 with the discharge-side injected refrigerant, which is the discharged refrigerant that has consumed the pressure energy.

[0125] As shown in Figure 4, the mixed refrigerant inlet 52a of the high-pressure separator 52 is connected to the mixed refrigerant outlet of the discharge-side pressure boosting unit 51f of the discharge-side ejector 51. The high-pressure separator 52 is a high-pressure separation unit that extracts a portion of the refrigerant that does not contain adsorbent from the mixed refrigerant flowing out of the discharge-side ejector 51. In other words, the high-pressure separator 52 separates the refrigerant from the mixed refrigerant.

[0126] The basic configuration of the high-pressure side separator 52 is the same as that of the low-pressure side separator 16. Therefore, the high-pressure side separator 52 has the same mixed refrigerant inlet 52a, gas phase refrigerant outlet 52b, and mixed refrigerant outlet 52c as the low-pressure side separator 16. Also, the internal space of the high-pressure side separator 52 is divided into an upper space 52d and a lower space 52e by an adsorbent filter 52f, similar to the low-pressure side separator 16.

[0127] The gas phase refrigerant outlet 52b of the high-pressure separator 52 is connected to the refrigerant inlet 13a side of the adsorbent 13. The mixed refrigerant outlet 52c of the high-pressure separator 52 is connected to the adsorbent inlet 13b side of the adsorbent 13. The other configurations of the refrigeration cycle device 10a and the air conditioning device 1a are the same as those described in the first embodiment of the refrigeration cycle device 10 and the air conditioning device 1.

[0128] Next, the operation of the air conditioning system 1a of this embodiment with the above configuration will be described. The basic operation of the air conditioning system 1a is the same as the operation of the air conditioning system 1 described in the first embodiment. Therefore, in the refrigeration cycle system 10a, the discharged refrigerant discharged from the compressor 11 flows into the discharge-side nozzle portion 51a of the discharge-side ejector 51.

[0129] The discharge refrigerant flowing into the discharge nozzle section 51a is depressurized isentropically and injected into the discharge mixing section 51e of the discharge body section 51b. Then, due to the suction action of the discharge-side injected refrigerant injected from the discharge nozzle section 51a, the mixed refrigerant that flows out from the mixed refrigerant outlet 16c of the low-pressure separator 16 is sucked in from the discharge suction port 51c.

[0130] The mixed refrigerant drawn in from the discharge-side suction port 51c flows into the discharge-side mixing section 51e via the discharge-side suction passage 51d. In this case, if the mixed refrigerant drawn in from the discharge-side suction port 51c contains liquid-phase refrigerant, the liquid-phase refrigerant absorbs heat from the discharge-side injected refrigerant and evaporates in the discharge-side mixing section 51e. As a result, the mixed refrigerant in the discharge-side mixing section 51e becomes a mixed refrigerant in which the adsorbent is mixed with the gaseous-phase refrigerant, and flows into the discharge-side pressurizing section 51f.

[0131] In the discharge-side pressure boosting section 51f, the kinetic energy of the mixed refrigerant is converted into pressure energy due to the action of the shock wave generated by the discharge-side injected refrigerant and the expansion of the passage cross-sectional area. As a result, the pressure of the mixed refrigerant increases.

[0132] The mixed refrigerant that flows out from the discharge-side pressure boosting section 51f of the discharge-side ejector 51 flows into the lower space 52e of the high-pressure-side separator 52. A portion of the refrigerant contained in the mixed refrigerant that flows into the lower space 52e flows into the upper space 52d via the adsorbent filter 52f.

[0133] The refrigerant flowing out from the gas phase refrigerant outlet 52b, which communicates with the upper space 52d, flows into the duct space 31b through the refrigerant inlet 13a of the adsorbent 13. The mixed refrigerant flowing out from the mixed refrigerant outlet 52c, which communicates with the lower space 52e, flows into the fluidized bed space 31a through the adsorbent inlet 13b of the adsorbent 13. Other operations are the same as in the first embodiment.

[0134] Therefore, in the air conditioning device 1a of this embodiment, the room can be cooled by blowing the cooled air that has passed through the decoupling device 15 into the room. Furthermore, the refrigeration cycle device 10a of this embodiment can also obtain the same effects as the refrigeration cycle device 10 described in the first embodiment. That is, it is possible to achieve stable fluidization of the adsorbent in the adsorbent 13, and to suppress the decrease in operating efficiency caused by the fluidization of the adsorbent.

[0135] Furthermore, the refrigeration cycle device 10a of this embodiment employs a discharge-side ejector 51. This allows for the transport of adsorbent material with less power consumption than the adsorbent pump 12, further suppressing the decrease in operating efficiency. In addition, it enables the realization of an adsorbent material transport section with fewer sliding and sealing parts than the adsorbent pump 12. Therefore, the refrigeration cycle device 10a of this embodiment can improve the reliability of a hybrid type refrigeration cycle device.

[0136] (Fourth Embodiment) In this embodiment, an example is described in which the refrigeration cycle device 10b shown in the overall configuration diagram of Figure 6 is applied to the air conditioning device 1b. In the refrigeration cycle device 10b, the high-pressure side separator 52 is eliminated compared to the refrigeration cycle device 10a described in the third embodiment, and the adsorbent 13, which is the adsorption part, is changed to an adsorbent 131.

[0137] In the refrigeration cycle device 10b, the refrigerant inlet 13a side of the adsorbent 131 is connected to the mixed refrigerant outlet of the discharge-side pressure boosting section 51f of the discharge-side ejector 51.

[0138] The detailed configuration of the adsorbent 131 of this embodiment will be explained with reference to Figure 7. In Figure 7, various sensors are omitted from the illustration for clarity. This is also the case in the partial cross-sectional view of the adsorbent of the embodiment described later. In the adsorbent 131 of this embodiment, the adsorbent inlet 13b and the powder nozzle 33 have been eliminated compared to the adsorbent 13 described in the first embodiment. A mixed refrigerant passage 36 is arranged inside the adsorbent 131.

[0139] The mixed refrigerant passage 36 has a portion that extends vertically and is a mixed refrigerant passage that guides the mixed refrigerant that has flowed out from the discharge-side ejector 51 to the upper side of the fluidized bed space 31a. More specifically, the mixed refrigerant passage 36 is a refrigerant passage that guides the mixed refrigerant that has flowed out from the discharge-side ejector 51 to the upper side of the adsorbent that is in a fluidized bed state inside the fluidized bed space 31a.

[0140] Here, Figure 7 shows an example in which the refrigerant inlet 13a is located on the side facing the duct space 31b, but the arrangement of the refrigerant inlet 13a is not limited to this. The refrigerant inlet 13a may be located on the side facing the fluidized bed space 31a as long as it is possible to guide the mixed refrigerant to the upper side of the fluidized bed space 31a. The other configurations of the refrigeration cycle device 10b and the air conditioning device 1b are the same as those of the refrigeration cycle device 10a and the air conditioning device 1a described in the third embodiment.

[0141] Next, the operation of the air conditioning system 1b of this embodiment with the above configuration will be described. The basic operation of the air conditioning system 1b is the same as the operation of the air conditioning system 1a described in the third embodiment. Therefore, in the refrigeration cycle system 10b, as in the third embodiment, the discharged refrigerant discharged from the compressor 11 flows into the discharge-side nozzle portion 51a of the discharge-side ejector 51.

[0142] In the discharge-side ejector 51, similar to the third embodiment, the mixed refrigerant that has flowed out from the mixed refrigerant outlet 16c of the low-pressure-side separator 16 is sucked in from the discharge-side suction port 51c by the suction action of the discharge-side injected refrigerant. In the discharge-side pressure boosting section 51f, the pressure of the mixed refrigerant increases.

[0143] The mixed refrigerant flowing out from the discharge-side pressure boosting section 51f of the discharge-side ejector 51 flows into the refrigerant inlet 13a of the adsorbent 131. The mixed refrigerant flowing into the refrigerant inlet 13a of the adsorbent 131 is guided to the upper side of the fluidized bed space 31a via the mixed refrigerant passage 36. The adsorbent contained in the mixed refrigerant flowing out from the mixed refrigerant passage 36 moves from the upper side to the lower side due to the action of gravity. Other operations are the same as in the first embodiment.

[0144] Therefore, in the air conditioning device 1b of this embodiment, the room can be cooled by blowing the cooled air that has passed through the decoupling device 15 into the room. Furthermore, the refrigeration cycle device 10b of this embodiment can also obtain the same effects as the refrigeration cycle device 10 described in the first embodiment. That is, it is possible to achieve stable fluidization of the adsorbent in the adsorbent 13, and to suppress the decrease in operating efficiency caused by the fluidization of the adsorbent.

[0145] Furthermore, in the adsorbent 131 of this embodiment, the refrigeration cycle device 10a guides the mixed refrigerant through the mixed refrigerant passage 36 to a position above the adsorbent that is fluidized within the fluidized bed space 31a. This allows the adsorbent to flow evenly into the fluidized bed space 31a, even with a simple configuration that eliminates the powder nozzle 33.

[0146] Furthermore, in this embodiment, the adsorbent inside the adsorbent 13 is made into a fluidized bed solely by the circulating refrigerant pumped from the turbo fan 35. Therefore, similar to the third embodiment, it is possible to achieve even more stable fluidization of the adsorbent inside the adsorbent 13.

[0147] (Fifth Embodiment) In this embodiment, an example is described in which the configuration of the adsorbent 131 is modified from that of the refrigeration cycle device 10b of the fourth embodiment, as shown in Figure 8. In this embodiment, a collision plate 36a is added to the adsorbent 131 described in the fourth embodiment.

[0148] The impact plate 36a is a plate-shaped member that collides with the mixed refrigerant flowing out of the mixed refrigerant outlet of the mixed refrigerant passage 36. The impact plate 36a is located within the fluidized bed space 31a and is positioned above the mixed refrigerant outlet of the mixed refrigerant passage 36, extending horizontally. As a result, the mixed refrigerant flowing upward from the mixed refrigerant passage 36 collides with the impact plate 36a, reducing its flow velocity. Then, the adsorbent contained in the mixed refrigerant moves from the top to the bottom due to the action of gravity. The other configurations and operation of the refrigeration cycle device 10b are the same as in the fourth embodiment.

[0149] Therefore, the air conditioning system 1b of this embodiment can cool the room, similar to the fourth embodiment. Furthermore, the refrigeration cycle system 10b of this embodiment can also obtain the same effects as the fourth embodiment. That is, it is possible to achieve stable fluidization of the adsorbent in the adsorbent 13, and to suppress the decrease in operating efficiency caused by the fluidization of the adsorbent.

[0150] Furthermore, since the adsorbent 131 of this embodiment employs an impact plate 36a, it can separate the gaseous refrigerant contained in the mixed refrigerant flowing out of the mixed refrigerant passage 36 from the adsorbent, similar to a so-called impact-type gas-liquid separator. The separated adsorbent can then be reliably moved downwards.

[0151] (Sixth Embodiment) In this embodiment, an example is described in which the configuration of the adsorbent 131 is modified from that of the refrigeration cycle device 10b of the fourth embodiment, as shown in Figure 9. In this embodiment, the fluidized bed space 31a of the adsorbent 131 is connected to the adsorbent inlet 13b, etc., as well as the refrigerant inlet 13a. The refrigerant inlet 13a in this embodiment is formed on the upper surface of the main body 31, similar to the refrigerant outlet 13c.

[0152] Therefore, in the adsorber 131 of this embodiment, the mixed refrigerant that flows out from the mixed refrigerant passage 36 is blown out from the upper side to the lower side of the fluidized bed space 31a. The other configurations and operation of the refrigeration cycle device 10b are the same as in the fourth embodiment.

[0153] Therefore, the air conditioning device 1b of this embodiment can cool the room, similar to the fourth embodiment. Furthermore, the refrigeration cycle device 10b of this embodiment can also obtain the same effects as the fourth embodiment. That is, it is possible to achieve stable fluidization of the adsorbent in the adsorbent 13, and to suppress the decrease in operating efficiency caused by the fluidization of the adsorbent.

[0154] (Seventh Embodiment) In this embodiment, an example is described in which the refrigeration cycle device 10c shown in the overall configuration diagram of Figure 10 is applied to the air conditioning device 1c. In the refrigeration cycle device 10c, the turbo fan 35 is eliminated compared to the refrigeration cycle device 10b described in the fourth embodiment, and a branching section 53, a circulation expansion valve 54, and a circulation side ejector 55 are adopted.

[0155] In the refrigeration cycle device 10c, the inlet side of the branching section 53 is connected to the discharge port of the compressor 11. The branching section 53 branches the flow of the discharged refrigerant discharged from the compressor 11. The branching section 53 is a three-way joint having three inlet and outlet ports that communicate with each other. The inlet side of the discharge nozzle portion 51a of the discharge side ejector 51 is connected to one of the outlet ports of the branching section 53. The inlet side of the circulation expansion valve 54 is connected to the other outlet port of the branching section 53.

[0156] The circulating expansion valve 54 is a refrigerant pressure reducing unit that reduces the pressure of the refrigerant flowing out from the other outlet of the branching unit 53. Furthermore, the circulating expansion valve 54 is a refrigerant flow rate adjustment unit that adjusts the flow rate of the refrigerant flowing into the circulating nozzle unit 55a of the circulating ejector 55. The basic configuration of the circulating expansion valve 54 is the same as that of the expansion valve 14.

[0157] The outlet of the circulating expansion valve 54 is connected to the inlet side of the circulating nozzle portion 55a of the circulating ejector 55. The circulating ejector 55 draws in the refrigerant that has flowed out of the refrigerant circulation passage 34 by the suction action of the circulating injection refrigerant sprayed from the circulating nozzle portion 55a. Furthermore, the circulating ejector 55 converts the kinetic energy (i.e., expansion energy) of the mixed refrigerant, which is a mixture of the discharged injection refrigerant and an adsorbent, into pressure energy, thereby increasing the pressure of the mixed refrigerant.

[0158] The basic configuration of the circulating ejector 55 is the same as that of the discharge-side ejector 51. Therefore, the circulating ejector 55 has a circulating nozzle section 55a and a circulating body section 55b, similar to the discharge-side ejector 51. The circulating body section 55b has a circulating suction port 55c and a circulating pressure boosting section 55f, similar to the discharge-side ejector 51.

[0159] The outlet of the refrigerant circulation passage 34 is connected to the circulation-side suction port 55c. The duct space 31b side of the adsorption unit 131 is connected to the mixed refrigerant outlet of the circulation-side pressure boosting unit 55f.

[0160] Therefore, the adsorbent 131 of this embodiment has a circulation supply unit for the adsorption section that circulates and supplies the refrigerant that has flowed out of the adsorbent 131 back to the adsorbent 131. The circulation supply unit for the adsorption section of this embodiment is composed of a refrigerant circulation passage 34, a circulation-side adsorbent filter 34a, a circulation-side ejector 55, a circulation expansion valve 54, and the like.

[0161] The dimensions of the circulation-side ejector 55 are determined to reduce the amount of pressure increase in the circulation-side pressure boosting section 55f and increase the amount of suction from the circulation-side suction port 55c, compared to the discharge-side ejector 51. The other configurations of the refrigeration cycle device 10c and the air conditioning device 1c are the same as those of the refrigeration cycle device 10b and the air conditioning device 1b described in the fourth embodiment.

[0162] Next, the operation of the air conditioning system 1c of this embodiment with the above configuration will be described. The basic operation of the air conditioning system 1c is the same as the operation of the air conditioning system 1b described in the fourth embodiment.

[0163] Furthermore, the control program for the refrigeration cycle device 10c determines the throttle opening of the circulating expansion valve 54 by referring to a control map pre-stored in the control device 40 based on the rotational speed of the compressor 11. The control map determines the throttle opening of the circulating expansion valve 54 so that the adsorbent in the fluidized bed space 31a of the adsorbent 131 becomes a fluidized bed.

[0164] Therefore, in the refrigeration cycle device 10c, the flow of discharged refrigerant discharged from the compressor 11 is branched at the branching section 53. One of the refrigerants branched at the branching section 53 flows into the discharge nozzle section 51a of the discharge side ejector 51.

[0165] In the discharge-side ejector 51, similar to the fourth embodiment, the mixed refrigerant that has flowed out from the mixed refrigerant outlet 16c of the low-pressure-side separator 16 is sucked in from the discharge-side suction port 51c by the suction action of the discharge-side injected refrigerant. In the discharge-side pressure boosting section 51f, the pressure of the mixed refrigerant increases.

[0166] The mixed refrigerant that flows out from the discharge-side pressure boosting section 51f of the discharge-side ejector 51 flows into the refrigerant inlet 13a of the adsorber 131. The mixed refrigerant that flows into the refrigerant inlet 13a of the adsorber 131 is guided to the upper side of the fluidized bed space 31a via the mixed refrigerant passage 36.

[0167] The other refrigerant branched off at the branching section 53 flows into the circulation nozzle section 55a of the circulation-side ejector 55. In the circulation-side ejector 55, similar to the discharge-side ejector 51, the circulating refrigerant that has flowed from the fluidized bed space 31a into the refrigerant circulation passage 34 is drawn in from the circulation-side suction port 55c by the suction action of the circulating-side injected refrigerant sprayed from the circulation-side nozzle section 55a.

[0168] In the circulation-side pressure boosting section 55f, the pressure of the refrigerant, which is a combination of the circulating-side injected refrigerant sprayed from the circulation-side nozzle section 55a and the refrigerant drawn in from the circulation-side suction port 55c, increases. The circulating refrigerant flowing out from the circulation-side pressure boosting section 55f is pumped into the duct space 31b. Other operations are the same as in the fourth embodiment.

[0169] Therefore, in the air conditioning device 1c of this embodiment, the room can be cooled by blowing the cooled air that has passed through the decoupling device 15 into the room. Furthermore, the refrigeration cycle device 10c of this embodiment can also obtain the same effects as the refrigeration cycle device 10 described in the first embodiment. That is, it is possible to achieve stable fluidization of the adsorbent in the adsorbent 13, and to suppress the decrease in operating efficiency caused by the fluidization of the adsorbent.

[0170] Furthermore, the refrigeration cycle device 10c of this embodiment employs a circulation-side ejector 55. This makes it possible to realize a circulation supply section with fewer sliding and sealing parts than the turbo fan 35. In addition, even if an adsorbent enters the refrigerant circulation passage 34, the circulation-side ejector 55 is less likely to be damaged than the turbo fan 35. As a result, the refrigeration cycle device 10c of this embodiment can improve the reliability of a hybrid refrigeration cycle device.

[0171] (Eighth Embodiment) In this embodiment, an example is described in which an auxiliary heat transfer medium circuit 60 is added to the refrigeration cycle device 10 of the first embodiment, as shown in the overall configuration diagram of Figure 11. The auxiliary heat transfer medium circuit 60 is a circuit that circulates the auxiliary heat transfer medium. In this embodiment, the same type of heat transfer medium as the high-temperature side heat transfer medium is used as the auxiliary heat transfer medium. The auxiliary heat transfer medium circuit 60 is equipped with an auxiliary heat transfer medium pump 61, a circulation side heat exchanger 62, a utilization side heat exchanger 63, etc.

[0172] The auxiliary heat transfer fluid pump 61 is a heat transfer fluid pumping unit that sucks in the auxiliary heat transfer fluid that has flowed out from the user-side heat exchanger 63 and pumps it to the inlet side of the heat transfer fluid passage of the circulation-side heat exchanger 62. The basic configuration of the auxiliary heat transfer fluid pump 61 is the same as that of the high-temperature side heat transfer fluid pump 21.

[0173] The circulating heat exchanger 62 is a heat exchange unit that exchanges heat between the refrigerant flowing through the refrigerant passage and the auxiliary heat transfer medium flowing through the heat transfer medium passage. The refrigerant passage of the circulating heat exchanger 62 is connected to the refrigerant circulation passage 34. Therefore, circulating refrigerant pumped from the turbo fan 35 flows through the refrigerant passage. The auxiliary heat transfer medium pumped from the auxiliary heat transfer medium pump 61 flows through the heat transfer medium passage.

[0174] In the circulating heat exchanger 62, the heat contained in the circulating refrigerant is released to the auxiliary heat transfer medium, and the auxiliary heat transfer medium, which is the object of heat exchange, is heated.

[0175] The outlet of the heat transfer medium passage of the circulating heat exchanger 62 is connected to the heat transfer medium inlet of the utilization-side heat exchanger 63. The utilization-side heat exchanger 63 is a heat exchange section that exchanges heat between the auxiliary heat transfer medium and the fluid to be heated. In the utilization-side heat exchanger 63, the heat contained in the auxiliary heat transfer medium heated in the circulating heat exchanger 62 is released to the fluid to be heated. The fluid to be heated can be air supplied to the air-conditioned space, hot water supplied to the kitchen or bathroom, etc. It may also be domestic water, etc.

[0176] The intake side of the auxiliary heat transfer fluid pump 61 is connected to the heat transfer fluid outlet of the heat transfer fluid outlet of the heat exchanger 63 on the user side. The rest of the refrigeration cycle device 10 is the same as in the first embodiment.

[0177] Next, the operation of the air conditioning system 1 of this embodiment, which has the above configuration, will be described. The basic operation of the air conditioning system 1 is the same as in the first embodiment. Furthermore, in the control program of this embodiment, the operation of the auxiliary heat transfer fluid pump 61 is controlled so as to achieve a predetermined standard pumping capacity.

[0178] Therefore, the refrigeration cycle device 10 and the high-temperature side heat transfer medium circuit 20 operate in the same manner as in the first embodiment. In the auxiliary heat transfer medium circuit 60, the auxiliary heat transfer medium pumped from the auxiliary heat transfer medium pump 61 flows into the heat transfer medium passage of the circulating side heat exchanger 62. The auxiliary heat transfer medium that flows into the heat transfer medium passage of the circulating side heat exchanger 62 is heated by heat exchange with the refrigerant flowing through the refrigerant passage. As a result, the refrigerant that is pumped to the duct space 31b via the refrigerant circulation passage 34 is cooled.

[0179] The auxiliary heat transfer medium heated in the circulating heat exchanger 62 flows into the utilization-side heat exchanger 63. The auxiliary heat transfer medium that flows into the utilization-side heat exchanger 63 is cooled by heat exchange with the fluid to be heated. As a result, the fluid to be heated is heated. The auxiliary heat transfer medium that flows out of the utilization-side heat exchanger 63 is drawn into the auxiliary heat transfer medium pump 61 and pumped back into the heat transfer medium passage of the circulating heat exchanger 62. Other operations are the same as in the first embodiment.

[0180] Therefore, in the air conditioning system 1 of this embodiment, the room can be cooled by blowing the cooled air that has passed through the decoupling device 15 into the room. Furthermore, the refrigeration cycle device 10 of this embodiment can also obtain the same effects as in the first embodiment. That is, it is possible to achieve stable fluidization of the adsorbent in the adsorbent 13, and to suppress the decrease in operating efficiency caused by the fluidization of the adsorbent.

[0181] Furthermore, since the refrigeration cycle device 10 of this embodiment is equipped with a circulating heat exchanger 62, the heat of adsorption that could not be dissipated to the high-temperature heat transfer medium flowing through the heat transfer tubes 22 can be dissipated to the fluid to be heated via the refrigerant and auxiliary heat transfer medium. Therefore, the heat of adsorption can be effectively utilized.

[0182] (Ninth Embodiment) In this embodiment, an example is described in which the refrigeration cycle device 10e shown in the overall configuration diagram of Figure 12 is applied to the air conditioning device 1e. In the refrigeration cycle device 10e, compared to the refrigeration cycle device 10b described in the fourth embodiment, the adsorbent 13 as the adsorption part is changed to an adsorbent 132, and the detachable device 15 as the detachable part is changed to a detachable device 151.

[0183] In the refrigeration cycle device 10e, the mixed refrigerant inlet side of the adsorbent 132 is connected to the mixed refrigerant outlet of the discharge-side pressure boosting section 51f of the discharge-side ejector 51. The adsorbent 132 is a heat exchange unit for heat dissipation that exchanges heat between the mixed refrigerant flowing out from the discharge-side ejector 51 and outside air blown from an outside air fan (not shown), thereby releasing the heat of adsorption from the mixed refrigerant to the outside air. As the adsorbent 132, a heat exchanger or the like with an air passage for blown air formed around the refrigerant piping through which the mixed refrigerant flows can be used.

[0184] Furthermore, in the refrigeration cycle device 10e, the mixed refrigerant inlet 151a side of the decoupling device 151 is connected to the outlet of the expansion valve 14. The detailed configuration of the decoupling device 151 will be explained with reference to Figure 13.

[0185] The basic configuration of the desorber 151 is similar to that of the adsorber 13 described in the first embodiment. The desorber 151 has the same main body 71, dispersion plate 72, refrigerant circulation passage 74, turbo fan 75, etc. as the adsorber 13. The dispersion plate 72 divides the internal space of the main body 71 into a fluidized bed space 71a and a duct space 71b in the vertical direction. The dispersion plate 72 has ejection holes 72a similar to the ejection holes 32a of the dispersion plate 32.

[0186] The fluidized bed space 71a is connected to the mixed refrigerant inlet 151a, the adsorbent outlet 151b, and the refrigerant outlet 151c of the desorber 151. The mixed refrigerant inlet 151a is the part that allows the mixed refrigerant that has flowed out from the expansion valve 14 to flow into the fluidized bed space 71a of the desorber 151. The mixed refrigerant inlet 151a is located on the lower side of the fluidized bed space 71a. In other words, the mixed refrigerant inlet 151a is located closer to the bottom surface than to the top surface of the main body 71.

[0187] The adsorbent outlet 151b is the outlet for discharging the adsorbent, which has had the refrigerant desorbed in the fluidized bed space 71a. The adsorbent outlet 151b is located above the mixed refrigerant inlet 151a in the fluidized bed space 71a. The mixed refrigerant inlet 16a side of the low-pressure separator 16 is connected to the adsorbent outlet 151b.

[0188] The refrigerant outlet 151c is the refrigerant outlet section that allows refrigerant to flow out from the fluidized bed space 71a. The inlet of the refrigerant circulation passage 74 is connected to the refrigerant outlet 151c. Similar to the adsorbent 13, a circulation-side adsorbent filter 74a is arranged in the refrigerant circulation passage 74. The intake port of the turbo fan 75 is connected to the outlet of the refrigerant circulation passage 74. The duct space 71b side of the main body 71 is connected to the discharge port of the turbo fan 75.

[0189] Therefore, the decoupling unit 151 of this embodiment has a circulation supply unit for the decoupling section that circulates and supplies the refrigerant that has flowed out of the decoupling unit 151 back to the decoupling unit 151. The circulation supply unit for the decoupling section of this embodiment is composed of a refrigerant circulation passage 74, a circulation-side adsorbent filter 74a, a turbo fan 75, and the like.

[0190] Furthermore, multiple heat transfer tubes 82 are arranged within the fluidized bed space 71a. The heat transfer tubes 82 are heat exchange passages that exchange heat between the heat transfer medium circulating in the low-temperature side heat transfer medium circuit 80 and the mixed refrigerant flowing within the fluidized bed space 71a. The heat transfer tubes 82 are heat absorption passages that absorb heat from the low-temperature side heat transfer medium to remove the heat of desorption required to desorb the refrigerant from the adsorbent.

[0191] The diameter, number, and arrangement of the multiple heat transfer tubes 82 are determined so as not to obstruct the flow of refrigerant and adsorbent in the fluidized bed space 71a. Heat exchange promoting fins to facilitate heat exchange between the heat transfer medium and the mixed refrigerant, guide fins to direct the flow direction of the refrigerant and adsorbent in the fluidized bed space 31a from downward to upward, etc. may be formed on the outer circumference of the heat transfer tubes 82.

[0192] Next, the low-temperature side heat transfer medium circuit 80 shown in Figure 12 will be described. The low-temperature side heat transfer medium circuit 80 is a circuit that circulates the low-temperature side heat transfer medium. In this embodiment, the same type of heat transfer medium as the high-temperature side heat transfer medium is used as the low-temperature side heat transfer medium. The low-temperature side heat transfer medium circuit 80 is equipped with a low-temperature side heat transfer medium pump 81, a plurality of heat transfer tubes 82, a cooler core 83, and the like.

[0193] The low-temperature side heat transfer fluid pump 81 is a low-temperature side heat transfer fluid pumping unit that sucks in the low-temperature side heat transfer fluid that has flowed out from the cooler core 83 and pumps it to the inlet side of the multiple heat transfer tubes 82. The basic configuration of the low-temperature side heat transfer fluid pump 81 is the same as that of the high-temperature side heat transfer fluid pump 21.

[0194] The discharge port of the low-temperature heat transfer fluid pump 81 is connected to the inlet side of a plurality of heat transfer tubes 82 via a distribution unit. The outlets of the plurality of heat transfer tubes 82 are connected to the inlet side of the heat transfer fluid of a cooler core 83 via a manifold. The cooler core 83 is a cooling heat exchange unit that cools the blown air by exchanging heat between the low-temperature heat transfer fluid flowing out of the heat transfer tubes 82 and the blown air blown into the room from a blower (not shown).

[0195] The outlet of the cooler core 83 is connected to the inlet side of the low-temperature side heat transfer fluid pump 81. The other configurations of the refrigeration cycle device 10e and the air conditioning device 1e are the same as those described in the fourth embodiment for the refrigeration cycle device 10b and the air conditioning device 1b.

[0196] Next, the operation of the air conditioning system 1e of this embodiment with the above configuration will be described. The basic operation of the air conditioning system 1e is the same as the operation of the air conditioning system 1b described in the fourth embodiment.

[0197] Furthermore, the control program for the refrigeration cycle device 10c determines the rotation speed of the turbo fan 75 (i.e., the airflow capacity) by referring to a control map pre-stored in the control device 40 based on the rotation speed of the compressor 11. In the control map, similar to the first embodiment, the rotation speed of the turbo fan 75 is determined so that the adsorbent in the fluidized bed space 71a of the desorber 151 becomes a fluidized bed.

[0198] Furthermore, the control program controls the operation of the low-temperature side heat transfer fluid pump 81 so that it exhibits a predetermined standard pumping capacity.

[0199] Therefore, in the refrigeration cycle device 10e, the discharged refrigerant discharged from the compressor 11 flows into the discharge nozzle portion 51a of the discharge side ejector 51.

[0200] In the discharge-side ejector 51, similar to the fourth embodiment, the mixed refrigerant that has flowed out from the mixed refrigerant outlet 16c of the low-pressure-side separator 16 is sucked in from the discharge-side suction port 51c by the suction action of the discharge-side injected refrigerant. In the discharge-side pressure boosting section 51f, the pressure of the mixed refrigerant increases.

[0201] The mixed refrigerant that flows out from the discharge-side pressure boosting section 51f of the discharge-side ejector 51 flows into the refrigerant inlet of the adsorbent 132. The mixed refrigerant that flows into the adsorbent 132 releases the internal energy stored when the adsorbent adsorbs the refrigerant as heat of adsorption to the outside air.

[0202] The mixed refrigerant that flows out from the adsorber 132 flows into the expansion valve 14 and is depressurized. The mixed refrigerant that has been depressurized in the expansion valve 14 flows into the mixed refrigerant inlet 151a of the desorber 151. The mixed refrigerant that flows into the fluidized bed space 71a from the mixed refrigerant inlet 151a of the desorber 151 is suspended and floated by the refrigerant ejected from the ejection holes 72a of the dispersion plate 72, and becomes a fluidized bed.

[0203] When the fluidized bed adsorbent desorbs the refrigerant, it absorbs heat from the low-temperature heat transfer medium flowing through the heat transfer tube 82. This cools the low-temperature heat transfer medium. Furthermore, in the fluidized bed space 71a, due to weight loss and classification phenomena as the desorption reaction progresses, the adsorbent with the smallest adsorption capacity moves upward. The adsorbent that has moved upward, along with some of the refrigerant, flows out of the adsorbent outlet 151b of the desorber 151 and into the mixed refrigerant inlet 16a of the low-pressure separator 16.

[0204] The refrigerant ejected from the discharge holes 72a of the dispersion plate 72 into the fluidized bed space 71a, and the remaining refrigerant that did not flow out from the adsorbent outlet 151b of the refrigerant desorber 151, flow out from the refrigerant outlet 151c of the desorber 151 and into the refrigerant circulation passage 74.

[0205] The refrigerant flowing into the refrigerant circulation passage 74 is drawn into the turbo fan 75. The circulating refrigerant pumped from the turbo fan 75 is then pumped into the duct space 71b. The refrigerant pumped into the duct space 71b is then ejected into the fluidized bed space 71a from the ejection holes 72a of the dispersion plate 72. The operation of the rest of the refrigeration cycle device 10e is the same as in the fourth embodiment.

[0206] In the low-temperature heat transfer medium circuit 80, the low-temperature heat transfer medium pumped from the low-temperature heat transfer medium pump 81 flows into the heat transfer tubes 82. The low-temperature heat transfer medium that flows into the heat transfer tubes 82 is cooled by the adsorption of heat absorbed by the adsorbent. The low-temperature heat transfer medium cooled in the heat transfer tubes 82 flows into the cooler core 83. In the cooler core 83, the low-temperature heat transfer medium cooled in the heat transfer tubes 82 and the blown air exchange heat. As a result, the blown air is cooled. The low-temperature heat transfer medium that flows out of the cooler core 83 is drawn into the low-temperature heat transfer medium pump 81 and pumped back into the heat transfer tubes 82.

[0207] As described above, the air conditioning system 1 of this embodiment can cool the room by blowing out the cooled air that has passed through the cooler core 83 into the room.

[0208] Furthermore, the decontamination unit 151 of this embodiment is equipped with a circulation supply unit for the decontamination unit similar to the circulation supply unit for the adsorption unit described in the first embodiment. This allows the adsorbent in the fluidized bed space 71a to be stably converted into a fluidized bed by injecting refrigerant into the fluidized bed space 71a.

[0209] Furthermore, by fluidizing the adsorbent in the fluidized bed space 71a, the relative velocity between the adsorbent and the refrigerant can be increased, thereby increasing the slip ratio. In other words, the residence time of the adsorbent from the desorbent 151 until it flows out of the desorbent 151 can be increased. In addition, the contact area between the adsorbent and the refrigerant can be increased.

[0210] Therefore, according to the refrigeration cycle device 10e of this embodiment, by making the adsorbent in the fluidized bed space 71a a fluidized bed, the desorption reaction between the refrigerant and the adsorbent can be sufficiently advanced to approach an equilibrium state.

[0211] Furthermore, the circulation supply unit pumps the refrigerant that has flowed out of the desorber 151 and circulates it back to the desorber 151. Therefore, similar to the circulation supply unit for the adsorption unit described in the first embodiment, the adsorbent in the fluidized bed space 71a can be made into a fluidized bed with relatively little power consumption.

[0212] As a result, the refrigeration cycle device 10e of this embodiment can achieve stable fluidization of the adsorbent in the desorber 151, and can suppress the deterioration of the cycle's operating efficiency in order to fluidize the adsorbent in the desorber 151.

[0213] This disclosure is not limited to the embodiments described above, and can be modified in various ways without departing from the spirit of this disclosure, as follows.

[0214] In the embodiments described above, examples were given in which the refrigeration cycle devices 10 to 10e according to the present disclosure were applied to air conditioning devices 1 to 1e, respectively. However, the application of the refrigeration cycle devices 10 to 10e according to the present disclosure is not limited thereto. For example, they may be applied to vehicle air conditioning systems, refrigeration systems, refrigerators, etc.

[0215] Furthermore, in the above-described embodiment, an example was explained in which the adsorption unit and the high-temperature heat transfer medium circuit 20 release the heat of adsorption to the outside air, and the desorption unit and the low-temperature heat transfer medium circuit 80 absorb the heat of desorption from the blown air, but the embodiment is not limited to this. Alternatively, the adsorption unit and the high-temperature heat transfer medium circuit 20 may release the heat of adsorption to the object to be heated, and the desorption unit and the low-temperature heat transfer medium circuit 80 may absorb the heat of desorption from the outside air.

[0216] In this case, it may be applied to heating devices that heat blown air as the object to be heated, hot water supply devices that heat domestic water, etc.

[0217] The configuration of the refrigeration cycle device is not limited to the configuration disclosed in the embodiments described above.

[0218] In the above-described embodiment, an example was explained in which circulation-side adsorbent filters 34a and 74a are placed at the inlets of the refrigerant circulation passages 34 and 74, but the embodiment is not limited to this.

[0219] The circulation-side adsorbent filters 34a and 74a should be positioned in a way that prevents the adsorbent from moving into the duct spaces 31b and 71b. More preferably, they should be positioned upstream of the refrigerant flow from the intake ports of the turbofans 35 and 75, and upstream of the refrigerant flow from the circulation-side suction port 55c of the circulation-side ejector 55. Therefore, the circulation-side adsorbent filters 34a and 74a may be positioned within the fluidized bed spaces 31a and 71a.

[0220] In the seventh embodiment described above, an example in which a circulating expansion valve 54 is employed was explained, but the invention is not limited thereto. For example, the circulating expansion valve 54 and the circulating side ejector 55 may be integrated. In this case, a needle-shaped or conical valve body may be placed in the passage of the circulating side nozzle portion 55a of the circulating side ejector 55, and the valve body may be displaced to perform the same function as the circulating expansion valve 54.

[0221] In the eighth embodiment described above, an example in which an auxiliary heat transfer medium circuit 60 is added was explained, but the invention is not limited to this. For example, a heat exchanger that exchanges heat between the refrigerant and the fluid to be heated may be used as the circulating heat exchanger 62.

[0222] Furthermore, although the above-described embodiment described an example in which a metal-organic structure was used as the adsorbent, the invention is not limited to this. For example, activated carbon in the form of a solid powder or solid particles may be used as the adsorbent.

[0223] In each of the embodiments described above, the group of control sensors connected to the input side of the control device 40 is not limited to the detection unit disclosed in the embodiments described above. Various detection units may be added as needed.

[0224] Furthermore, although the above-described embodiment uses carbon dioxide as the refrigerant, it is not limited to this. For example, R1234yf, R134a, R600a, R410A, R404A, R32, R407C, R290 (propane), ammonia, or a mixture thereof may be used as the refrigerant.

[0225] Furthermore, although the above-described embodiment described an example in which an aqueous ethylene glycol solution was used as the high-temperature heat transfer medium, auxiliary heat transfer medium, and low-temperature heat transfer medium, the invention is not limited to this. For example, a solution containing dimethylpolysiloxane or nanofluids, antifreeze, an aqueous liquid refrigerant containing alcohol, or a liquid medium containing oil may be used.

[0226] The operating modes of the refrigeration cycle device are not limited to those disclosed in the embodiments described above.

[0227] In the first to sixth and eighth embodiments described above, examples were given in which the rotation speed of the turbo fan 35 was determined so that the adsorbent inside the fluidized bed space 31a of the adsorbents 13 and 131 becomes a fluidized bed, but the invention is not limited to this. For example, a flow control valve may be placed in the refrigerant circulation passage 34, and the circulation flow rate may be adjusted by the flow control valve. That is, the operation of the flow control valve should be controlled so that the adsorbent inside the fluidized bed space 31a of the adsorbents 13 and 131 becomes a fluidized bed.

[0228] Similarly, in the seventh embodiment, a flow control valve may be placed in the refrigerant circulation passage 34 to adjust the amount of refrigerant drawn in by the circulating ejector 55. Similarly, in the ninth embodiment, a flow control valve may be placed in the refrigerant circulation passage 74 to adjust the circulation flow rate.

[0229] In the first to sixth and eighth embodiments described above, examples were given in which the rotational speed of the turbofan 35 was determined so that the pressure loss ΔPf approaches the target pressure loss ΔPFO, but the invention is not limited to these examples. For example, the rotational speed of the turbofan 35 may be determined based on the rotational speed of the compressor 11. For example, in the seventh embodiment, the throttle opening of the circulating expansion valve 54 may be adjusted based on the rotational speed of the compressor 11. For example, in the ninth embodiment, the rotational speed of the turbofan 75 may be determined based on the rotational speed of the compressor 11.

[0230] Furthermore, although the above-described embodiment uses an adsorbent level sensor 41a as the mass detection unit, the invention is not limited to this. For example, a weight sensor that directly detects the weight of the adsorbent that is in a fluidized bed state inside 31a may be used.

[0231] The means disclosed in each of the above embodiments may be combined as appropriate to the extent that they are feasible.

[0232] For example, the device may include both the adsorbent 13 described in the first embodiment and the detacher 151 described in the ninth embodiment. Alternatively, it may include both the adsorbent 131 described in the fourth embodiment and the detacher 151 described in the ninth embodiment.

[0233] Furthermore, the adsorbent 13 described in the second embodiment may be applied to the refrigeration cycle devices 10 and 10a described in the third and eighth embodiments. Also, the adsorbent 131 described in the fifth and sixth embodiments and the refrigeration cycle device 10c described in the seventh embodiment may be applied.

[0234] Furthermore, the circulating heat exchanger 62 and the auxiliary heat transfer medium circuit 60 described in the eighth embodiment may also be applied to the refrigeration cycle devices 10a to 10c and 10e described in the second to seventh and ninth embodiments.

[0235] When applied to the second to seventh embodiments, the refrigerant passage of the circulating heat exchanger 62 may be positioned either upstream or downstream of the turbo fan 35 or the circulating ejector 55. Preferably, it is desirable to position it downstream of the turbo fan 35 or the circulating ejector 55. This is because, downstream of the turbo fan 35 or the circulating ejector 55, the refrigerant is pressurized and its density increases, thus improving the heat transfer performance of the gaseous refrigerant.

[0236] Furthermore, by applying the circulating heat exchanger 62 and the auxiliary heat transfer medium circuit 60 to the refrigeration cycle device 10e of the ninth embodiment, the refrigerant flowing into the duct space 71b can be heated. This promotes the desorption of the refrigerant in the fluidized bed space 71a, thereby accelerating the cooling of the low-temperature side heat transfer medium.

[0237] Furthermore, instead of the turbo fan 75, the circulation side ejector 55 described in the seventh embodiment may be used as the circulation supply unit of the refrigeration cycle device 10e described in the ninth embodiment. Also, the adsorbent medium described in the first embodiment may be mixed into the refrigerant of the refrigeration cycle devices 10a to 10e described in the second to ninth embodiments.

[0238] The features of the refrigeration cycle apparatus disclosed herein are as follows: (Item 1) A refrigeration cycle apparatus for circulating a mixed refrigerant obtained by mixing a refrigerant and an adsorbent, comprising: a compression unit (11) for compressing and discharging the refrigerant; adsorption units (13, 131, 132) for adsorbing the refrigerant discharged from the compression unit onto the adsorbent; and desorption units (15, 151) for desorbing the refrigerant drawn from the adsorbent into the compression unit, wherein at least one of the adsorption unit and the desorption unit has a circulation supply unit (34, 34a, 35, 55, 74, 74a, 75) for circulating and supplying the refrigerant, and the circulation supply unit circulates and supplies the refrigerant so as to create a fluidized bed within the adsorbent unit or the desorption unit. (Item 2) The refrigeration cycle apparatus according to Item 1, wherein the circulation supply unit has a circulation blower unit (35, 75) for pressurizing the refrigerant. (Item 3) The refrigeration cycle apparatus according to item 1 or 2, comprising: a low-pressure side extraction unit (16) that extracts the refrigerant from the mixed refrigerant discharged from the detachment unit and discharges it to the suction side of the compression unit; and an adsorbent transport unit (12) that transports the mixed refrigerant discharged from the low-pressure side extraction unit, wherein the refrigerant discharged from the compression unit is guided above the adsorbent which is in a fluidized bed inside the adsorbent unit, and the adsorbent transported by the adsorbent transport unit is guided above the adsorbent which is in a fluidized bed inside the adsorbent unit. (Item 4) The refrigeration cycle apparatus according to item 1 or 2, comprising: a low-pressure side extraction unit (16) that extracts the refrigerant from the mixed refrigerant discharged from the detachment unit and discharges it to the suction side of the compression unit; and an adsorbent transport unit (12) that transports the mixed refrigerant discharged from the low-pressure side extraction unit, wherein the refrigerant discharged from the compression unit is guided below the adsorbent which is in a fluidized bed inside the adsorbent unit, and the adsorbent transported by the adsorbent transport unit is guided above the adsorbent which is in a fluidized bed inside the adsorbent unit.(Item 5) The refrigeration cycle apparatus according to Item 1 or 2, comprising: a low-pressure side extraction unit (16) that extracts the refrigerant from the mixed refrigerant flowing out from the detachment unit and flows it out to the suction side of the compression unit; and a discharge side ejector (51) having a discharge side nozzle unit (51a) that reduces the pressure of the discharged refrigerant discharged from the compression unit, and a discharge side body unit (51b) formed thereon that sucks in the mixed refrigerant flowing out from the low-pressure side extraction unit, wherein the mixed refrigerant flowing out from the discharge side ejector flows into the adsorption unit. (Item 6) The refrigeration cycle apparatus according to Item 5, wherein the mixed refrigerant flowing out from the discharge side ejector is guided to the side above the adsorbent which is in a fluidized bed inside the adsorption unit. (Item 7) The refrigeration cycle apparatus according to Item 5, comprising a branching section (53) for branching the flow of the discharged refrigerant, which causes one of the discharged refrigerants branched at the branching section to flow into the discharge-side nozzle section, and the circulation supply section having a circulation-side ejector (55) which has a circulation-side nozzle section (55a) for reducing the pressure of one of the discharged refrigerants branched at the branching section, and a circulation-side body section (55b) formed with a circulation-side suction port (55c) for sucking the refrigerant that has flowed out from one of the adsorption section and the desorption section. (Item 8) The refrigeration cycle apparatus according to any one of Items 1 to 7, comprising a heat exchange section (62) for exchanging heat between the refrigerant circulated and supplied by the circulation supply section and an object to be heat exchanged. (Item 9) The refrigeration cycle apparatus according to any one of Items 1 to 8, comprising an adsorbent intrusion suppression section (34a, 74a) for suppressing the intrusion of the adsorbent into the circulation supply section. (Item 10) The refrigerant contains a non-adsorbent medium that is not adsorbed by the adsorbent, and the circulation supply unit circulates and supplies the refrigerant and the non-adsorbent medium, according to any one of items 1 to 9.(Item 11) A refrigeration cycle apparatus according to any one of items 1 to 10, comprising: a mass detection unit (41a) for detecting the mass (Mf) of the adsorbent that is fluidized inside the adsorption unit or the desorption unit; an inlet pressure detection unit (41b) for detecting the inlet pressure (Pfin) of the refrigerant supplied to the adsorbent that is fluidized inside the adsorption unit or the desorption unit; and an outlet pressure detection unit (41c) for detecting the outlet pressure (Pfout) of the refrigerant that has flowed out from the adsorbent that is fluidized inside the adsorption unit or the desorption unit, wherein the circulation supply unit increases the pressure loss (ΔPf) obtained by subtracting the outlet pressure (Pfout) from the inlet pressure (Pfin) as the mass (Mf) increases.

[0239] This disclosure is described in accordance with the embodiments, but it is understood that this disclosure is not limited to such embodiments or structures. This disclosure also includes various modifications and variations within the equivalence. In addition, various combinations and forms, as well as other combinations and forms that include only one, more, or fewer of those elements, fall within the scope and concept of this disclosure.

Claims

1. A refrigeration cycle device for circulating a mixed refrigerant obtained by mixing a refrigerant and an adsorbent, comprising: a compression unit (11) for compressing and discharging the refrigerant; adsorption units (13, 131, 132) for adsorbing the refrigerant discharged from the compression unit onto the adsorbent; and desorption units (15, 151) for desorbing the refrigerant that is drawn from the adsorbent into the compression unit, wherein at least one of the adsorption unit and the desorption unit has a circulation supply unit (34, 34a, 35, 55, 74, 74a, 75) for circulating and supplying the refrigerant, and the circulation supply unit circulates and supplies the refrigerant so as to create a fluidized bed within the adsorbent unit or the desorption unit.

2. The refrigeration cycle apparatus according to claim 1, wherein the circulation supply unit has a circulation blower unit (35, 75) for pressurizing and supplying the refrigerant.

3. The refrigeration cycle apparatus according to claim 1, comprising: a low-pressure side extraction unit (16) that extracts the refrigerant from the mixed refrigerant discharged from the detachment unit and discharges it to the suction side of the compression unit; and an adsorbent transport unit (12) that transports the mixed refrigerant discharged from the low-pressure side extraction unit, wherein the refrigerant discharged from the compression unit is guided above the adsorbent which is in a fluidized bed inside the adsorbent unit, and the adsorbent transported by the adsorbent transport unit is guided above the adsorbent which is in a fluidized bed inside the adsorbent unit.

4. The refrigeration cycle apparatus according to claim 1, comprising: a low-pressure side extraction unit (16) that extracts the refrigerant from the mixed refrigerant discharged from the detachment unit and discharges it to the suction side of the compression unit; and an adsorbent transport unit (12) that transports the mixed refrigerant discharged from the low-pressure side extraction unit, wherein the refrigerant discharged from the compression unit is guided below the adsorbent which is in a fluidized bed inside the adsorbent unit, and the adsorbent transported by the adsorbent transport unit is guided above the adsorbent which is in a fluidized bed inside the adsorbent unit.

5. The refrigeration cycle apparatus according to claim 1, comprising: a low-pressure side extraction unit (16) that extracts the refrigerant from the mixed refrigerant flowing out from the detachable unit and flows it out to the suction side of the compression unit; and a discharge side ejector (51) having a discharge side nozzle unit (51a) that reduces the pressure of the discharged refrigerant discharged from the compression unit, and a discharge side body unit (51b) formed with a discharge side suction port (51c) that sucks in the mixed refrigerant flowing out from the low-pressure side extraction unit, wherein the mixed refrigerant flowing out from the discharge side ejector flows into the adsorption unit.

6. The refrigeration cycle apparatus according to claim 5, wherein the mixed refrigerant discharged from the discharge-side ejector is guided above the adsorbent which is in a fluidized bed state inside the adsorption section.

7. The refrigeration cycle apparatus according to claim 5, comprising a branching section (53) for branching the flow of the discharged refrigerant, which causes one of the discharged refrigerants branched at the branching section to flow into the discharge-side nozzle section, and the circulation supply section having a circulation-side nozzle section (55a) for reducing the pressure of one of the discharged refrigerants branched at the branching section, and a circulation-side body section (55b) formed with a circulation-side suction port (55c) for sucking the refrigerant that has flowed out from one side into the adsorption section and the desorption section.

8. The refrigeration cycle apparatus according to claim 1, further comprising a heat exchange unit (62) for exchanging heat between the refrigerant circulated and supplied by the circulation supply unit and an object to be heat exchanged.

9. The refrigeration cycle apparatus according to claim 1, further comprising adsorbent intrusion suppression units (34a, 74a) for suppressing the intrusion of the adsorbent into the circulation supply unit.

10. The refrigeration cycle apparatus according to claim 1, wherein the refrigerant contains a non-adsorbent medium that is not adsorbed by the adsorbent, and the circulation supply unit circulates and supplies the refrigerant and the non-adsorbent medium.

11. The refrigeration cycle apparatus according to claim 1, comprising: a mass detection unit (41a) for detecting the mass (Mf) of the adsorbent that is in a fluidized bed state inside the adsorption unit or the desorption unit; an inlet pressure detection unit (41b) for detecting the inlet pressure (Pfin) of the refrigerant supplied to the adsorbent that is in a fluidized bed state inside the adsorption unit or the desorption unit; and an outlet pressure detection unit (41c) for detecting the outlet pressure (Pfout) of the refrigerant that has flowed out from the adsorbent that is in a fluidized bed state inside the adsorption unit or the desorption unit, wherein the circulation supply unit increases the pressure loss (ΔPf) obtained by subtracting the outlet pressure (Pfout) from the inlet pressure (Pfin) as the mass (Mf) increases.

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