Refrigeration cycle device

Abstract

This refrigeration cycle device that circulates a mixed refrigerant obtained by mixing an adsorbent into a refrigerant comprises: a low-pressure-side extraction unit (16); a compression unit (11); a discharge-side transport unit (12); a heat dissipation unit (13); a mixed refrigerant decompression unit (14, 17); and a heat absorption unit (15, 15a, 15b). The low-pressure-side extraction unit (16) extracts the refrigerant from the mixed refrigerant flowing out from the heat absorption unit (15, 15a, 15b). The compression unit (11) sucks in and compresses a gas-phase refrigerant extracted by the low-pressure-side extraction unit (16). The discharge-side transport unit (12), by using the pressure energy of a discharged refrigerant discharged from the compression unit (11), transports, to the discharge side to which the refrigerant discharged from the compression unit (11) is discharged, the mixed refrigerant flowing out from the low-pressure-side extraction unit (16).

Description

Refrigeration Cycle Equipment CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Japanese Patent Application No. 2024-058847 filed on April 1, 2024, Japanese Patent Application No. 2024-106027 filed on July 1, 2024, and Japanese Patent Application No. 2024-189727 filed on October 29, 2024, the contents of which are incorporated herein by reference.

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

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

[0004] This type of refrigeration cycle device can utilize the heat of adsorption generated when the refrigerant is adsorbed onto the adsorbent and the heat of desorption generated when the refrigerant is desorbed from the adsorbent. As a result, the hybrid refrigeration cycle device can reduce the pressure of the high-pressure side refrigerant and improve the cycle operating efficiency compared to a normal vapor compression refrigeration cycle device that does not mix the refrigerant with an adsorbent.

[0005] Patent Document 1 also describes a method of separating an adsorbent from a low-pressure refrigerant mixture, compressing the refrigerant from which the adsorbent has been separated in a compressor, and pressurizing the adsorbent separated from the refrigerant in a booster. The method then describes a method of mixing the refrigerant discharged from the compressor with the adsorbent pressurized in the booster to produce a high-pressure refrigerant mixture. Patent Document 1 also describes that a powder pump can be used as the booster that pressurizes the adsorbent.

[0006] International Publication No. 2024 / 004971

[0007] However, in a typical powder pump, the flow of powder easily causes wear to the sliding parts and seals. Therefore, the powder pump tends to have a shorter lifespan than other components of a refrigeration cycle device. As a result, in a configuration such as that disclosed in Patent Document 1, in which a powder pump is used as a booster, the reliability of the refrigeration cycle device as a whole is likely to decrease.

[0008] In view of the above, an object of the present disclosure is to provide a highly reliable refrigeration cycle device that circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent.

[0009] A refrigeration cycle device according to a first aspect of the present disclosure circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent that adsorbs and desorbs the refrigerant, and further includes a low-pressure side extraction unit, a compression unit, a discharge-side transport unit, a heat dissipation unit, a mixed refrigerant decompression unit, and a heat absorption unit.

[0010] The low-pressure side extraction section extracts refrigerant from the mixed refrigerant. The compression section sucks in, compresses, and discharges the refrigerant extracted by the low-pressure side extraction section. The discharge side transport section transports the mixed refrigerant flowing out of the low-pressure side extraction section to the discharge refrigerant side using the pressure energy of the discharged refrigerant discharged from the compression section. The heat dissipation section dissipates heat from the mixed refrigerant flowing out of the discharge side transport section. The mixed refrigerant decompression section decompresses the mixed refrigerant flowing out of the heat dissipation section. The heat absorption section desorbs refrigerant from the adsorbent contained in the mixed refrigerant decompressed in the mixed refrigerant decompression section, and causes the mixed refrigerant to flow out of the mixed refrigerant inlet side of the low-pressure side extraction section.

[0011] This results in a so-called hybrid refrigeration cycle device. Therefore, the heat dissipation section can dissipate the heat of adsorption generated when the adsorbent adsorbs the refrigerant. Also, the heat absorption section can absorb the heat of desorption generated when the adsorbent desorbs the refrigerant. Therefore, the operating efficiency of the cycle can be improved compared to a typical vapor compression refrigeration cycle device that does not mix an adsorbent with the refrigerant.

[0012] Furthermore, since the discharge-side transport section transports the mixed refrigerant using the pressure energy of the discharged refrigerant, it is easy to realize a transport section with few sliding parts and sealing parts, which results in improved reliability of the refrigeration cycle device that circulates a mixed refrigerant obtained by mixing the refrigerant with the adsorbent.

[0013] Here, the operating efficiency of a hybrid refrigeration cycle device can be defined as the value obtained by dividing the amount of heat absorbed in the heat absorption section by the power consumption required to raise the pressure of both the refrigerant and the adsorption material from low pressure to high pressure.

[0014] The above and other objects, features, and advantages of the present disclosure will become more apparent from the following detailed description taken in conjunction with the accompanying drawings.

[0023] Fig. 1 is a schematic overall configuration diagram of a refrigeration cycle device of a first embodiment.

[0024] Fig. 2 is an axial cross-sectional view of an ejector of the first embodiment.

[0025] Fig. 3 is a schematic overall configuration diagram of a refrigeration cycle device of a second embodiment.

[0026] Fig. 4 is a schematic overall configuration diagram of a refrigeration cycle device of a third embodiment.

[0027] Fig. 5 is a schematic overall configuration diagram of a refrigeration cycle device of a fourth embodiment.

[0028] Fig. 6 is a schematic axial cross-sectional view of a low-pressure side extraction section of the fourth embodiment.

[0029] Fig. 7 is a schematic overall configuration diagram of a refrigeration cycle device of a fifth embodiment.

[0030] Fig. 8 is an explanatory diagram showing the positional relationship between the low-pressure side extraction section and a discharge-side ejector in a sixth embodiment.

[0031] Fig. 9 is a schematic overall configuration diagram of a refrigeration cycle device of a seventh embodiment.

[0032] Fig. 10 is a schematic cross-sectional view of an adsorbent heat exchanger of the seventh embodiment.

[0033] Fig. 11 is a schematic overall configuration diagram of a refrigeration cycle device of an eighth embodiment.

[0034] Fig. 12 is a schematic overall configuration diagram of a refrigeration cycle device of a ninth embodiment.

[0035] Fig. 13 is an explanatory diagram showing a low-pressure side extraction section and a vibration section in a tenth embodiment.

[0015] Hereinafter, multiple embodiments for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, parts corresponding to matters described in the preceding embodiment will be assigned the same reference numerals, and duplicate descriptions may be omitted. In each embodiment, when only a part of the configuration is described, other previously described embodiments may be applied to the other parts of the configuration. In addition to combinations of parts that are specifically specified as being combinable in each embodiment, it is also possible to partially combine embodiments even if not specified, as long as there is no particular problem with the combination.

[0016] First Embodiment A first embodiment of a refrigeration cycle device according to the present disclosure will be described using Figures 1 and 2. In this embodiment, a refrigeration cycle device 10 shown in the overall configuration diagram of Figure 1 is applied to an air conditioner 1. The air conditioner 1 includes the refrigeration cycle device 10, a control device 20, and the like.

[0017] The refrigeration cycle device 10 constitutes a vapor compression refrigeration cycle that cools the air to be blown into a room, which is a space to be air-conditioned, in the air conditioner 1. The refrigeration cycle device 10 uses carbon dioxide (i.e., R744) as a refrigerant.

[0018] The refrigerant contains an adsorbent. The adsorbent adsorbs the refrigerant under high pressure and desorbs (or desorbs) the refrigerant under low pressure. When adsorbing the refrigerant, the adsorbent releases heat (i.e., internal energy) contained in the adsorbed refrigerant as heat of adsorption, and when desorbing the refrigerant, it absorbs ambient heat as heat of desorption.

[0019] More specifically, in this embodiment, a metal-organic framework (MOF) is used as the adsorbent. MOF is a porous material obtained by reacting metal ions with organic ligands. MOF is a polymer structure that has numerous openings inside by linking metal ions with organic ligands.

[0020] The pore size of MOFs can be optimized by combining metal ions and organic ligands. By adjusting the pore size, MOFs can selectively adsorb the target substance. In this embodiment, a MOF suitable for adsorption of carbon dioxide, a refrigerant, is used. Specifically, MOF-5 or MOF-200 can be used.

[0021] The adsorbent is not dissolved in the refrigerant but is mixed with the refrigerant in a powder or particulate solid state. Furthermore, the amount of adsorbent mixed with the refrigerant in this embodiment is less than the amount that can adsorb all of the refrigerant under normal operating conditions of the refrigeration cycle apparatus 10. Therefore, in the refrigeration cycle apparatus 10, only the adsorbent does not circulate within the cycle.

[0022] In the following description, for the sake of clarity, a refrigerant mixed with an adsorbent will be referred to as a mixed refrigerant, and a refrigerant not mixed with an adsorbent will be referred to as a refrigerant, a discharged refrigerant, a discharge side injected refrigerant, a reduced pressure side injected refrigerant, etc., without using the term "mixed."

[0023] The compressor 11 is a compression unit in the refrigeration cycle apparatus 10 that draws in, compresses, and discharges refrigerant. The compressor 11 is an electric compressor that uses an electric motor to rotate a fixed-displacement compression mechanism with a fixed discharge capacity. The compression mechanism may be a rotary compression mechanism, a scroll compression mechanism, or the like. The rotation speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the control device 20.

[0024] The inlet side of a discharge side nozzle portion 12 a of a discharge side ejector 12 is connected to the discharge port of the compressor 11 .

[0025] The discharge side ejector 12 sucks the mixed refrigerant flowing out from the low-pressure side extraction section 16 (described later) through a discharge side suction port 12c formed in the discharge side body section 12b by the suction action of the discharge side injection refrigerant injected from the discharge side nozzle section 12a. Furthermore, the discharge side ejector 12 converts the velocity energy (i.e., expansion energy) of the mixed refrigerant, in which the adsorbent is mixed with the discharge side injection refrigerant, into pressure energy, thereby increasing the pressure of the mixed refrigerant.

[0026] The detailed configuration of the discharge side ejector 12 will be described with reference to Fig. 2. The discharge side ejector 12 has a discharge side nozzle portion 12a and a discharge side body portion 12b.

[0027] The discharge-side nozzle portion 12a is a nozzle that converts pressure energy of the refrigerant discharged from the compressor 11 into velocity energy and sprays the refrigerant. The discharge-side nozzle portion 12a is formed of a substantially cylindrical metal (stainless steel in this embodiment) member that gradually tapers in the direction of refrigerant flow.

[0028] The discharge-side nozzle 12a isentropically depressurizes the discharged refrigerant and accelerates it to supersonic speed, and then injects the discharge-side injection refrigerant into a discharge-side mixing section 12e formed in the discharge-side body 12b. A so-called Laval nozzle or a convergent nozzle can be used as the discharge-side nozzle 12a.

[0029] The discharge-side body portion 12b supports and fixes the discharge-side nozzle portion 12a and forms the outer shell of the discharge-side ejector 12. The discharge-side body portion 12b is formed of a substantially cylindrical member made of metal (aluminum alloy in this embodiment). The discharge-side nozzle portion 12a is fixed inside one longitudinal end of the discharge-side body portion 12b by means of press-fitting or the like. The discharge-side body portion 12b may be formed of resin.

[0030] The discharge-side body 12b has a cylindrical wall surface formed at a location corresponding to the outer periphery of the discharge-side nozzle 12a. The discharge-side suction port 12c penetrates the discharge-side body 12b from the inside to the outside and communicates with the refrigerant injection port of the discharge-side nozzle 12a. The discharge-side suction port 12c is a through-hole that draws the mixed refrigerant flowing out from the low-pressure extraction section 16 into the discharge-side body 12b by the suction action of the discharge-side injection refrigerant injected from the discharge-side nozzle 12a.

[0031] Furthermore, a discharge-side suction passage 12d, a discharge-side mixing section 12e, and a discharge-side pressurization section 12f are formed inside the discharge-side body section 12b. The discharge-side suction passage 12d is a passage that guides the mixed refrigerant sucked through the discharge-side suction port 12c to the discharge-side mixing section 12e. The discharge-side mixing section 12e is a space for mixing the mixed refrigerant sucked through the discharge-side suction port 12c with the discharge-side spray refrigerant. The discharge-side mixing section 12e is formed in a substantially cylindrical shape.

[0032] The discharge-side pressurization section 12f is a space for pressurizing the mixed refrigerant sucked through the discharge-side suction port 12c and the discharge-side spray refrigerant. The discharge-side pressurization section 12f is formed in a truncated cone shape whose cross-sectional area expands in the direction of the mixed refrigerant flow. In the discharge-side pressurization section 12f, the velocity energy of the mixed refrigerant is converted into pressure energy by the action of shock waves generated by the discharge-side spray refrigerant and the expansion of the passage cross-sectional area.

[0033] Therefore, the discharge side ejector 12 is a discharge side transport unit that transports the mixed refrigerant flowing out from the low-pressure side extraction unit 16 to the discharge refrigerant side by using the pressure energy of the discharge refrigerant discharged from the compressor 11. In other words, the discharge side ejector 12 uses the pressure energy of the discharge refrigerant to mix the mixed refrigerant flowing out from the low-pressure side extraction unit 16 with the discharge side injection refrigerant, which is the discharge refrigerant that has consumed the pressure energy.

[0034] The outlet of the discharge-side pressure boosting section 12f of the discharge-side ejector 12 is connected to the mixed refrigerant inlet side of the heat dissipation heat exchanger 13. The heat dissipation heat exchanger 13 is a heat dissipation section that exchanges heat between the mixed refrigerant flowing out of the discharge-side ejector 12 and outside air blown by an outside air fan (not shown), thereby dissipating heat contained in the mixed refrigerant to the outside air.

[0035] The inlet side of an electric expansion valve 14 is connected to the mixed refrigerant outlet of the heat dissipation heat exchanger 13. The electric expansion valve 14 is a mixed refrigerant decompression unit that decompresses the mixed refrigerant flowing out from the heat dissipation heat exchanger 13. More specifically, the electric expansion valve 14 decompresses the refrigerant contained in the mixed refrigerant, thereby reducing the pressure of the ambient refrigerant in the adsorbent. Furthermore, the electric expansion valve 14 is a flow rate adjustment unit that adjusts the flow rate of the mixed refrigerant flowing into the heat absorption heat exchanger 15.

[0036] Specifically, the electric 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 electric expansion valve 14 is controlled by a control signal output from the control device 20.

[0037] The outlet of the electric expansion valve 14 is connected to the mixed refrigerant inlet side of the heat absorption heat exchanger 15. The heat absorption heat exchanger 15 exchanges heat between the mixed refrigerant decompressed by the electric expansion valve 14 and the blown air blown into the room from a blower (not shown). The heat absorption heat exchanger 15 is a heat absorption unit that cools the blown air by desorbing the refrigerant from an adsorbent contained in the mixed refrigerant to exert a heat absorption effect.

[0038] The mixed refrigerant outlet of the endothermic heat exchanger 15 is connected to the mixed refrigerant inlet 16c side of the low-pressure side extraction section 16. The low-pressure side extraction section 16 extracts a portion of the refrigerant that does not contain adsorbent from the mixed refrigerant that has flowed out of the endothermic heat exchanger 15. In other words, the low-pressure side extraction section 16 can be called a low-pressure side separation section that separates the refrigerant that does not contain adsorbent from the mixed refrigerant.

[0039] The state of the remaining mixed refrigerant after the refrigerant is extracted in the low-pressure side extraction section 16 is affected by the pressure of the mixed refrigerant flowing out from the endothermic heat exchanger 15, the ambient temperature at the location where the low-pressure side extraction section 16 is located, the type of refrigerant, the amount of refrigerant charged, etc.

[0040] That is, the remaining mixed refrigerant after a portion of the refrigerant has been extracted in the low-pressure side extraction section 16 can be a mixed refrigerant in which the adsorbent is mixed with a gas-phase refrigerant, a mixed refrigerant in which the adsorbent is mixed with a two-phase gas-liquid refrigerant, or a mixed refrigerant in which the adsorbent is mixed with a liquid-phase refrigerant.

[0041] The low-pressure side extraction section 16 is formed by a cylindrical metal container with a bottom that defines an internal space. The low-pressure side extraction section 16 is arranged so that its axial direction is vertical. A flat adsorbent filter 161 is arranged in the internal space of the low-pressure side extraction section 16.

[0042] The adsorbent filter 161 vertically divides the internal space of the low-pressure side extraction section 16 into an upper space 16b and a lower space 16a. The adsorbent filter 161 is an adsorbent filtering section having selective permeability that allows the low-pressure side gas phase refrigerant separated from the mixed refrigerant to pass through, while prohibiting at least the adsorbent from passing through.

[0043] The lower space 16a is connected to a mixed refrigerant inlet 16c and a mixed refrigerant outlet 16d of the low-pressure side extraction section 16. The lower space 16a is configured to extract the refrigerant from the mixed refrigerant by utilizing the difference in specific gravity between the refrigerant and the adsorbent.

[0044] The volume of the lower space 16a is set so that, when the remaining mixed refrigerant becomes a mixed refrigerant in which the adsorbent is mixed with the liquid-phase refrigerant, the lower space 16a can be used as a liquid storage section to store excess refrigerant in the cycle as saturated liquid-phase refrigerant. As a result, in the low-pressure side extraction section 16, gas-phase refrigerant is extracted into the upper space 16b.

[0045] The mixed refrigerant outlet 16d is an outlet for discharging the mixed refrigerant stored in the lower space 16a, i.e., the remaining mixed refrigerant after the gas phase refrigerant has been extracted. The mixed refrigerant outlet 16d is formed on the bottom surface of the low-pressure side extraction section 16. The discharge-side suction port 12c side of the discharge-side ejector 12 is connected to the mixed refrigerant outlet 16d. A refrigerant passage connecting the mixed refrigerant outlet 16d and the discharge-side suction port 12c is a mixed refrigerant passage 23.

[0046] The upper space 16b is connected to a gas phase refrigerant outlet 16e of the low-pressure side extraction section 16. The gas phase refrigerant outlet 16e is an outlet through which the low-pressure side gas phase refrigerant that has passed through the adsorbent filter 161 flows out. The gas phase refrigerant outlet 16e is formed on the top surface of the low-pressure side extraction section 16. The low-pressure side extraction section 16 is connected to the suction port side of the compressor 11.

[0047] Next, the electrical control unit of the air conditioner 1 of this embodiment will be described. The control device 20 has a well-known microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuits. The control device 20 performs various calculations and processes based on control programs stored in the ROM. The control device 20 then controls the operation of various control target devices connected to the output side based on the results of the calculations and processes.

[0048] A group of various control sensors is connected to the input side of the control device 20. The group of control sensors includes an inside air temperature sensor, an outside air temperature sensor, a high-pressure pressure sensor, a high-pressure temperature sensor, an evaporator pressure sensor, an evaporator temperature sensor, and the like (not shown).

[0049] The inside air temperature sensor is an inside air temperature detector that detects the indoor air temperature (i.e., the inside air temperature) Tr. The outside air temperature sensor is an outside air temperature detector that detects the outside air temperature (i.e., the outside air temperature) Tam.

[0050] The high-pressure pressure sensor is a high-pressure pressure detection unit that detects a high-pressure pressure Pd, which is the pressure of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13. The high-pressure temperature sensor is a high-pressure temperature detection unit that detects a high-pressure temperature Td, which is the temperature of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13.

[0051] The evaporator pressure sensor is an evaporator pressure detection unit that detects the evaporator pressure Pe, which is the pressure of the mixed refrigerant flowing out from the heat absorption heat exchanger 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 heat absorption heat exchanger 15.

[0052] An operation panel (not shown) is connected by wire or wirelessly to the input side of the control device 20. Operation signals are input to the control device 20 from various operation switches provided on the operation panel. The various operation switches provided on the operation panel include an activation switch, a temperature setting switch, an air volume setting switch, etc.

[0053] The control device 20 is an integrated unit that controls various control target devices connected to the output side. Therefore, the components (hardware and software) that control the operation of each control target device constitute the control unit that controls the operation of each control target device. For example, the component of the control device 20 that controls the refrigerant discharge capacity of the compressor 11 constitutes the discharge capacity control unit.

[0054] Next, we will explain the operation of the air conditioner 1 configured as described above. When the operation switch of the air conditioner 1 is turned on (i.e., ON), the control device 20 executes a control program. The control program reads detection signals from the above-mentioned control sensors and operation signals from the operation panel.

[0055] The operation of the various controlled devices is then controlled based on the detection signals and operation signals that have been read in. Thereafter, the control routine of reading the detection signals and operation signals and controlling the various controlled devices based on the detection signals and operation signals is repeated at each predetermined control period until the termination condition of the control program is met.

[0056] More specifically, the control program of this embodiment controls the refrigerant discharge capacity 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 inside air temperature Tr detected by the inside air temperature sensor, the outside air temperature Tam detected by the outside air temperature sensor, the set temperature Tset set by the temperature setting switch, etc.

[0057] The control program also controls the throttle opening of the electric expansion valve 14 so that the high-pressure pressure Pd detected by the high-pressure 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 operating efficiency of the cycle approaches its maximum value.

[0058] In the refrigeration cycle device 10, when the control device 20 operates the compressor 11, the compressor 11 sucks in the low-pressure side gas phase refrigerant that flows out from the gas phase refrigerant outlet 16e of the low-pressure side extraction section 16, compresses it, and discharges it.

[0059] The refrigerant discharged from the compressor 11 flows into the discharge nozzle 12a of the discharge ejector 12. The refrigerant flowing into the discharge nozzle 12a is isentropically decompressed and injected into the discharge mixing section 12e of the discharge body 12b. The mixed refrigerant flowing out from the mixed refrigerant outlet 16d of the low-pressure extraction section 16 is then sucked into the discharge suction port 12c by the suction action of the discharge-side injected refrigerant injected from the discharge nozzle 12a.

[0060] The mixed refrigerant sucked through the discharge-side suction port 12c flows into the discharge-side mixing section 12e via the discharge-side suction passage 12d. At this time, if the mixed refrigerant sucked through the discharge-side suction port 12c contains liquid-phase refrigerant, the liquid-phase refrigerant absorbs heat from the discharge-side injected refrigerant and evaporates in the discharge-side mixing section 12e. As a result, the mixed refrigerant in the discharge-side mixing section 12e becomes a mixed refrigerant in which the adsorbent is mixed with the gas-phase refrigerant, and flows into the discharge-side pressurization section 12f.

[0061] In the discharge-side pressurization section 12f, the velocity energy of the mixed refrigerant is converted into pressure energy by the action of the shock waves generated by the discharge-side injected refrigerant and the expansion of the passage cross-sectional area. This increases the pressure of the mixed refrigerant. As the pressure of the mixed refrigerant increases in the discharge-side pressurization section 12f, the amount of adsorption by the adsorbent increases, and the volume of the mixed refrigerant decreases.

[0062] The mixed refrigerant flowing out from the discharge side pressure increasing section 12f flows into the heat dissipation heat exchanger 13. The mixed refrigerant flowing into the heat dissipation heat exchanger 13 dissipates the internal energy stored when the adsorbent adsorbed the gas phase refrigerant to the outside air as heat of adsorption.

[0063] The mixed refrigerant flowing out of the heat-rejection heat exchanger 13 flows into the electric expansion valve 14 and is decompressed. The mixed refrigerant decompressed by the electric expansion valve 14 flows into the heat-absorbing heat exchanger 15. In the mixed refrigerant flowing into the heat-absorbing heat exchanger 15, the refrigerant is desorbed from the adsorbent as the pressure drops. At this time, the adsorbent absorbs the heat of the blown air as desorption heat. Furthermore, if the mixed refrigerant contains liquid-phase refrigerant, the liquid-phase refrigerant evaporates and exhibits an endothermic effect, thereby cooling the blown air.

[0064] The mixed refrigerant flowing out of the endothermic heat exchanger 15 flows into the lower space 16a of the low-pressure side extraction section 16. A portion of the refrigerant contained in the mixed refrigerant flowing into the lower space 16a flows into the upper space 16b via the adsorbent filter 161.

[0065] The low-pressure gas phase refrigerant flowing out from the upper space 16b is drawn into the compressor 11 and compressed again. The mixed refrigerant flowing out from the lower space 16a is drawn through the discharge side suction port 12c of the discharge side ejector 12.

[0066] As described above, the air conditioner 1 of this embodiment can cool the room by blowing the blown air that has been cooled when passing through the heat-absorbing heat exchanger 15 into the room.

[0067] Furthermore, the refrigeration cycle apparatus 10 of this embodiment is a hybrid refrigeration cycle apparatus that circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent. Therefore, the heat dissipation heat exchanger 13 can dissipate the heat of adsorption generated when the adsorbent adsorbs the refrigerant to the outside air. Furthermore, the heat absorption heat exchanger 15 can absorb the heat of desorption generated when the adsorbent desorbs the refrigerant from the blown air.

[0068] Therefore, according to the refrigeration cycle apparatus 10 of this embodiment, the pressure of the mixed refrigerant in the heat dissipation heat exchanger 13 and the pressure of the discharged refrigerant can be reduced more than in a normal vapor compression refrigeration cycle apparatus in which the refrigerant is not mixed with an adsorbent, thereby improving the operating efficiency of the cycle.

[0069] In a refrigeration cycle system that circulates a mixed refrigerant, if the adsorbent is drawn into the compressor together with the refrigerant, this may adversely affect the compressor's service life. In contrast, the refrigeration cycle system 10 of this embodiment is equipped with the low-pressure side extraction section 16, which prevents the compressor 11 from drawing in the adsorbent.

[0070] Furthermore, the refrigeration cycle apparatus 10 of this embodiment is equipped with a discharge-side transport section. The discharge-side transport section transports the mixed refrigerant to the discharge refrigerant side using pressure energy of the discharged refrigerant, thereby realizing a transport section with few sliding parts and sealing parts. As a result, the refrigeration cycle apparatus 10 of this embodiment can improve the reliability of the refrigeration cycle apparatus that circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent.

[0071] In addition, the refrigeration cycle apparatus 10 of this embodiment specifically employs a discharge-side ejector 12 as the discharge-side transport section. This allows the adsorbent to be pressurized and transported with less power consumption than a booster configured with a powder pump or the like. Furthermore, the discharge-side ejector 12 allows the refrigerant and mixed refrigerant to be mixed with a small and simple configuration.

[0072] In the refrigeration cycle device 10 of this embodiment, the amount of adsorbent mixed with the refrigerant is less than the amount required to adsorb all of the refrigerant. Therefore, only the adsorbent that has adsorbed the refrigerant does not circulate within the cycle. Therefore, even if a powdered or granular adsorbent is used, it is easy to prevent the adsorbent from remaining in a specific location within the cycle.

[0073] Second Embodiment In this embodiment, an example will be described in which a refrigeration cycle apparatus 10a according to the present disclosure is applied to an air conditioner 1a. As shown in the overall configuration diagram of FIG. 3 , the refrigeration cycle apparatus 10a includes a high-pressure side extraction unit 26, a pressure-reducing side ejector 22, and a fixed throttle 17 in addition to the refrigeration cycle apparatus 10 described in the first embodiment.

[0074] In the refrigeration cycle apparatus 10a, the mixed refrigerant inlet 26c side of the high-pressure side extraction unit 26 is connected to the refrigerant outlet of the heat dissipation heat exchanger 13. The high-pressure side extraction unit 26 extracts a portion of the refrigerant that does not contain adsorbent from the mixed refrigerant that has flowed out from the heat dissipation heat exchanger 13. In other words, the high-pressure side extraction unit 26 can be called a high-pressure side separation unit that separates the refrigerant that does not contain adsorbent from the mixed refrigerant.

[0075] In this embodiment, the state of the refrigerant extracted by the high-pressure side extraction unit 26 is affected by the pressure of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13, the ambient temperature at the location where the high-pressure side extraction unit 26 is located, the type of refrigerant, the amount of refrigerant charged, etc. In other words, the refrigerant extracted by the high-pressure side extraction unit 26 can be a supercritical refrigerant, a gas-phase refrigerant, a gas-liquid two-phase refrigerant, or a liquid-phase refrigerant.

[0076] The state of the remaining mixed refrigerant after the refrigerant is extracted in the high-pressure side extraction section 26 is affected by the pressure of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13, the ambient temperature at the location where the high-pressure side extraction section 26 is located, the type of refrigerant, the amount of refrigerant charged, etc.

[0077] That is, the remaining mixed refrigerant after the refrigerant is extracted in the high-pressure side extraction section 26 can be a mixed refrigerant in which the adsorbent is mixed with a refrigerant in a supercritical state, a mixed refrigerant in which the adsorbent is mixed with a gas-phase refrigerant, a mixed refrigerant in which the adsorbent is mixed with a two-phase gas-liquid refrigerant, or a mixed refrigerant in which the adsorbent is mixed with a liquid-phase refrigerant.

[0078] The high-pressure side extraction section 26 has a basic configuration similar to that of the low-pressure side extraction section 16. Therefore, the internal space of the high-pressure side extraction section 26 is divided into an upper space 26b and a lower space 26a by a filter 261. The lower space 26a is connected to a mixed refrigerant inlet 26c and a mixed refrigerant outlet 26d of the high-pressure side extraction section 26. The upper space 26b is connected to a refrigerant outlet 26e of the high-pressure side extraction section 26.

[0079] The inlet side of the electric expansion valve 14a is connected to the refrigerant outlet 26e of the high-pressure side extraction section 26. The basic configuration of the electric expansion valve 14a is similar to that of the electric expansion valve 14 described in the first embodiment. The outlet of the electric expansion valve 14a is connected to the inlet side of the pressure reduction side nozzle portion 22a of the pressure reduction side ejector 22.

[0080] The inlet side of the fixed throttle 17 is connected to the mixed refrigerant outlet 26d of the high-pressure side extraction section 26. The fixed throttle 17 is a mixed refrigerant decompression section that decompresses the mixed refrigerant that flows out from the mixed refrigerant outlet 26d of the high-pressure side extraction section 26. More specifically, the fixed throttle 17 decompresses the refrigerant contained in the mixed refrigerant, thereby reducing the pressure of the ambient refrigerant around the adsorbent.

[0081] Furthermore, the fixed throttle 17 is a flow rate adjusting unit that adjusts the flow rate of the mixed refrigerant sucked into the decompression-side suction port 22c of the decompression-side ejector 22. More specifically, an orifice, a capillary tube, or the like can be used as the fixed throttle 17. The outlet of the fixed throttle 17 is connected to the decompression-side suction port 22c side of the decompression-side ejector 22.

[0082] The pressure reduction side ejector 22 sucks the mixed refrigerant decompressed by the fixed throttle 17 through a pressure reduction side suction port 22c formed in the pressure reduction side body portion 22b by the suction action of the pressure reduction side injection refrigerant injected from the pressure reduction side nozzle portion 22a. Furthermore, the pressure reduction side ejector 22 converts the velocity energy of the mixed refrigerant, in which the adsorbent is mixed with the pressure reduction side injection refrigerant, into pressure energy, thereby increasing the pressure of the mixed refrigerant.

[0083] The basic configuration of the pressure reduction side ejector 22 is the same as that of the discharge side ejector 12. Therefore, as shown in Fig. 3, the pressure reduction side ejector 22 has a pressure reduction side nozzle portion 22a and a pressure reduction side body portion 22b. The pressure reduction side body portion 22b is formed with a pressure reduction side suction port 22c, a pressure reduction side mixing portion 22e, a pressure reduction side pressure increasing portion 22f, etc.

[0084] The pressure-boosting performance of the pressure-reducing side pressure-boosting section 22f of the present embodiment is set lower than the pressure-boosting performance of the discharge-side pressure-boosting section 12f of the discharge-side ejector 12. The outlet of the pressure-reducing side pressure-boosting section 22f of the pressure-reducing side ejector 22 is connected to the refrigerant inlet side of the heat-absorbing heat exchanger 15.

[0085] Therefore, the pressure reduction side ejector 22 is a pressure reduction side transport unit that uses the pressure energy of the refrigerant extracted by the high-pressure side extraction unit 26 to transport the mixed refrigerant flowing out from the high-pressure side extraction unit 26 to the refrigerant extracted by the high-pressure side extraction unit 26. In other words, the pressure reduction side ejector 22 uses the pressure energy of the refrigerant extracted by the high-pressure side extraction unit 26 to mix the mixed refrigerant flowing out from the high-pressure side extraction unit 26 with the pressure reduction side injection refrigerant, which is the refrigerant extracted by the high-pressure side extraction unit 26 that has consumed the pressure energy.

[0086] Other configurations of the refrigeration cycle device 10a and the air conditioner 1a are similar to those of the refrigeration cycle device 10 and the air conditioner 1 described in the first embodiment.

[0087] Next, the operation of the air conditioner 1a having the above-described configuration will be described. The basic operation of the refrigeration cycle device 10a of this embodiment is the same as that of the first embodiment.

[0088] In the refrigeration cycle apparatus 10a, the mixed refrigerant flowing out from the heat dissipation heat exchanger 13 flows into the lower space 26a of the high-pressure side extraction section 26. A portion of the refrigerant contained in the mixed refrigerant flowing into the lower space 26a flows into the upper space 26b via the filter 261.

[0089] The refrigerant flowing out from the upper space 26b passes through the electric expansion valve 14a and flows into the pressure reduction side nozzle portion 22a of the pressure reduction side ejector 22. The refrigerant flowing into the pressure reduction side nozzle portion 22a is isentropically decompressed and injected into the pressure reduction side mixing portion 22e of the pressure reduction side body portion 22b.

[0090] Then, due to the suction action of the decompression-side injected refrigerant injected from the decompression-side nozzle portion 22a, the mixed refrigerant decompressed by the fixed throttle 17 is sucked from the decompression-side suction port 22c of the decompression-side body portion 22b.

[0091] The mixed refrigerant sucked through the reduced pressure side suction port 22c flows into the reduced pressure side mixing section 22e, where the reduced pressure side refrigerant sprayed from the reduced pressure side nozzle section 22a and the mixed refrigerant sucked through the reduced pressure side suction port 22c are mixed.

[0092] The mixed refrigerant mixed in the pressure reduction side mixing section 22e flows out from the pressure reduction side pressure increasing section 22f and into the heat absorption heat exchanger 15. In the heat absorption heat exchanger 15, the blown air is cooled, as in the first embodiment. Other operations are the same as in the first embodiment.

[0093] As described above, the air conditioner 1a of this embodiment can cool the room by blowing the blown air that has been cooled when passing through the heat-absorbing heat exchanger 15 into the room.

[0094] Furthermore, the refrigeration cycle apparatus 10a of this embodiment can achieve the same effects as those of the first embodiment. That is, the refrigeration cycle apparatus 10a of this embodiment can improve the cycle operating efficiency compared to a typical vapor compression refrigeration cycle apparatus in which an adsorbent is not mixed with a refrigerant. Furthermore, the reliability of a refrigeration cycle apparatus that circulates a mixed refrigerant in which an adsorbent is mixed with a refrigerant can be improved.

[0095] The refrigeration cycle apparatus 10a of this embodiment is also provided with a high-pressure side extraction section 26. This prevents the adsorbent from flowing into the electric expansion valve 14a. This protects the electric expansion valve 14a, further improving the reliability of the refrigeration cycle apparatus. This also improves the accuracy of adjusting the pressure reduction amount and the flow rate in the electric expansion valve 14a.

[0096] The refrigeration cycle apparatus 10a of this embodiment also includes a pressure-reducing side transport section. The pressure-reducing side transport section uses the pressure energy of the refrigerant extracted by the high-pressure side extraction section 26 to transport the mixed refrigerant to the refrigerant extracted by the high-pressure side extraction section 26. Therefore, similar to the discharge-side transport section, a transport section with fewer sliding parts and sealing parts can be realized, further improving the reliability of the refrigeration cycle apparatus.

[0097] Furthermore, in the refrigeration cycle apparatus 10a of this embodiment, the pressure reduction side ejector 22 is employed as the pressure reduction side transport section, so that the refrigerant and the mixed refrigerant can be mixed with a small and simple configuration.

[0098] Third Embodiment In this embodiment, a refrigeration cycle apparatus 10b according to the present disclosure is applied to an air conditioner 1b. The refrigeration cycle apparatus 10b includes a second heat absorption heat exchanger 15b in addition to the refrigeration cycle apparatus 10a described in the second embodiment. In this embodiment, for clarity, the heat absorption heat exchanger 15 described in the first embodiment will be referred to as a first heat absorption heat exchanger 15a.

[0099] The second heat absorption heat exchanger 15b exchanges heat between the mixed refrigerant decompressed by the fixed throttle 17, which is a mixed refrigerant pressure reducing section, and the blown air that has passed through the first heat absorption heat exchanger 15a. The second heat absorption heat exchanger 15b is a heat absorption section that cools the blown air by desorbing the refrigerant from the adsorbent contained in the mixed refrigerant to exert a heat absorption effect.

[0100] The second heat absorption heat exchanger 15b has a basic configuration similar to that of the first heat absorption heat exchanger 15a. In this embodiment, the mixed refrigerant inlet of the second heat absorption heat exchanger 15b is connected to the outlet of the fixed throttle 17. The mixed refrigerant outlet of the second heat absorption heat exchanger 15b is connected to the pressure reduction suction port 22c of the pressure reduction ejector 22.

[0101] In the pressure reduction side ejector 22 of this embodiment, the dimensional specifications of the pressure reduction side pressure boosting section 22 f are set so as to achieve appropriate pressure boosting performance. The rest of the configuration of the refrigeration cycle apparatus 10 b and the air conditioner 1 b is the same as that of the refrigeration cycle apparatus 10 a and the air conditioner 1 a described in the second embodiment.

[0102] Next, the operation of the air conditioner 1b having the above-described configuration will be described. The basic operation of the refrigeration cycle apparatus 10b of this embodiment is the same as that of the second embodiment.

[0103] In the refrigeration cycle apparatus 10b, the refrigerant flowing out from the upper space 26b of the high-pressure side extraction section 26 flows through the electric expansion valve 14a into the pressure reduction side nozzle section 22a of the pressure reduction side ejector 22. The refrigerant flowing into the pressure reduction side nozzle section 22a is isentropically decompressed and injected into the pressure reduction side mixing section 22e of the pressure reduction side body section 22b.

[0104] Then, due to the suction action of the reduced pressure side injected refrigerant sprayed from the reduced pressure side nozzle portion 22a, the mixed refrigerant flowing out from the second heat absorption heat exchanger 15b is sucked from the reduced pressure side suction port 22c of the reduced pressure side body portion 22b.

[0105] In the pressure reduction side mixing section 22e, the pressure reduction side refrigerant injected from the pressure reduction side nozzle section 22a and the mixed refrigerant sucked from the pressure reduction side suction port 22c are mixed. The mixed refrigerant mixed in the pressure reduction side mixing section 22e flows into the pressure reduction side pressurization section 22f. In the pressure reduction side pressurization section 22f, the velocity energy of the mixed refrigerant is converted into pressure energy by the action of shock waves generated by the pressure reduction side injected refrigerant and the expansion of the passage cross-sectional area. This increases the pressure of the mixed refrigerant.

[0106] The mixed refrigerant flowing out from the pressure reduction side pressure boosting section 22f flows into the first heat absorption heat exchanger 15a. In the mixed refrigerant flowing into the first heat absorption heat exchanger 15a, the refrigerant is desorbed from the adsorbent depending on the pressure. At this time, the adsorbent absorbs heat from the blown air as desorption heat. Furthermore, if the mixed refrigerant contains liquid-phase refrigerant, the liquid-phase refrigerant evaporates and exhibits a heat absorption effect, thereby cooling the blown air blown from the blower.

[0107] The mixed refrigerant that flows out from the lower space 26a of the high-pressure side extraction section 26 flows into the fixed throttle 17. The mixed refrigerant that has been depressurized by the fixed throttle 17 flows into the second heat absorption heat exchanger 15b. In the mixed refrigerant that has flowed into the second heat absorption heat exchanger 15b, the refrigerant is desorbed from the adsorbent due to the pressure drop.

[0108] In this case, the adsorbent absorbs heat from the blown air that has passed through the first heat absorption heat exchanger 15a as heat of desorption. Furthermore, if the mixed refrigerant contains a liquid-phase refrigerant, the liquid-phase refrigerant evaporates and exhibits a heat absorption effect, thereby cooling the blown air that has passed through the first heat absorption heat exchanger 15a. Other operations are the same as those in the second embodiment.

[0109] As described above, the air conditioning device 1b of this embodiment can cool the room by blowing the ventilation air cooled in the first heat absorption heat exchanger 15a and the second heat absorption heat exchanger 15b into the room.

[0110] Furthermore, the refrigeration cycle apparatus 10b of this embodiment can achieve the same effects as those of the first and second embodiments. That is, the refrigeration cycle apparatus 10b of this embodiment can improve the cycle operating efficiency compared to a typical vapor compression refrigeration cycle apparatus in which the refrigerant is not mixed with an adsorbent. Furthermore, the reliability of a refrigeration cycle apparatus that circulates a mixed refrigerant in which the refrigerant is mixed with an adsorbent can be improved.

[0111] In the refrigeration cycle apparatus 10b of this embodiment, the mixed refrigerant outlet of the second heat absorption heat exchanger 15b is connected to the decompression-side suction port 22c of the decompression-side ejector 22. As a result, the pressure of the mixed refrigerant in the second heat absorption heat exchanger 15b becomes lower than the pressure of the mixed refrigerant in the first heat absorption heat exchanger 15a due to the pressure increase action of the decompression-side ejector 22.

[0112] Therefore, the amount of cooling of the blown air in the second heat absorption heat exchanger 15b (i.e., the amount of heat absorbed by the adsorbent) is greater than the amount of cooling of the blown air in the first heat absorption heat exchanger 15a. Therefore, in the refrigeration cycle apparatus 10b, the blown air to be blown into the room can be efficiently cooled in the order of the first heat absorption heat exchanger 15a to the second heat absorption heat exchanger 15b.

[0113] Fourth Embodiment This embodiment describes a modification of the refrigeration cycle apparatus 10 described in the first embodiment. In the refrigeration cycle apparatus 10 of this embodiment, as shown in the overall configuration diagram of Figure 5, compared to the first embodiment, part of the configuration of the low-pressure side extraction section 16 is changed and a foreign matter filter 18 is added.

[0114] As shown in Fig. 6, the low-pressure side extraction section 16 of this embodiment has a tapered portion 16f that forms a truncated cone-shaped space tapering downward at the lower end of the bottomed cylindrical container. The lower space 16h of this embodiment is formed inside the tapered portion 16f.

[0115] Furthermore, the mixed refrigerant inlet 16c is formed so that the refrigerant flows in a tangential direction to the inner wall surface of the circular cross section of the low-pressure side extraction section 16. The mixed refrigerant outlet 16d is formed in the center of the truncated cone-shaped bottom surface of the low-pressure side extraction section 16. Therefore, the lower space 16h in this embodiment constitutes a centrifugal separation section that extracts gas-phase refrigerant from the mixed refrigerant by the action of centrifugal force.

[0116] Furthermore, at least the inner wall surface 16i of the low-pressure side extraction section 16, which is the portion that forms the lower space 16h, is subjected to a surface treatment to improve the slipperiness of the adsorbent. Specifically, the inner wall surface 16i in this embodiment is coated with a fluororesin.

[0117] The foreign matter filter 18 is disposed in a refrigerant passage extending from the gas-phase refrigerant outlet 16e of the low-pressure side extraction section 16 to the suction port of the compressor 11. The average opening diameter of the foreign matter filter 18 is smaller than the average opening diameter of the adsorbent filter 161. In other words, the mesh size of the foreign matter filter 18 is finer than the mesh size of the adsorbent filter 161. That is, the mesh size of the foreign matter filter 18 is smaller than the mesh size of the adsorbent filter 161.

[0118] Other configurations and operations of the refrigeration cycle device 10 and the air conditioner 1 are the same as those in the first embodiment. Therefore, the air conditioner 1 of this embodiment can cool the room, similarly to the first embodiment.

[0119] Furthermore, the refrigeration cycle apparatus 10 of this embodiment can achieve the same effects as those of the first embodiment. That is, the refrigeration cycle apparatus 10 of this embodiment can improve the cycle operating efficiency compared to a typical vapor compression refrigeration cycle apparatus in which the refrigerant is not mixed with an adsorbent. Furthermore, the reliability of a refrigeration cycle apparatus that circulates a mixed refrigerant in which the refrigerant is mixed with an adsorbent can be improved.

[0120] Some adsorbents may lose part of their structure during circulation, generating foreign matter. If the compressor sucks in the foreign matter along with the refrigerant, this may adversely affect the compressor's service life. In contrast, the refrigeration cycle apparatus 10 of this embodiment is equipped with a foreign matter filter 18, which prevents the compressor 11 from sucking in foreign matter.

[0121] In the low-pressure side extraction section 16 of the present embodiment, the lower space 16h constitutes a centrifugal separation section, which allows a low-pressure side extraction section that extracts gas phase refrigerant from the mixed refrigerant to be realized with a simple configuration.

[0122] Furthermore, in the low-pressure side extraction section 16 of this embodiment, the mixed refrigerant outlet 16d is formed in the center of the truncated cone-shaped bottom surface of the low-pressure side extraction section 16. This makes it easy for the powdery or particulate adsorbent to flow out from the mixed refrigerant outlet 16d.

[0123] Here, if the proportion of adsorbent contained in the mixed refrigerant stored in the lower space 16h of the low-pressure side extraction section 16 increases, there is a possibility that the powdery or particulate adsorbent will clog the lower space 16h. If the adsorbent clogs the lower space 16h, there is a possibility that the refrigeration cycle apparatus 10 will not be able to stably exert its cooling capacity.

[0124] In contrast, in this embodiment, the inner wall surface of the low-pressure side extraction section 16 is coated with a fluororesin to improve the slipperiness of the adsorbent. This prevents the powdery or particulate adsorbent from clogging the lower space 16h. Therefore, this embodiment can improve the reliability of the refrigeration cycle apparatus 10 and ensure stable operation of the refrigeration cycle apparatus 10.

[0125] Fifth Embodiment This embodiment describes a modification of the refrigeration cycle apparatus 10 described in the first embodiment. As shown in the overall configuration diagram of FIG. 7 , the refrigeration cycle apparatus 10 of this embodiment additionally includes an auxiliary adsorbent pump 27 in addition to the first embodiment.

[0126] The auxiliary adsorbent pump 27 is an auxiliary transport section that transports the refrigerant contained in the mixed refrigerant flowing out from the mixed refrigerant outlet 16d of the low-pressure side extraction section 16 to the discharge side suction port 12c of the discharge side ejector 12 without increasing the pressure of the refrigerant.

[0127] Here, the auxiliary adsorbent pump 27 not increasing the pressure of the refrigerant contained in the mixed refrigerant means that the auxiliary adsorbent pump 27 does not increase the pressure of the refrigerant at the discharge suction port 12c above the pressure of the refrigerant contained in the mixed refrigerant at the mixed refrigerant outlet 16d. Therefore, when the auxiliary adsorbent pump 27 transports the mixed refrigerant, a change in the packing density of the adsorbent contained in the mixed refrigerant causes an increase in the pressure of the surrounding gas-phase refrigerant, but this is not included in the increase in the pressure of the refrigerant contained in the mixed refrigerant by the auxiliary adsorbent pump 27.

[0128] The auxiliary adsorbent pump 27 may be an electric rotary positive displacement uniaxial eccentric screw pump, a rotary pump, a diaphragm pump, or the like, which have little change in volume. The rotation speed (i.e., transport capacity) of the auxiliary adsorbent pump 27 is controlled by a control signal output from the control device 20. The other configurations of the refrigeration cycle system 10 and the air conditioner 1 are the same as those of the first embodiment.

[0129] Next, a description will be given of the operation of the air conditioner 1 having the above configuration. In the refrigeration cycle system 10 of this embodiment, the control device 20 increases the transport capacity of the auxiliary adsorbent pump 27 as the refrigerant discharge capacity of the compressor 11 increases.

[0130] Other operations are the same as those of the first embodiment. Therefore, the air conditioner 1 of this embodiment can cool the room, as in the first embodiment. Furthermore, the refrigeration cycle device 10 of this embodiment can improve the operating efficiency of the cycle and can also improve reliability, as in the first embodiment.

[0131] Here, the discharge side pressure boosting section 12f of the discharge side ejector 12 uses the pressure energy of the discharged refrigerant to boost the pressure of both the discharge side injected refrigerant and the gas phase refrigerant contained in the mixed refrigerant sucked through the discharge side suction port 12c. Therefore, in order to reduce the power consumption of the compressor 11, it is effective to reduce the amount of gas phase refrigerant contained in the mixed refrigerant sucked through the discharge side suction port 12c.

[0132] However, in order to transport the adsorbents contained in the mixed refrigerant flowing out from the mixed refrigerant outlet 16d to the discharge-side suction port 12c by the suction action of the discharge-side ejector 12, it is necessary to cause the gas-phase refrigerant contained in the mixed refrigerant to flow and transport the adsorbents by the drag of the gas-phase refrigerant. Therefore, in order to properly transport the adsorbents by the suction action of the discharge-side ejector 12, it is not preferable to reduce the amount of refrigerant contained in the mixed refrigerant.

[0133] In contrast, the refrigeration cycle apparatus 10 of this embodiment is provided with an auxiliary adsorbent pump 27. With this, even if the amount of refrigerant contained in the mixed refrigerant is reduced, the adsorbent contained in the mixed refrigerant can be transported by the transport capacity of the auxiliary adsorbent pump 27. Therefore, the amount of refrigerant contained in the mixed refrigerant can be reduced, and the power consumption of the compressor 11 can be reduced.

[0134] Furthermore, the auxiliary adsorbent pump 27 of this embodiment does not increase the pressure of the refrigerant contained in the mixed refrigerant. Therefore, the power consumption of the auxiliary adsorbent pump 27 can be reduced, and the addition of the auxiliary adsorbent pump 27 is unlikely to cause a deterioration in the operating efficiency of the cycle. Furthermore, the auxiliary adsorbent pump 27 is not required to have high sealing properties, etc. Therefore, the addition of the auxiliary adsorbent pump 27 is unlikely to cause a deterioration in the reliability of the cycle.

[0135] Sixth Embodiment This embodiment describes a modification of the refrigeration cycle apparatus 10 described in the first embodiment. As shown in the explanatory diagram of FIG. 8 , the refrigeration cycle apparatus 10 of this embodiment has a more clarified positional relationship between the low-pressure side extraction section 16 and the discharge side ejector 12 than the first embodiment, and an adsorbent flow rate adjustment valve 28 is added.

[0136] In the discharge side ejector 12 and the low-pressure side extraction unit 16 of this embodiment, the mixed refrigerant outlet 16d of the low-pressure side extraction unit 16 is positioned above the discharge side suction port 12c of the discharge side ejector 12. Therefore, the discharge side ejector 12 and the low-pressure side extraction unit 16 are arranged so that the mixed refrigerant flowing out from the mixed refrigerant outlet 16d can flow through the mixed refrigerant passage 23 by gravity and move toward the discharge side suction port 12c.

[0137] The adsorbent flow rate control valve 28 is a powder flow rate control unit that adjusts the flow rate of the adsorbent flowing through the mixed refrigerant passage 23. The adsorbent flow rate control valve 28 adjusts the flow rate of the adsorbent flowing through the mixed refrigerant passage 23 by changing the cross-sectional area of ​​the mixed refrigerant passage 23 without clogging the mixed refrigerant passage 23.

[0138] An electric gate valve or the like that operates with a relatively small driving force can be used as the adsorbent flow control valve 28. The opening degree (opening area of ​​the passage cross-sectional area) of the adsorbent flow control valve 28 is controlled by a control signal output from the control device 20. Other configurations of the refrigeration cycle device 10 and the air conditioner 1 are the same as those in the first embodiment.

[0139] Next, a description will be given of the operation of the air conditioner 1 having the above configuration. In the refrigeration cycle system 10 of this embodiment, the control device 20 controls the operation of the adsorbent flow control valve 28 so as to increase the passage cross-sectional area of ​​the mixed refrigerant passage 23 as the refrigerant discharge capacity of the compressor 11 increases.

[0140] Other operations are the same as those of the first embodiment. Therefore, the air conditioner 1 of this embodiment can cool the room, as in the first embodiment. Furthermore, the refrigeration cycle device 10 of this embodiment can improve the operating efficiency of the cycle and can also improve reliability, as in the first embodiment.

[0141] Furthermore, in the refrigeration cycle apparatus 10 of this embodiment, the adsorbent contained in the mixed refrigerant flowing out from the mixed refrigerant outlet 16d can be transported by gravity to the discharge-side suction port 12c of the discharge-side ejector 12. Therefore, similar to the fifth embodiment, the amount of refrigerant contained in the mixed refrigerant can be reduced, and the power consumption of the compressor 11 can be reduced.

[0142] Furthermore, the refrigeration cycle apparatus 10 of this embodiment is provided with the adsorbent flow rate control valve 28, which makes it possible to adjust the amount of adsorbent sucked through the discharge-side suction port 12c of the discharge-side ejector 12 to an appropriate amount. Furthermore, the adsorbent flow rate control valve 28 does not block the mixed refrigerant passage 23, which makes it less likely to cause wear on sliding parts and sealing parts. Therefore, the addition of the adsorbent flow rate control valve 28 is less likely to cause a decrease in cycle reliability.

[0143] Seventh Embodiment This embodiment describes a modification of the refrigeration cycle apparatus 10 described in the first embodiment. In the refrigeration cycle apparatus 10 of this embodiment, an adsorbent heat exchanger 29 is added to the refrigeration cycle apparatus 10 of the first embodiment, as shown in the overall configuration diagram of FIG.

[0144] The adsorbent heat exchanger 29 is an adsorbent heat exchange section that exchanges heat between the adsorbent contained in the mixed refrigerant flowing through the flow path from the mixed refrigerant outlet of the heat dissipation heat exchanger 13 to the mixed refrigerant inlet of the heat absorption heat exchanger 15 and the adsorbent contained in the mixed refrigerant flowing through the flow path from the mixed refrigerant outlet of the heat absorption heat exchanger 15 to the mixed refrigerant inlet of the heat dissipation heat exchanger 13.

[0145] More specifically, the adsorbent heat exchanger 29 of this embodiment exchanges heat between the adsorbent contained in the mixed refrigerant flowing through the flow path from the mixed refrigerant outlet of the heat dissipation heat exchanger 13 to the inlet of the electric expansion valve 14 and the adsorbent contained in the mixed refrigerant flowing through the mixed refrigerant passage 23. That is, the adsorbent heat exchanger 29 of this embodiment exchanges heat between the adsorbent contained in the mixed refrigerant flowing through region H1 in Fig. 9 and the adsorbent contained in the mixed refrigerant flowing through region L1.

[0146] Here, a mixed refrigerant containing a powdery or particulate adsorbent flows through the adsorbent heat exchanger 29. For this reason, it is desirable that the adsorbent heat exchanger 29 has a configuration with low passage resistance. Therefore, in this embodiment, as shown in Fig. 10, a high-temperature side passage 29a and a low-temperature side passage 29b formed by metal refrigerant piping are joined to form a heat exchange section that exchanges heat between the adsorbents contained in the mixed refrigerant flowing through each passage.

[0147] The high-temperature side passage 29a is a refrigerant passage through which the mixed refrigerant flowing out from the mixed refrigerant outlet of the heat-rejection heat exchanger 13 flows. The low-temperature side passage 29b is a refrigerant passage through which the mixed refrigerant flowing out from the mixed refrigerant outlet of the heat-absorbing heat exchanger 15 flows. As shown in Fig. 10 , the adsorbent heat exchanger 29 forms a so-called counterflow type heat exchange section in which the flow direction of the adsorbent flowing through the high-temperature side passage 29a is opposite to the flow direction of the adsorbent flowing through the low-temperature side passage 29b.

[0148] Other configurations and operations of the refrigeration cycle device 10 and the air conditioner 1 are the same as those of the first embodiment. Therefore, the air conditioner 1 of this embodiment can cool the room, as in the first embodiment. Furthermore, the refrigeration cycle device 10 of this embodiment can improve the operating efficiency of the cycle and can also improve reliability, as in the first embodiment.

[0149] The adsorbent, which is a powder or particulate solid, does not change in volume or temperature even when the ambient pressure changes. Therefore, when a low-temperature adsorbent is introduced into the heat dissipation heat exchanger 13, the heat of adsorption released in the heat dissipation heat exchanger 13 is not only released to the outside air, but also dissipated into the adsorbent itself and consumed to raise the temperature of the adsorbent.

[0150] Similarly, if a high-temperature adsorbent is introduced into the endothermic heat exchanger 15, the heat of desorption absorbed in the endothermic heat exchanger 15 is absorbed not only from the blown air but also from the adsorbent itself, and is consumed to lower the temperature of the adsorbent. As a result, the air conditioning device 1 may not be able to sufficiently improve the cooling capacity of the blown air.

[0151] In contrast to this, the refrigeration cycle apparatus 10 of this embodiment is provided with an adsorbent heat exchanger 29. The adsorbent heat exchanger 29 can transfer heat possessed by the adsorbent flowing into the heat absorption heat exchanger 15 to the adsorbent flowing into the heat dissipation heat exchanger 13. The temperature of the adsorbent flowing into the heat dissipation heat exchanger 13 can be increased, and the temperature of the adsorbent flowing into the heat absorption heat exchanger 15 can be decreased.

[0152] This suppresses the sensible heat change of the adsorbent in the heat release heat exchanger 13, thereby increasing the amount of heat released to the outside air. Furthermore, it suppresses the sensible heat change of the adsorbent in the heat absorption heat exchanger 15, thereby increasing the amount of heat absorbed from the blown air. As a result, the air conditioning device 1 can sufficiently improve the cooling capacity of the blown air.

[0153] Furthermore, in this embodiment, an example has been described in which an adsorbent heat exchanger 29 is used to perform heat exchange between an adsorbent contained in the mixed refrigerant flowing through the H1 region of Figure 9 and an adsorbent contained in the mixed refrigerant flowing through the L1 region of Figure 9, but the adsorbent heat exchange unit is not limited to this.

[0154] In the adsorbent heat exchange section, heat exchange between different combinations of adsorbents may be performed as long as it is possible to transfer the heat contained in the adsorbent flowing into the heat absorption heat exchanger 15 to the adsorbent flowing into the heat dissipation heat exchanger 13.

[0155] For example, heat exchange may be performed between one of the adsorbents contained in the mixed refrigerant flowing through region H1 in Figure 9 and one of the adsorbents contained in the mixed refrigerant flowing through region H2 and one of the adsorbents contained in the mixed refrigerant flowing through region L1, the adsorbents contained in the mixed refrigerant flowing through region L2, and the adsorbents contained in the mixed refrigerant flowing through region L3.

[0156] The L2 region indicates the flow path from the outlet of the discharge-side pressure increasing section 12f of the discharge-side ejector 12 to the mixed refrigerant inlet of the heat dissipation heat exchanger 13. The L3 region indicates the flow path from the mixed refrigerant outlet of the heat absorption heat exchanger 15 to the mixed refrigerant inlet 16c of the low-pressure side extraction section 16. The H2 region indicates the flow path from the outlet of the electric expansion valve 14 to the mixed refrigerant inlet of the heat absorption heat exchanger 15.

[0157] In the refrigeration cycle device 10, in order to improve the efficiency of heat exchange between adsorbents and to suppress unnecessary heat exchange between gas phase refrigerants contained in the mixed refrigerant, it is desirable to perform heat exchange in the adsorbent heat exchanger 29 between the adsorbent contained in the mixed refrigerant flowing through the L1 region and the adsorbent contained in the mixed refrigerant flowing through the H1 region.

[0158] Eighth Embodiment This embodiment describes a modification of the refrigeration cycle apparatus 10a described in the second embodiment. As shown in the overall configuration diagram of Fig. 11 , the refrigeration cycle apparatus 10a of this embodiment is configured by adding an adsorbent heat exchanger 29 similar to that of the seventh embodiment to the second embodiment.

[0159] The adsorbent heat exchanger 29 of this embodiment exchanges heat between the adsorbent contained in the mixed refrigerant flowing through the flow path from the mixed refrigerant outlet 26d of the high-pressure side extraction section 26 to the inlet of the fixed throttle 17 and the adsorbent contained in the mixed refrigerant flowing through the mixed refrigerant passage 23. That is, the adsorbent heat exchanger 29 of this embodiment exchanges heat between the adsorbent contained in the mixed refrigerant flowing through the H3 region of Figure 11 and the adsorbent contained in the mixed refrigerant flowing through the L1 region of Figure 11.

[0160] The rest of the configuration and operation of the refrigeration cycle apparatus 10a and the air conditioner 1a are the same as those of the second embodiment. Therefore, the air conditioner 1a of this embodiment can cool the room, as in the second embodiment. Furthermore, the refrigeration cycle apparatus 10a of this embodiment can improve the operating efficiency of the cycle and can also improve reliability, as in the second embodiment.

[0161] In addition, the refrigeration cycle apparatus 10a of this embodiment is provided with the adsorbent heat exchanger 29, so that the cooling capacity of the blown air can be sufficiently improved, similarly to the seventh embodiment.

[0162] Furthermore, in this embodiment, an example has been described in which an adsorbent heat exchanger 29 is used to perform heat exchange between an adsorbent contained in the mixed refrigerant flowing through the H3 region of Figure 11 and an adsorbent contained in the mixed refrigerant flowing through the L1 region of Figure 11, but the adsorbent heat exchange unit is not limited to this.

[0163] For example, heat exchange may be performed between any one of the adsorbents contained in the mixed refrigerant flowing through region H1 in Figure 11, the adsorbents contained in the mixed refrigerant flowing through region H3, the adsorbents contained in the mixed refrigerant flowing through region H4, and the adsorbents contained in the mixed refrigerant flowing through region H5, and any one of the adsorbents contained in the mixed refrigerant flowing through region L1, the adsorbents contained in the mixed refrigerant flowing through region L2, and the adsorbents contained in the mixed refrigerant flowing through region L3.

[0164] The H3 region indicates a flow path from the mixed refrigerant outlet 26d of the high-pressure side extraction section 26 to the inlet of the fixed throttle 17. The H4 region indicates a flow path from the outlet of the fixed throttle 17 to the pressure reduction side suction port 22c of the pressure reduction side ejector 22. The H5 region indicates a flow path from the outlet of the pressure reduction side boost section 22f of the pressure reduction side ejector 22 to the mixed refrigerant inlet of the heat absorption heat exchanger 15.

[0165] In the refrigeration cycle device 10a, in order to improve the efficiency of heat exchange between adsorbents and to suppress unnecessary heat exchange between gas phase refrigerants contained in the mixed refrigerant, it is desirable to perform heat exchange in the adsorbent heat exchanger 29 between the adsorbent contained in the mixed refrigerant flowing through the L1 region and the adsorbent contained in the mixed refrigerant flowing through the H3 region or the H4 region.

[0166] Ninth Embodiment This embodiment describes a modification of the refrigeration cycle apparatus 10b described in the third embodiment. As shown in the overall configuration diagram of Fig. 12, the refrigeration cycle apparatus 10b of this embodiment is configured by adding an adsorbent heat exchanger 29 similar to that of the seventh embodiment to the third embodiment.

[0167] As in the eighth embodiment, the adsorbent heat exchanger 29 of this embodiment exchanges heat between the adsorbent contained in the mixed refrigerant flowing through the H3 region of Figure 12 and the adsorbent contained in the mixed refrigerant flowing through the L1 region of Figure 12.

[0168] The rest of the configuration and operation of the refrigeration cycle device 10b and the air conditioner 1b are the same as those of the third embodiment. Therefore, the air conditioner 1b of this embodiment can cool the room, as in the third embodiment. Furthermore, the refrigeration cycle device 10b of this embodiment can improve the operating efficiency of the cycle and also improve reliability, as in the third embodiment.

[0169] In addition, the refrigeration cycle apparatus 10b of this embodiment is provided with the adsorbent heat exchanger 29, and therefore, similarly to the seventh embodiment, the cooling capacity of the blown air can be sufficiently improved.

[0170] Furthermore, in this embodiment, an example has been described in which an adsorbent heat exchanger 29 is used to perform heat exchange between an adsorbent contained in the mixed refrigerant flowing through the H3 region of Figure 12 and an adsorbent contained in the mixed refrigerant flowing through the L1 region of Figure 12, but the adsorbent heat exchange unit is not limited to this.

[0171] For example, heat exchange may be performed between one of the adsorbents contained in the mixed refrigerant flowing through region H1 in Figure 12, the adsorbents contained in the mixed refrigerant flowing through region H3, and the adsorbents contained in the mixed refrigerant flowing through region H6, and one of the adsorbents contained in the mixed refrigerant flowing through region L1, the adsorbents contained in the mixed refrigerant flowing through region L2, and the adsorbents contained in the mixed refrigerant flowing through region L3.

[0172] Region H6 indicates a flow path from the outlet of the fixed throttle 17 to the mixed refrigerant inlet of the second heat absorption heat exchanger 15b.

[0173] In this embodiment, in order to minimize the effect on the cooling capacity of the gas phase refrigerant in the mixed refrigerant due to temperature changes, it is desirable to perform heat exchange in the adsorbent heat exchanger 29 between the adsorbent contained in the mixed refrigerant flowing through the L1 region and the adsorbent contained in the mixed refrigerant flowing through the H3 region or the H6 region.

[0174] Tenth Embodiment In this embodiment, a modified example of the refrigeration cycle apparatus 10 described in the fourth embodiment will be described. As shown in the explanatory diagram of Fig. 13 , the refrigeration cycle apparatus 10 of this embodiment has a vibration transmission rod 16j in comparison with the first embodiment.

[0175] The vibration transmission rod 16j is a vibration transmission part that transmits vibrations of the compressor 11 to the low-pressure side extraction part 16. The vibration transmission rod 16j is a rigid metal body that is directly connected to both the compressor 11 and the low-pressure side extraction part 16. Therefore, the vibration transmission rod 16j is included in the vibrating part that vibrates the low-pressure side extraction part 16. Furthermore, the compressor 11 of this embodiment also functions as a vibrating part.

[0176] Other configurations and operations of the refrigeration cycle device 10 and the air conditioner 1 are the same as those of the first embodiment. Therefore, the air conditioner 1 of this embodiment can cool the room, as in the first embodiment. Furthermore, the refrigeration cycle device 10 of this embodiment can improve the operating efficiency of the cycle and can also improve reliability, as in the first embodiment.

[0177] Furthermore, in the refrigeration cycle apparatus 10 of this embodiment, the vibration transmission rod 16j transmits the vibration of the compressor 11 to the low-pressure side extraction section 16. Therefore, it is possible to prevent the powdery or particulate adsorbent from clogging the lower space 16h.

[0178] The present disclosure is not limited to the above-described embodiments, and various modifications can be made as follows within the scope of the present disclosure.

[0179] In the above-described embodiment, the refrigeration cycle apparatus 10, 10a, 10b according to the present disclosure is applied to an air conditioner, but the application of the refrigeration cycle apparatus 10, 10a, 10b according to the present disclosure is not limited to this. For example, the refrigeration cycle apparatus 10, 10a, 10b may be applied to a vehicle air conditioner, a freezing apparatus, a refrigerator, etc.

[0180] In the above-described embodiment, the heat radiating section radiates heat from the refrigerant mixture to the outside air, and the heat absorbing section causes the refrigerant mixture to absorb heat from the ventilation air, which is the object to be cooled. However, the present invention is not limited to this. The heat radiating section may radiate heat from the refrigerant mixture to the object to be heated, and the heat absorbing section may cause the refrigerant mixture to absorb heat from the outside air. In this case, the present invention may be applied to a heating device that heats the ventilation air, which is the object to be heated, or a hot water heater that heats water for daily use, etc., which is the object to be heated.

[0181] The configuration of the refrigeration cycle device is not limited to the configuration disclosed in the above-described embodiment.

[0182] In the above embodiment, the discharge-side ejector 12 is used as the discharge-side transport unit, but the present invention is not limited to this. For example, the discharge-side transport unit may be an expander that converts the pressure energy of the refrigerant into mechanical energy for transporting the mixed refrigerant. The same applies to the pressure-reducing-side transport unit.

[0183] In the second and third embodiments, the electric expansion valve 14 a is used, but the electric expansion valve 14 a is not an essential component. Therefore, the refrigerant separated in the high-pressure-side extraction section 26 may be directly introduced into the pressure-reducing-side nozzle section 22 a of the pressure-reducing-side ejector 22.

[0184] Furthermore, the electric expansion valve 14a may be integrated with the pressure-reducing side ejector 22. In this case, a needle-shaped or conical valve element may be disposed in the passage of the pressure-reducing side nozzle portion 22a of the pressure-reducing side ejector 22, and the same function as that of the electric expansion valve 14a may be achieved by displacing the valve element.

[0185] In the fourth embodiment described above, an example was described in which a fluororesin coating was used to improve the slipperiness of the inner wall surface of the low-pressure side extraction section 16, but this is not limiting. Titanium oxide coating, nickel-polytetraethylene composite plating, ultrasonic surface finishing, etc. may also be used as long as it can improve the slipperiness of the inner wall surface of the low-pressure side extraction section 16.

[0186] In the tenth embodiment, the vibrating unit is formed by the compressor 11 and the vibration transmission rod 16j. However, the present invention is not limited to this. For example, the vibrating unit may be formed by other in-vehicle equipment that generates vibrations when in operation. For example, the vibrating unit may be formed by an ultrasonic vibration device. In this case, the ultrasonic vibration device, which is the vibrating unit, may be directly attached to the low-pressure side extraction unit 16, and the vibration transmission rod 16j may be eliminated.

[0187] In the above-described tenth embodiment, the vibration of the compressor 11 is transmitted to the low-pressure side extraction section 16 by the vibration transmission rod 16j, but the present invention is not limited to this. For example, the vibration of the compressor 11 may be transmitted to the low-pressure side extraction section 16 by a refrigerant pipe connecting the gas-phase refrigerant outlet 16e of the low-pressure side extraction section 16 and the suction port of the compressor 11.

[0188] The vibration transmission rod 16j is not limited to a rigid metal body, but may be made of an elastic material. Furthermore, the vibration transmission rod 16j may have a frequency filter function that transmits vibrations of a frequency effective for preventing clogging of the adsorbent and attenuates vibrations of other frequencies.

[0189] The refrigeration cycle apparatuses 10 a and 10 b may also include a vibration unit for the high-pressure side extraction unit that vibrates the high-pressure side extraction unit 26 .

[0190] In the above-described embodiment, an example in which a metal organic framework is used as the adsorbent has been described, but the adsorbent is not limited to this. For example, activated carbon or a hydrate may be used as the adsorbent.

[0191] In the above-described embodiment, carbon dioxide is used as the refrigerant for the refrigeration cycle devices 10, 10a, and 10b. However, the refrigerant is not limited to carbon dioxide. For example, R1234yf, R134a, R600a, R410A, R404A, R32, R407C, R290 (propane), ammonia, or a mixture thereof may be used as the refrigerant.

[0192] Furthermore, a gas-liquid separation unit of an impingement type, which decelerates the mixed refrigerant by causing it to collide with an impingement plate and causes the high-density liquid-phase refrigerant to fall downward, may be applied to the lower space 16a of the low-pressure side extraction unit 16 and the lower space 26a of the high-pressure side extraction unit 26 in the above-described embodiment. A gas-liquid separation unit of a surface tension type, which separates the liquid-phase refrigerant into gas and liquid by causing the liquid-phase refrigerant to adhere to a wavy adhesion plate, may also be applied.

[0193] The operation of the refrigeration cycle device is not limited to the operation disclosed in the above embodiment.

[0194] In the above embodiment, the low-pressure side extraction unit 16 extracts gas-phase refrigerant from the mixed refrigerant, but the refrigerant extracted by the low-pressure side extraction unit 16 is not limited to saturated gas-phase refrigerant or gas-phase refrigerant with a degree of superheat. For example, the refrigerant may be a gas-liquid two-phase refrigerant with a relatively high dryness that contains an appropriate amount of liquid-phase refrigerant for lubricating the compressor 11.

[0195] Although the above embodiment does not describe the state of the refrigerant discharged from the compressor 11, the state of the discharged refrigerant changes depending on the type of refrigerant, the outside air temperature, etc. For example, the pressure of the discharged refrigerant may be in a supercritical state where it is equal to or higher than the critical pressure of the refrigerant, or in a subcritical state where it is lower than the critical pressure of the refrigerant.

[0196] Although the above embodiment does not describe the state of the refrigerant in the mixed refrigerant flowing out from the discharge-side pressurization section 12f of the discharge-side ejector 12, the state of the refrigerant in the mixed refrigerant flowing out from the discharge-side pressurization section 12f of the discharge-side ejector 12 changes depending on the type of refrigerant, the outside air temperature, etc. For example, the state of the refrigerant in the mixed refrigerant flowing out from the discharge-side pressurization section 12f may be in a supercritical state or a subcritical state.

[0197] Although the above embodiment does not describe in detail the state of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13, the state of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13 changes depending on the type of refrigerant, the outside temperature, etc. For example, depending on the type of refrigerant, the outside temperature, etc., the mixed refrigerant flowing out from the heat dissipation heat exchanger 13 may be in a supercritical state, a subcritical liquid-phase refrigerant, a gas-liquid two-phase refrigerant, or a gas-phase refrigerant.

[0198] In other words, depending on the type of refrigerant, the outside air temperature, etc., the mixed refrigerant flowing out from the heat dissipation heat exchanger 13 may be a mixed refrigerant in which an adsorbent is mixed with a refrigerant in a supercritical state, a mixed refrigerant in which an adsorbent is mixed with a liquid-phase refrigerant, a mixed refrigerant in which an adsorbent is mixed with a gas-liquid two-phase refrigerant with a low specific enthalpy, or a mixed refrigerant in which an adsorbent is mixed with a gas-phase refrigerant.

[0199] In the above embodiment, an example has been described in which the mixed refrigerant flowing out of the endothermic heat exchanger 15 is a mixed refrigerant in which the adsorbent is mixed with a gas-liquid two-phase refrigerant having a high specific enthalpy, but the present invention is not limited to this. For example, depending on the type of refrigerant, the outside air temperature, etc., the mixed refrigerant may be a mixed refrigerant in which the adsorbent is mixed with a liquid-phase refrigerant, or a mixed refrigerant in which the adsorbent is mixed with a gas-phase refrigerant.

[0200] The means disclosed in each of the above embodiments may be combined as appropriate within the scope of feasibility.

[0201] For example, the low-pressure side extraction section 16 having the tapered portion 16f described in the fourth embodiment may be applied to the refrigeration cycle devices 10, 10a, and 10b described in the second to ninth embodiments. Furthermore, the high-pressure side extraction section 26 described in the second embodiment and the like may have a configuration including a tapered portion and a centrifugal separation section, similar to the low-pressure side extraction section 16 described in the fourth embodiment. Furthermore, the inner wall surface of the high-pressure side extraction section 26 may be surface-treated to improve the slipperiness of the adsorbent, similar to the fourth embodiment.

[0202] Furthermore, the placement of the foreign matter filter 18 described in the fourth embodiment is not limited to the refrigerant passage extending from the gas-phase refrigerant outlet 16e of the low-pressure side extraction section 16 to the suction port of the compressor 11. For example, the foreign matter filter 18 may be placed in the refrigerant passage extending from the discharge port of the compressor 11 to the inlet of the discharge-side nozzle 12a of the discharge-side ejector 12. This can prevent foreign matter from entering the discharge-side nozzle 12a.

[0203] For example, the refrigerant extractor 26 may be disposed in the refrigerant passage extending from the refrigerant outlet 26e of the high-pressure side extraction part 26 to the electric expansion valve 14a. This makes it possible to prevent foreign matter from entering the electric expansion valve 14a.

[0204] For example, the foreign matter filter 18 may be disposed in the refrigerant passage extending from the outlet of the electric expansion valve 14a to the inlet of the pressure-reducing nozzle 22a of the pressure-reducing ejector 22. This can prevent foreign matter from entering the pressure-reducing nozzle 22a. Of course, the foreign matter filter 18 is not limited to being disposed in one location, and may be disposed in multiple locations.

[0205] Furthermore, the auxiliary transport section described in the fifth embodiment may be applied to the refrigeration cycle devices 10, 10a, and 10b described in the second to fourth and seventh to ninth embodiments.

[0206] Furthermore, the positional relationship between the low-pressure side extraction section 16 and the discharge side ejector 12, as well as the adsorbent flow rate control valve, described in the sixth embodiment may be applied to the refrigeration cycle devices 10, 10a, and 10b described in the second to fourth and seventh to ninth embodiments.

[0207] Furthermore, the vibration section described in the tenth embodiment may be applied to the refrigeration cycle devices 10, 10a, and 10b described in the second to ninth embodiments.

[0208] The features of the refrigeration cycle device disclosed in this specification are as follows: (Item 1) A refrigeration cycle device that circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent that adsorbs and desorbs a refrigerant, the refrigeration cycle device comprising: a low-pressure side extraction section (16) that extracts the refrigerant from the mixed refrigerant, a compression section (11) that sucks in the refrigerant extracted by the low-pressure side extraction section, compresses it, and discharges it, a discharge-side transport section (12) that transports the mixed refrigerant that has flowed out of the low-pressure side extraction section to the discharged refrigerant side using pressure energy of the discharged refrigerant discharged from the compression section, a heat radiating section (13) that radiates heat from the mixed refrigerant that has flowed out of the discharge-side transport section, a mixed refrigerant decompression section (14, 17) that decompresses the mixed refrigerant that has flowed out of the heat radiating section, and a heat absorption section (15, 15a, 15b) that desorbs the refrigerant from the adsorbent contained in the mixed refrigerant decompressed by the mixed refrigerant decompression section, and causes the mixed refrigerant to flow out to the mixed refrigerant inlet side of the low-pressure side extraction section. (Item 2) The discharge-side transport unit is a discharge-side ejector (12) having a discharge-side body (12b) formed with a discharge-side nozzle (12a) that decompresses the discharged refrigerant and a discharge-side suction port (12c) that sucks the mixed refrigerant flowing out from the low-pressure-side extraction unit, and the discharge-side body is formed with a discharge-side mixing unit (12e) that mixes the mixed refrigerant sucked through the discharge-side suction port with the discharge-side injection refrigerant sprayed from the discharge-side nozzle. (Item 3) The refrigeration cycle apparatus according to item 2, further comprising an auxiliary transport unit (27) that transports the mixed refrigerant flowing out from the low-pressure-side extraction unit to the discharge-side suction port without increasing the pressure of the refrigerant contained in the mixed refrigerant. (Item 4) The refrigeration cycle device according to any one of Items 1 to 3, further comprising: a high-pressure side extraction section (26) that extracts the refrigerant from the mixed refrigerant flowing out from the heat dissipation section; and a reduced-pressure side transport section (22) that transports the mixed refrigerant flowing out from the high-pressure side extraction section to the refrigerant extracted by the high-pressure side extraction section using pressure energy of the refrigerant extracted by the high-pressure side extraction section.(Item 5) The refrigeration cycle apparatus according to item 4, wherein the decompression-side transport section is a decompression-side ejector (22) having a decompression-side nozzle section (22a) that decompresses the refrigerant extracted by the high-pressure-side extraction section and a decompression-side body section (22b) formed with a decompression-side suction port (22c) that sucks the mixed refrigerant flowing out from the high-pressure-side extraction section, and the decompression-side body section is formed with a decompression-side mixing section (22e) that mixes the mixed refrigerant sucked through the decompression-side suction port with the decompression-side injection refrigerant sprayed from the decompression-side nozzle section. (Item 6) The refrigeration cycle apparatus according to item 5, wherein a mixed refrigerant outlet of the heat absorption section (15b) is connected to the decompression-side suction port. (Item 7) The refrigeration cycle apparatus according to any one of items 1 to 6, wherein the low-pressure-side extraction section has an adsorbent filtration section (161) that allows the refrigerant separated from the mixed refrigerant to pass through and prohibits at least the adsorbent from passing through. (Item 8) The refrigeration cycle apparatus of item 7, further comprising a foreign matter filtering section (18) that allows the refrigerant extracted by the low-pressure side extraction section to pass through but prohibits foreign matter contained in the refrigerant from passing through, wherein the average opening diameter of the foreign matter filtering section is smaller than the average opening diameter of the adsorbent filtering section. (Item 9) The refrigeration cycle apparatus of any one of items 1 to 8, wherein the low-pressure side extraction section has a centrifugal separation section (16h) that separates the refrigerant and the adsorbent by the action of centrifugal force. (Item 10) The refrigeration cycle apparatus of any one of items 1 to 9, wherein an inner wall surface of the low-pressure side extraction section is surface-treated to improve slipperiness. (Item 11) The refrigeration cycle apparatus of items 1 to 10, further comprising a vibration section that vibrates the low-pressure side extraction section. (Item 12) The refrigeration cycle device according to any one of items 1 to 11, further comprising an adsorbent heat exchanger that exchanges heat between the adsorbent flowing through a flow path from a mixed refrigerant outlet of the heat dissipation unit to a mixed refrigerant inlet of the heat absorption unit and the adsorbent flowing through a flow path from the mixed refrigerant outlet of the heat absorption unit to the mixed refrigerant inlet of the heat dissipation unit. (Item 13) The refrigeration cycle device according to any one of items 1 to 12, wherein the adsorbent includes a metal organic framework having a metal ion and an organic ligand.

[0209] Although the present disclosure has been described with reference to the embodiments, it is understood that the present disclosure is not limited to the embodiments or structures. The present disclosure also encompasses various modifications and equivalent modifications. In addition, various combinations and forms, including only one element, more than one element, or less than one element, are also within the scope and spirit of the present disclosure.

Claims

1. A refrigeration cycle device that circulates a mixed refrigerant obtained by mixing a refrigerant with an adsorbent that adsorbs and desorbs a refrigerant, the refrigeration cycle device comprising: a low-pressure side extraction section (16) that extracts the refrigerant from the mixed refrigerant; a compression section (11) that sucks in the refrigerant extracted by the low-pressure side extraction section, compresses it, and discharges it; a discharge side transport section (12) that transports the mixed refrigerant that flows out of the low-pressure side extraction section to the discharged refrigerant side using pressure energy of the discharged refrigerant discharged from the compression section; a heat dissipation section (13) that dissipates heat from the mixed refrigerant that flows out of the discharge side transport section; a mixed refrigerant decompression section (14, 17) that decompresses the mixed refrigerant that flows out of the heat dissipation section; and a heat absorption section (15, 15a, 15b) that desorbs the refrigerant from the adsorbent contained in the mixed refrigerant decompressed by the mixed refrigerant decompression section, and causes the mixed refrigerant to flow out to the mixed refrigerant inlet side of the low-pressure side extraction section.

2. The discharge side transport section is a discharge side ejector (12) having a discharge side body section (12b) formed with a discharge side nozzle section (12a) that reduces the pressure of the discharged refrigerant and a discharge side suction port (12c) that sucks in the mixed refrigerant flowing out from the low pressure side extraction section, and the refrigeration cycle device described in claim 1 is provided with a discharge side mixing section (12e) that mixes the mixed refrigerant sucked from the discharge side suction port with the discharge side injection refrigerant sprayed from the discharge side nozzle section.

3. A refrigeration cycle device as described in claim 2, which is provided with an auxiliary transport section (27) that transports the mixed refrigerant flowing out from the low-pressure side extraction section to the discharge side suction port side without increasing the pressure of the refrigerant contained in the mixed refrigerant.

4. A refrigeration cycle device as described in claim 1, comprising: a high-pressure side extraction section (26) that extracts the refrigerant from the mixed refrigerant flowing out from the heat dissipation section; and a reduced-pressure side transport section (22) that uses the pressure energy of the refrigerant extracted in the high-pressure side extraction section to transport the mixed refrigerant flowing out from the high-pressure side extraction section to the refrigerant extracted in the high-pressure side extraction section.

5. The refrigeration cycle device according to claim 4, wherein the pressure-reducing side transport section is a pressure-reducing side ejector (22) having a pressure-reducing side nozzle section (22a) that reduces the pressure of the refrigerant extracted by the high-pressure side extraction section, and a pressure-reducing side body section (22b) formed with a pressure-reducing side suction port (22c) that sucks in the mixed refrigerant flowing out from the high-pressure side extraction section, and the pressure-reducing side body section is formed with a pressure-reducing side mixing section (22e) that mixes the mixed refrigerant sucked from the pressure-reducing side suction port with the pressure-reducing side injection refrigerant sprayed from the pressure-reducing side nozzle section.

6. The refrigeration cycle device according to claim 5, wherein the mixed refrigerant outlet of the heat absorption portion (15b) is connected to the pressure reduction side suction port.

7. A refrigeration cycle device as described in claim 1, wherein the low-pressure side extraction section has an adsorbent filtration section (161) that allows the refrigerant separated from the mixed refrigerant to pass through and prohibits at least the adsorbent from passing through.

8. A refrigeration cycle device as described in claim 7, comprising a foreign matter filtering section (18) that allows the refrigerant extracted in the low-pressure side extraction section to pass through and prevents foreign matter contained in the refrigerant from passing through, and the average opening diameter of the foreign matter filtering section is smaller than the average opening diameter of the adsorbent filtering section.

9. A refrigeration cycle device according to claim 1, wherein the low-pressure side extraction section has a centrifugal separation section (16h) for separating the refrigerant from the adsorbent by the action of centrifugal force.

10. A refrigeration cycle device according to claim 1, wherein the inner wall surface of the low-pressure side extraction section is surface-treated to improve slipperiness.

11. The refrigeration cycle device according to claim 1, further comprising a vibration unit for vibrating the low-pressure side extraction unit.

12. A refrigeration cycle device as described in claim 1, comprising an adsorbent heat exchange section (29) for exchanging heat between the adsorbent flowing through a flow path from the mixed refrigerant outlet of the heat dissipation section to the mixed refrigerant inlet of the heat absorption section and the adsorbent flowing through a flow path from the mixed refrigerant outlet of the heat absorption section to the mixed refrigerant inlet of the heat dissipation section.

13. A refrigeration cycle device according to any one of claims 1 to 11, wherein the adsorbent contains a metal organic framework having metal ions and organic ligands.

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