Refrigeration cycle device

Abstract

A refrigeration cycle device that circulates a mixed refrigerant in which an adsorbent is mixed in a refrigerant, includes a low-pressure-side extraction portion (16), a compression portion (11), a discharge-side transport portion (12), a heat radiation portion (13), a mixed refrigerant pressure-reducing portion (14, 17), and a heat absorption portion (15, 15a, 15b). The low-pressure-side extraction portion (16) extracts refrigerant from the mixed refrigerant that flows from the heat absorption portion (15, 15a, 15b). The compression portion (11) sucks and compresses the gas-phase refrigerant extracted by the low-pressure-side extraction portion (16). The discharge-side transport portion (12) uses the pressure energy of the discharge refrigerant discharged from the compression portion (11) to transport the mixed refrigerant that flows from the low-pressure-side extraction portion (16) to the discharge refrigerant side that is discharged from the compression portion (11).

Description

[0001] Cross-reference of related applications

[0002] This application is based on the contents of 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, and the contents thereof are incorporated herein by reference. Technical Field

[0003] This disclosure relates to a refrigeration cycle device. Background Technology

[0004] Previously, Patent Document 1 disclosed a so-called hybrid refrigeration cycle device. The hybrid refrigeration cycle device is a vapor compression refrigeration cycle device that circulates a mixed refrigerant in which an adsorbent is mixed with the refrigerant.

[0005] In this type of refrigeration cycle, the heat of adsorption during the adsorption of refrigerant by the adsorbent and the heat of desorption during the desorption of refrigerant from the adsorbent can be utilized. Therefore, in this mixed-type refrigeration cycle, compared to a conventional vapor compression refrigeration cycle in which the adsorbent is not mixed with the refrigerant, the pressure of the refrigerant on the high-pressure side can be reduced, and the cycle efficiency can be improved.

[0006] Furthermore, Patent Document 1 describes separating the adsorbent from the mixed refrigerant on the low-pressure side, compressing the refrigerant with the separated adsorbent using a compressor, and pressurizing the adsorbent separated from the refrigerant using a booster. It also describes mixing the pressurized adsorbent with the refrigerant discharged from the compressor as a mixed refrigerant on the high-pressure side. Additionally, Patent Document 1 describes that a powder pump can be used as the booster for pressurizing the adsorbent.

[0007] Existing technical documents

[0008] Patent documents

[0009] Patent document 1: International Publication No. 2024 / 004971.

[0010] However, in typical powder pumps, wear is easily caused by the flow of powder, particularly in sliding and sealing parts. Consequently, the service life of powder pumps is more likely to be shorter than that of other components in a refrigeration cycle. As a result, as in Patent Document 1, the overall reliability of the refrigeration cycle can be reduced in structures using powder pumps as boosters. Summary of the Invention

[0011] In view of the above points, the present disclosure aims to provide a refrigeration cycle apparatus that recycles a mixed refrigerant containing an adsorbent in the refrigerant and has high reliability.

[0012] The first aspect of the refrigeration cycle apparatus disclosed herein circulates a mixed refrigerant in which adsorbates and desorbs refrigerant are mixed. Furthermore, it includes a low-pressure side extraction section, a compression section, a discharge side conveying section, a heat dissipation section, a mixed refrigerant pressure reduction section, and a heat absorption section.

[0013] The low-pressure side extraction section extracts refrigerant from the mixed refrigerant. The compression section draws in the refrigerant extracted from the low-pressure side extraction section, compresses it, and discharges it. The discharge side delivery section uses the pressure energy of the discharged refrigerant discharged from the compression section to deliver the mixed refrigerant flowing from the low-pressure side extraction section to the discharge side. The heat dissipation section dissipates heat from the mixed refrigerant flowing from the discharge side delivery section. The mixed refrigerant depressurization section depressurizes the mixed refrigerant flowing from the heat dissipation section. The heat absorption section desorbs refrigerant from the adsorbent contained in the mixed refrigerant depressurized by the mixed refrigerant depressurization section, causing the mixed refrigerant to flow out towards the mixed refrigerant inlet side of the low-pressure side extraction section.

[0014] This constitutes a so-called hybrid refrigeration cycle device. Therefore, in the heat dissipation section, the adsorption heat during refrigerant adsorption by the adsorbent can be dissipated. Furthermore, in the heat absorption section, the desorption heat during refrigerant desorption by the adsorbent can be absorbed. Therefore, compared to conventional vapor compression refrigeration cycles that do not mix the adsorbent with the refrigerant, the cycle efficiency can be improved.

[0015] Furthermore, in the discharge-side conveying section, because the pressure energy of the discharged refrigerant is used to convey the mixed refrigerant, it is easy to achieve a conveying section with fewer sliding and sealing parts. As a result, the reliability of the refrigeration cycle device that circulates a mixed refrigerant containing adsorbents in the refrigerant can be improved.

[0016] Here, the operating efficiency of the hybrid refrigeration cycle device can be defined by dividing the amount of heat absorbed in the heat absorption section by the power consumed to boost both the refrigerant and the adsorbent from low pressure to high pressure. Attached Figure Description

[0017] The foregoing and other objects, features and advantages of this disclosure will become more apparent from the following detailed description with reference to the accompanying drawings.

[0018] Figure 1 This is a schematic overall structural diagram of the refrigeration cycle device according to the first embodiment.

[0019] Figure 2 This is an axial sectional view of the injector according to the first embodiment.

[0020] Figure 3 This is a schematic overall structural diagram of the refrigeration cycle device according to the second embodiment.

[0021] Figure 4 This is a schematic overall structural diagram of the refrigeration cycle device according to the third embodiment.

[0022] Figure 5 This is a schematic overall structural diagram of the refrigeration cycle device according to the fourth embodiment.

[0023] Figure 6 This is a schematic axial cross-sectional view of the low-pressure side extraction section of the fourth embodiment.

[0024] Figure 7 This is a schematic overall structural diagram of the refrigeration cycle device according to the fifth embodiment.

[0025] Figure 8 This is an explanatory diagram showing the positional relationship between the low-pressure side extraction section and the discharge side injector in the sixth embodiment.

[0026] Figure 9 This is a schematic overall structural diagram of the refrigeration cycle apparatus according to the seventh embodiment.

[0027] Figure 10 This is a schematic cross-sectional view of the adsorbent heat exchanger according to the seventh embodiment.

[0028] Figure 11 This is a schematic overall structural diagram of the refrigeration cycle apparatus according to the eighth embodiment.

[0029] Figure 12 This is a schematic overall structural diagram of the refrigeration cycle apparatus according to the ninth embodiment.

[0030] Figure 13 This is an explanatory diagram showing the low-pressure side extraction section and the vibration section in the tenth embodiment. Detailed Implementation

[0031] Hereinafter, several embodiments for implementing this disclosure will be described with reference to the accompanying drawings. In each embodiment, parts corresponding to matters described in previous embodiments are marked with the same reference numerals, and repeated descriptions are omitted. Where only a part of the structure is described in each embodiment, other previously described embodiments can be applied to the other parts of the structure. Not only are combinations of parts that can be specifically combined in each embodiment explicitly shown, but embodiments can also be partially combined with each other, even if not explicitly shown, as long as the combination does not particularly hinder it.

[0032] (First Implementation)

[0033] use Figure 1 , Figure 2 A first embodiment of the refrigeration cycle apparatus according to this disclosure will be described. In this embodiment, [the following will be described]. Figure 1 The refrigeration cycle device 10 shown in the overall structure diagram is used in the air conditioning unit 1. The air conditioning unit 1 includes the refrigeration cycle device 10, the control device 20, etc.

[0034] In the air conditioning unit 1, the refrigeration cycle device 10 constitutes a vapor compression refrigeration cycle that cools the supply air blown into the indoor space that is the target space for air conditioning. In the refrigeration cycle device 10, carbon dioxide (i.e., R744) is used as the refrigerant.

[0035] The refrigerant contains adsorbents. The adsorbents adsorb the refrigerant under high pressure and desorb (in other words, detach) the refrigerant under low pressure. Furthermore, when adsorbing the refrigerant, the adsorbent dissipates the heat (i.e., internal energy) of the adsorbed refrigerant as adsorption heat, and when desorbing the refrigerant, it absorbs the surrounding heat as desorption heat.

[0036] More specifically, in this embodiment, a metal-organic framework (MOF) is used as the adsorbent. MOFs are porous materials obtained by reacting metal ions with organic ligands. MOFs are polymeric structures with numerous openings inside, formed by linking metal ions and organic ligands.

[0037] MOFs can optimize their aperture size through combinations of metal ions and organic ligands. By adjusting the aperture size, MOFs can selectively adsorb target substances. In this embodiment, a MOF suitable for adsorbing carbon dioxide as a refrigerant is used. Specifically, MOF-5 or MOF-200 can be used.

[0038] The adsorbent is insoluble in the refrigerant and is mixed in the refrigerant in the form of a powder or particulate solid. Furthermore, the amount of adsorbent mixed in the refrigerant of this embodiment is less than the amount capable of adsorbing all the refrigerant under normal operating conditions of the refrigeration cycle device 10. Therefore, in the refrigeration cycle device 10, there is no situation where only the adsorbent circulates within the cycle.

[0039] In the following description, for clarity, refrigerants mixed with adsorbents will be referred to as mixed refrigerants. Refrigerants without adsorbents will not be referred to by the term "mixed" but will be referred to as refrigerants, discharge refrigerants, discharge-side injection refrigerants, pressure-reducing-side injection refrigerants, etc.

[0040] In the refrigeration cycle unit 10, the compressor 11 is the compression section that draws in, compresses, and discharges refrigerant. The compressor 11 is an electric compressor that uses an electric motor to drive a fixed-capacity compression mechanism with a fixed discharge capacity. The compression mechanism can be a rotary compressor, a scroll compressor, or the like. The rotational speed of the compressor 11 (i.e., the refrigerant discharge capacity) is controlled by a control signal output from the control device 20.

[0041] At the outlet of the compressor 11, the inlet side of the discharge-side nozzle portion 12a of the discharge-side injector 12 is connected.

[0042] The discharge-side ejector 12 draws in the mixed refrigerant flowing out from the low-pressure side extraction section 16 through the suction effect of the discharge-side injected refrigerant injected from the discharge-side nozzle section 12a, forming a discharge-side suction port 12c in the discharge-side main body section 12b. Furthermore, the discharge-side ejector 12 converts the velocity energy (i.e., expansion energy) of the mixed refrigerant (which is injected into the discharge side and contains the adsorbent) into pressure energy, thereby pressurizing the mixed refrigerant.

[0043] use Figure 2 The detailed structure of the discharge-side injector 12 will be described. The discharge-side injector 12 has a discharge-side nozzle portion 12a and a discharge-side main body portion 12b.

[0044] The discharge-side nozzle 12a is a nozzle that injects refrigerant by converting the pressure energy of the discharged refrigerant from the compressor 11 into velocity energy. The discharge-side nozzle 12a is formed of a generally cylindrical metal member (in this embodiment, stainless steel) that tapers gradually toward the direction of refrigerant flow.

[0045] The discharge-side nozzle section 12a depressurizes the discharged refrigerant isentropically and injects it into the discharge-side mixing section 12e formed in the discharge-side main body section 12b, accelerating the refrigerant to supersonic speeds. The discharge-side nozzle section 12a can be a so-called Laval nozzle or a gradually tapering nozzle.

[0046] The discharge-side main body 12b supports and fixes the discharge-side nozzle 12a, and forms the outer shell of the discharge-side injector 12. The discharge-side main body 12b is formed of a generally cylindrical member made of metal (in this embodiment, aluminum alloy). The discharge-side nozzle 12a is fixed to the interior of one end of the discharge-side main body 12b in the longitudinal direction by means of pressing or the like. The discharge-side main body 12b may also be formed of resin.

[0047] A discharge-side suction port 12c is formed in the cylindrical wall of the discharge-side main body 12b, at a location corresponding to the outer periphery of the discharge-side nozzle 12a. This discharge-side suction port 12c is configured to penetrate both the inside and outside of the discharge-side main body 12b and communicate with the refrigerant injection port of the discharge-side nozzle 12a. The discharge-side suction port 12c draws the mixed refrigerant flowing from the low-pressure side extraction section 16 into the interior of the discharge-side main body 12b through the suction effect of the discharge-side sprayed refrigerant injected from the discharge-side nozzle 12a.

[0048] Furthermore, within the discharge-side main body 12b, a discharge-side suction passage 12d, a discharge-side mixing section 12e, and a discharge-side pressurization section 12f are formed. The discharge-side suction passage 12d is a passage that guides the mixed refrigerant drawn from 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 drawn from the discharge-side suction port 12c with the discharge-side injected refrigerant. The discharge-side mixing section 12e is formed in a generally cylindrical shape.

[0049] The discharge-side pressure boosting section 12f is a space for pressurizing the mixed refrigerant drawn from the discharge-side suction port 12c and the mixed refrigerant injected from the discharge side. The discharge-side pressure boosting section 12f is formed in the shape of a frustum with an enlarged cross-sectional area in the direction of refrigerant flow. In the discharge-side pressure boosting section 12f, the velocity energy of the mixed refrigerant is converted into pressure energy by the shock wave generated by the refrigerant injected from the discharge side and the enlarged cross-sectional area of ​​the passage.

[0050] Therefore, the discharge-side ejector 12 is a discharge-side delivery section that uses the pressure energy of the discharge refrigerant discharged from the compressor 11 to deliver the mixed refrigerant flowing from the low-pressure side extraction section 16 to the discharge refrigerant side. In other words, the discharge-side ejector 12 uses the pressure energy of the discharge refrigerant to mix the mixed refrigerant flowing from the low-pressure side extraction section 16 into the discharge-side injected refrigerant, which is the discharge refrigerant that has consumed pressure energy.

[0051] At the outlet of the discharge-side booster section 12f of the discharge-side ejector 12, a mixed refrigerant inlet side is connected to a heat exchanger 13 for heat dissipation. The heat exchanger 13 is a heat dissipation section that allows the mixed refrigerant flowing out from the discharge-side ejector 12 to exchange heat with the outside air blown by an outside air fan (not shown), thereby dissipating the heat of the mixed refrigerant to the outside air.

[0052] An electric expansion valve 14 is connected to the inlet side of the mixed refrigerant outlet of the heat exchanger 13. The electric expansion valve 14 is a refrigerant depressurization unit that reduces the pressure of the mixed refrigerant flowing out of the heat exchanger 13. More specifically, the electric expansion valve 14 depressurizes 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 regulating unit that adjusts the flow rate of the mixed refrigerant flowing into the heat exchanger 15.

[0053] Specifically, the electrically operated expansion valve 14 has a valve core and an actuation unit. The valve core changes the throttling opening. The actuation unit displaces the valve core. The actuation unit can be an electric actuator such as a stepper motor or a brushless DC motor. The operation of the electrically operated expansion valve 14 is controlled by a control signal output from the control device 20.

[0054] At the outlet of the electric expansion valve 14, a heat-absorbing heat exchanger 15 is connected to the inlet side of the mixed refrigerant. The heat-absorbing heat exchanger 15 allows the mixed refrigerant, whose pressure is reduced by the electric expansion valve 14, to exchange heat with the supply air blown into the room by a blower (not shown). The heat-absorbing heat exchanger 15 is a heat-absorbing section that cools the supply air by desorbing refrigerant from adsorbates contained in the mixed refrigerant and thus cooling the supply air.

[0055] At the mixed refrigerant outlet of the heat exchanger 15, a mixed refrigerant inlet 16c side of a low-pressure side extraction section 16 is connected. The low-pressure side extraction section 16 extracts a portion of the refrigerant that does not contain adsorbates from the mixed refrigerant flowing out of the heat exchanger 15. In other words, the low-pressure side extraction section 16 can be referred to as a low-pressure side separation section that separates the refrigerant without adsorbates from the mixed refrigerant.

[0056] The state of the residual mixed refrigerant from which refrigerant has been extracted in the low-pressure side extraction section 16 is affected by the pressure of the mixed refrigerant flowing out of the heat exchanger 15, the ambient temperature of the area where the low-pressure side extraction section 16 is located, the type of refrigerant, and the amount of refrigerant injected.

[0057] That is, the residual mixed refrigerant from which a portion of the refrigerant has been extracted in the low-pressure side extraction section 16 can be a mixed refrigerant in which an adsorbent is mixed in a gaseous refrigerant, a mixed refrigerant in which an adsorbent is mixed in a gas-liquid two-phase refrigerant, or a mixed refrigerant in which an adsorbent is mixed in a liquid phase refrigerant.

[0058] The low-pressure side extraction section 16 is formed of a bottomed cylindrical metal container with an internal space. The low-pressure side extraction section 16 is configured so that its axial direction is vertical. A flat plate-shaped adsorbent filter 161 is disposed in the internal space of the low-pressure side extraction section 16.

[0059] The adsorbent filter 161 divides the internal space of the low-pressure side extraction section 16 into an upper space 16b and a lower space 16a in the vertical direction. The adsorbent filter 161 is a selectively permeable adsorbent filter section that allows the passage of gaseous refrigerant separated from the mixed refrigerant on the low-pressure side and at least prohibits the passage of adsorbents.

[0060] In the lower space 16a, a mixed refrigerant inlet 16c and a mixed refrigerant outlet 16d are connected to the low-pressure side extraction section 16. In the lower space 16a, a structure is adopted to extract refrigerant from the mixed refrigerant by utilizing the specific gravity difference between the refrigerant and the adsorbent.

[0061] Furthermore, the volume of the lower space 16a is set such that, in the case where the remaining mixed refrigerant is a mixed refrigerant in which adsorbents are mixed in with the liquid phase refrigerant, the lower space 16a can be used as a liquid storage section to store the remaining circulating refrigerant as a saturated liquid phase refrigerant. Thus, gaseous refrigerant is extracted into the upper space 16b from the low-pressure side extraction section 16.

[0062] The mixed refrigerant outlet 16d is an outlet through which the mixed refrigerant stored in the lower space 16a, i.e., the residual mixed refrigerant after the gaseous refrigerant has been extracted, flows out. 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 of the discharge-side ejector 12 is connected to the mixed refrigerant outlet 16d. The refrigerant passage connecting the mixed refrigerant outlet 16d and the discharge-side suction port 12c is the mixed refrigerant passage 23.

[0063] In the upper space 16b, a gaseous refrigerant outlet 16e is connected to the low-pressure side extraction section 16. The gaseous refrigerant outlet 16e is an outlet through which the gaseous refrigerant that has passed through the adsorbent filter 161 on the low-pressure side flows out. The gaseous refrigerant outlet 16e is formed on the top surface of the low-pressure side extraction section 16. The suction port side of the compressor 11 is connected to the low-pressure side extraction section 16.

[0064] Next, the electrical control unit of the air conditioning device 1 in this embodiment will be described. The control device 20 includes a known microcomputer with a CPU, ROM, RAM, etc., and its peripheral circuitry. The control device 20 performs various calculations and processes based on a control program stored in the ROM. Furthermore, based on the results of the calculations and processing, the control device 20 controls the operation of various controllable devices connected to the output side.

[0065] On the input side of the control device 20, various control sensor groups are connected. The control sensor groups include, but are not shown, an interior air temperature sensor, an exterior air temperature sensor, a high-pressure sensor, a high-pressure temperature sensor, an evaporator pressure sensor, and an evaporator temperature sensor.

[0066] The indoor air temperature sensor is an indoor air temperature detection unit that detects the indoor air temperature (i.e., indoor temperature) Tr. The outdoor air temperature sensor is an outdoor air temperature detection unit that detects the outdoor air temperature (i.e., outdoor temperature) Tam.

[0067] The high-pressure sensor is a high-pressure detection unit that detects the high-pressure Pd, which is the pressure of the mixed refrigerant flowing out of the heat exchanger 13. The high-pressure temperature sensor is a high-pressure detection unit that detects the high-pressure temperature Td, which is the temperature of the mixed refrigerant flowing out of the heat exchanger 13.

[0068] 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 of the heat exchanger 15 for heat absorption. 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 of the heat exchanger 15 for heat absorption.

[0069] Additionally, an operation panel (not shown) is connected via wired or wireless connection to the input side of the control device 20. The control device 20 receives operation signals from various operation switches mounted on the operation panel. These operation switches include action switches, temperature setting switches, and airflow setting switches.

[0070] The control device 20 is an integral unit that controls various controllable devices connected to the output side. Therefore, the structure (hardware and software) that controls the operation of each controllable device constitutes the control unit that controls the operation of each controllable device. For example, in the control device 20, the structure that controls the refrigerant discharge capacity of the compressor 11 constitutes the discharge capacity control unit.

[0071] Next, the operation of the air conditioning unit 1 in the above structure will be explained. In the air conditioning unit 1, if the operation switch is turned on (i.e., ON), the control device 20 executes the control program. In the control program, the detection signals of the control sensor group and the operation signals of the operation panel are read in.

[0072] Furthermore, based on the read detection signals and operation signals, the actions of various controlled devices are controlled. Then, at predetermined control cycles, the above control routine of reading detection signals and operation signals, and controlling various controlled devices based on the detection signals and operation signals, is repeated until the termination condition of the control program is met.

[0073] More specifically, in the control program of this embodiment, the refrigerant discharge capacity of the compressor 11 is controlled so that the evaporator temperature Te detected by the evaporator temperature sensor is close to the target evaporator temperature TEO. The target evaporator temperature TEO is calculated based on the indoor air temperature Tr detected by the indoor air temperature sensor, the outdoor air temperature Tam detected by the outdoor air temperature sensor, and the set temperature Tset set by the temperature setting switch, etc.

[0074] Additionally, in the control program, the throttling opening of the electric expansion valve 14 is controlled so that the high pressure Pd detected by the high pressure sensor is close to 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, and is set such that the cycle efficiency is close to its maximum value.

[0075] In the refrigeration cycle device 10, if the control device 20 causes the compressor 11 to operate, the compressor 11 draws in the gaseous refrigerant flowing out of the gaseous refrigerant outlet 16e of the low-pressure side extraction section 16, and compresses and discharges it.

[0076] The refrigerant discharged from the compressor 11 flows into the discharge-side nozzle 12a of the discharge-side injector 12. The refrigerant flowing into the discharge-side nozzle 12a is depressurized isentropically and injected into the discharge-side mixing section 12e of the discharge-side main body 12b. Furthermore, through the suction effect of the discharge-side injected refrigerant from the discharge-side nozzle 12a, the mixed refrigerant flowing out of the mixed refrigerant outlet 16d of the low-pressure side extraction section 16 is drawn in from the discharge-side suction port 12c.

[0077] The mixed refrigerant drawn from the discharge-side suction port 12c flows into the discharge-side mixing section 12e via the discharge-side suction passage 12d. At this time, assuming the mixed refrigerant drawn from the discharge-side suction port 12c contains liquid refrigerant, in the discharge-side mixing section 12e, the liquid refrigerant evaporates by absorbing heat from the discharge side as refrigerant is injected. Therefore, the mixed refrigerant in the discharge-side mixing section 12e becomes a mixed refrigerant containing adsorbents mixed in with the gaseous refrigerant, and flows into the discharge-side pressurization section 12f.

[0078] In the discharge-side pressure boosting section 12f, the velocity energy of the mixed refrigerant is converted into pressure energy by the shock wave generated by the refrigerant injected on the discharge side and the expansion of the passage cross-sectional area. As a result, the pressure of the mixed refrigerant increases. Furthermore, as the pressure of the mixed refrigerant in the discharge-side pressure boosting section 12f increases, the adsorption capacity of the adsorbent increases, and the volume of the mixed refrigerant decreases.

[0079] The mixed refrigerant flowing out from the discharge side booster section 12f flows into the heat exchanger 13 for heat dissipation. The mixed refrigerant flowing into the heat exchanger 13 dissipates heat to the outside gas by using the internal energy stored in the adsorbent when it adsorbs the gaseous refrigerant as adsorption heat.

[0080] The mixed refrigerant flowing from the heat exchanger 13 flows into the electric expansion valve 14 and is depressurized. The depressurized mixed refrigerant then flows into the heat exchanger 15. As the pressure decreases, refrigerant desorbs from the adsorber in the mixed refrigerant flowing into the heat exchanger 15. At this time, the adsorber absorbs heat from the supply air as desorption heat. Furthermore, if the mixed refrigerant contains liquid refrigerant, the liquid refrigerant evaporates and absorbs heat, thereby cooling the supply air.

[0081] The mixed refrigerant flowing out of the 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.

[0082] The gaseous refrigerant flowing from the upper space 16b on the low-pressure side is drawn into the compressor 11 and compressed again. The mixed refrigerant flowing from the lower space 16a is drawn in through the discharge-side suction port 12c of the discharge-side ejector 12.

[0083] As described above, in the air conditioning device 1 of this embodiment, indoor cooling can be achieved by blowing the supply air, which is cooled when passing through the heat exchanger 15 for heat absorption, into the room.

[0084] Furthermore, the refrigeration cycle apparatus 10 of this embodiment is configured as a mixed refrigeration cycle apparatus in which a mixed refrigerant containing adsorbents is circulated. Therefore, in the heat exchanger 13 for heat dissipation, the adsorption heat when the adsorbents adsorb the refrigerant can be dissipated to the outside air. In addition, in the heat exchanger 15 for heat absorption, the desorption heat when the adsorbents desorb the refrigerant can be absorbed from the supply air.

[0085] Therefore, the refrigeration cycle apparatus 10 according to this embodiment, compared with a conventional vapor compression refrigeration cycle apparatus in which the adsorbent is not mixed in the refrigerant, can reduce the pressure of the mixed refrigerant in the heat exchanger 13 for heat dissipation and the pressure of the discharged refrigerant. As a result, the operating efficiency of the cycle can be improved.

[0086] In a refrigeration cycle apparatus that circulates a mixed refrigerant, if the adsorbent is drawn into the compressor along with the refrigerant, it may adversely affect the compressor's lifespan. In contrast, in the refrigeration cycle apparatus 10 of this embodiment, because it has a low-pressure side extraction section 16, it is possible to prevent the compressor 11 from drawing in the adsorbent.

[0087] Furthermore, the refrigeration cycle apparatus 10 of this embodiment includes a discharge-side conveying section. In the discharge-side conveying section, since the pressure energy of the discharged refrigerant is used to convey the mixed refrigerant to the discharge refrigerant side, a conveying section with fewer sliding and sealing parts can be achieved. As a result, the reliability of the refrigeration cycle apparatus 10 according to this embodiment can be improved for circulating a mixed refrigerant in which an adsorbent is mixed in the refrigerant.

[0088] Furthermore, in the refrigeration cycle apparatus 10 of this embodiment, a discharge-side ejector 12 is specifically used as the discharge-side conveying unit. This allows the adsorbent to be pressurized and conveyed with less power than a booster such as a powder pump. Moreover, the discharge-side ejector 12 enables the mixing of refrigerant and mixed refrigerant with a small and simple structure.

[0089] Furthermore, in the refrigeration cycle apparatus 10 of this embodiment, the amount of adsorbent mixed in the refrigerant is less than the amount capable of adsorbing all the refrigerant. Therefore, there is no situation where adsorbents that only adsorb refrigerant circulate within the cycle. Therefore, even if powdered or particulate adsorbents are used, it is easy to prevent adsorbents from remaining in a predetermined location within the cycle.

[0090] (Second Implementation)

[0091] In this embodiment, an example of applying the refrigeration cycle apparatus 10a according to this disclosure to an air conditioning device 1a will be described. In the refrigeration cycle apparatus 10a, as... Figure 3 As shown in the overall structural diagram, compared with the refrigeration cycle device 10 described in the first embodiment, a high-pressure side extraction section 26, a pressure-reducing side ejector 22, and a fixed throttling section 17 are added.

[0092] In the refrigeration cycle apparatus 10a, a mixed refrigerant inlet 26c side of a high-pressure side extraction section 26 is connected to the refrigerant outlet of the heat exchanger 13. The high-pressure side extraction section 26 extracts a portion of the refrigerant that does not contain adsorbates from the mixed refrigerant flowing out of the heat exchanger 13. In other words, the high-pressure side extraction section 26 can be referred to as a high-pressure side separation section that separates the refrigerant without adsorbates from the mixed refrigerant.

[0093] In this embodiment, the state of the refrigerant extracted by the high-pressure side extraction section 26 is affected by the pressure of the mixed refrigerant flowing out of the heat exchanger 13, the ambient temperature of the area where the high-pressure side extraction section 26 is located, the type of refrigerant, and the amount of refrigerant injected. That is, the refrigerant extracted by the high-pressure side extraction section 26 can be a supercritical refrigerant, a gaseous refrigerant, a gas-liquid two-phase refrigerant, or a liquid refrigerant.

[0094] The state of the residual mixed refrigerant from which refrigerant has been extracted in the high-pressure side extraction section 26 is affected by the pressure of the mixed refrigerant flowing out of the heat exchanger 13, the ambient temperature of the area where the high-pressure side extraction section 26 is located, the type of refrigerant, and the amount of refrigerant injected.

[0095] That is, the residual mixed refrigerant from which the refrigerant has been extracted in the high-pressure side extraction section 26 can be a mixed refrigerant that is mixed with adsorbents in a supercritical refrigerant, a mixed refrigerant that is mixed with adsorbents in a gaseous refrigerant, a mixed refrigerant that is mixed with adsorbents in a gas-liquid two-phase refrigerant, or a mixed refrigerant that is mixed with adsorbents in a liquid-phase refrigerant.

[0096] The basic structure of the high-pressure side extraction section 26 is the same as 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. In the lower space 26a, the mixed refrigerant inlet 26c and the mixed refrigerant outlet 26d of the high-pressure side extraction section 26 are connected. In the upper space 26b, the refrigerant outlet 26e of the high-pressure side extraction section 26 is connected.

[0097] 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 structure of the electric expansion valve 14a is the same as that of the electric expansion valve 14 described in the first embodiment. The inlet side of the pressure-reducing nozzle section 22a of the pressure-reducing injector 22 is connected to the outlet of the electric expansion valve 14a.

[0098] A fixed throttling section 17 is connected to the inlet side of the mixed refrigerant outlet 26d of the high-pressure side extraction section 26. The fixed throttling section 17 is a mixed refrigerant depressurization section that depressurizes the mixed refrigerant flowing out of the mixed refrigerant outlet 26d of the high-pressure side extraction section 26. More specifically, in the fixed throttling section 17, the refrigerant contained in the mixed refrigerant is depressurized, thereby reducing the pressure of the ambient refrigerant in the adsorbent.

[0099] Furthermore, the fixed throttling section 17 is a flow adjustment section that adjusts the flow rate of the mixed refrigerant drawn into the pressure-reducing side suction port 22c of the pressure-reducing side injector 22. More specifically, the fixed throttling section 17 can be a throttling orifice, a capillary tube, or the like. The outlet of the fixed throttling section 17 is connected to the pressure-reducing side suction port 22c side of the pressure-reducing side injector 22.

[0100] The pressure-reducing ejector 22 draws in the mixed refrigerant, which has been depressurized by the fixed throttling section 17, from the pressure-reducing side suction port 22c formed in the pressure-reducing side main body 22b through the suction effect of the pressure-reducing side refrigerant injected from the pressure-reducing side nozzle section 22a. Furthermore, the pressure-reducing ejector 22 converts the velocity energy of the mixed refrigerant (which contains the adsorbent) injected onto the pressure-reducing side into pressure energy, thereby increasing the pressure of the mixed refrigerant.

[0101] The basic structure of the decompression-side injector 22 is the same as that of the discharge-side injector 12. Therefore, as Figure 3 As shown, the pressure-reducing side injector 22 has a pressure-reducing side nozzle portion 22a and a pressure-reducing side main body portion 22b. The pressure-reducing side main body portion 22b includes a pressure-reducing side suction port 22c, a pressure-reducing side mixing portion 22e, and a pressure-reducing side pressurizing portion 22f.

[0102] In this embodiment, the pressure boosting performance in the pressure-reducing side boosting section 22f is set to be lower than that in the discharge side boosting section 12f of the discharge side ejector 12. The outlet of the pressure-reducing side boosting section 22f of the pressure-reducing side ejector 22 is connected to the refrigerant inlet side of the heat exchanger 15 for heat absorption.

[0103] Therefore, the pressure-reducing ejector 22 is a pressure-reducing side delivery section that uses the pressure energy of the refrigerant extracted from the high-pressure side extraction section 26 to deliver the mixed refrigerant flowing out of the high-pressure side extraction section 26 to the refrigerant side extracted from the high-pressure side extraction section 26. In other words, the pressure-reducing ejector 22 uses the pressure energy of the refrigerant extracted from the high-pressure side extraction section 26 to mix the mixed refrigerant flowing out of the high-pressure side extraction section 26 into the pressure-reducing side injected refrigerant, which is the refrigerant extracted from the high-pressure side extraction section 26 after consuming pressure energy.

[0104] The remaining structures of the refrigeration cycle device 10a and the air conditioning device 1a are the same as those of the refrigeration cycle device 10 and the air conditioning device 1 described in the first embodiment.

[0105] Next, the operation of the air conditioning unit 1a in the above structure will be explained. The basic operation of the refrigeration cycle unit 10a in this embodiment is the same as that in the first embodiment.

[0106] In the refrigeration cycle device 10a, the mixed refrigerant flowing out from the 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.

[0107] The refrigerant flowing out from the upper space 26b flows into the pressure-reducing nozzle section 22a of the pressure-reducing injector 22 via the electric expansion valve 14a. The refrigerant flowing into the pressure-reducing nozzle section 22a is isentropically depressurized and injected into the pressure-reducing mixing section 22e of the pressure-reducing body section 22b.

[0108] Furthermore, through the suction effect of the refrigerant injected from the pressure-reducing nozzle 22a, the mixed refrigerant after being depressurized by the fixed throttling section 17 is drawn from the pressure-reducing suction port 22c of the pressure-reducing body section 22b.

[0109] The mixed refrigerant drawn from the pressure-reducing side suction port 22c flows into the pressure-reducing side mixing section 22e. In the pressure-reducing side mixing section 22e, the pressure-reducing side sprayed refrigerant injected from the pressure-reducing side nozzle section 22a mixes with the mixed refrigerant drawn from the pressure-reducing side suction port 22c.

[0110] The mixed refrigerant, after being mixed in the pressure-reducing side mixing section 22e, flows out from the pressure-reducing side boosting section 22f and into the heat-absorbing heat exchanger 15. In the heat-absorbing heat exchanger 15, the supply air is cooled, similar to the first embodiment. The remaining operations are the same as in the first embodiment.

[0111] As described above, in the air conditioning device 1a of this embodiment, indoor cooling can be achieved by blowing the supply air, which is cooled when passing through the heat exchanger 15, into the room.

[0112] Furthermore, the refrigeration cycle apparatus 10a according to this embodiment can achieve the same effects as the first embodiment. That is, compared with a conventional vapor compression type refrigeration cycle apparatus that does not mix the adsorbent into the refrigerant, the refrigeration cycle apparatus 10a according to this embodiment can improve the cycle efficiency. Furthermore, the reliability of the refrigeration cycle apparatus that circulates a mixed refrigerant in which the adsorbent is mixed into the refrigerant can be improved.

[0113] Furthermore, the refrigeration cycle apparatus 10a of this embodiment includes a high-pressure side extraction section 26. Therefore, it is possible to suppress the inflow of adsorbent into the electrically operated expansion valve 14a. This provides protection for the electrically operated expansion valve 14a and further improves the reliability of the refrigeration cycle apparatus. Additionally, it improves the adjustment accuracy of the pressure reduction or flow rate in the electrically operated expansion valve 14a.

[0114] Furthermore, the refrigeration cycle apparatus 10a of this embodiment includes a pressure-reducing side conveying section. In the pressure-reducing side conveying section, the pressure energy of the refrigerant extracted from the high-pressure side extraction section 26 can be used to convey the mixed refrigerant to the refrigerant side extracted from the high-pressure side extraction section 26. Therefore, similar to the discharge side conveying section, a conveying section with fewer sliding or sealing parts can be realized, further improving the reliability of the refrigeration cycle apparatus.

[0115] Furthermore, in the refrigeration cycle apparatus 10a of this embodiment, a pressure-reducing side ejector 22 is used as the pressure-reducing side delivery unit, so the refrigerant and the mixed refrigerant can be mixed in a small and simple structure.

[0116] (Third implementation method)

[0117] In this embodiment, an example of applying the refrigeration cycle device 10b according to this disclosure to an air conditioning device 1b will be described. In the refrigeration cycle device 10b, a second heat-absorbing heat exchanger 15b is added compared to the refrigeration cycle device 10a described in the second embodiment. In this embodiment, for clarity of explanation, the heat-absorbing heat exchanger 15 described in the first embodiment will be referred to as the first heat-absorbing heat exchanger 15a.

[0118] The second heat exchanger 15b allows the mixed refrigerant, after being depressurized by the fixed throttling section 17 (which serves as a pressure-reducing section for the mixed refrigerant), to exchange heat with the supply air that has passed through the first heat exchanger 15a. The second heat exchanger 15b is a heat-absorbing section that cools the supply air by desorbing refrigerant from adsorbates contained in the mixed refrigerant and thus cooling the supply air.

[0119] The basic structure of the second heat exchanger 15b is the same as that of the first heat exchanger 15a. Furthermore, in this embodiment, the mixed refrigerant inlet side of the second heat exchanger 15b is connected to the outlet of the fixed throttling section 17. The pressure-reducing side suction port 22c side of the pressure-reducing ejector 22 is connected to the outlet of the mixed refrigerant of the second heat exchanger 15b.

[0120] In the pressure-reducing side ejector 22 of this embodiment, the dimensions of the pressure-reducing side boosting section 22f are set in order to achieve appropriate pressure boosting performance. The remaining structures of the refrigeration cycle device 10b and the air conditioning device 1b are the same as those of the refrigeration cycle device 10a and the air conditioning device 1a described in the second embodiment.

[0121] Next, the operation of the air conditioning unit 1b in the above structure will be explained. The basic operation of the refrigeration cycle device 10b in this embodiment is the same as that in the second embodiment.

[0122] In the refrigeration cycle unit 10b, refrigerant flowing out from the space 26b above the high-pressure side extraction section 26 flows into the pressure-reducing side nozzle section 22a of the pressure-reducing side injector 22 via the electric expansion valve 14a. The refrigerant flowing into the pressure-reducing side nozzle section 22a is isentropically depressurized and injected into the pressure-reducing side mixing section 22e of the pressure-reducing side main body section 22b.

[0123] Furthermore, the mixed refrigerant flowing out of the second heat exchanger 15b is attracted from the pressure-reducing side suction port 22c of the pressure-reducing side main body 22b by the suction effect of the pressure-reducing side sprayed refrigerant from the pressure-reducing side nozzle 22a.

[0124] In the pressure-reducing side mixing section 22e, the pressure-reducing side refrigerant injected from the pressure-reducing side nozzle section 22a mixes with the mixed refrigerant drawn from the pressure-reducing side suction port 22c. The mixed refrigerant in the pressure-reducing side mixing section 22e flows into the pressure-reducing side boosting section 22f. In the pressure-reducing side boosting section 22f, the velocity energy of the mixed refrigerant is converted into pressure energy by the shock wave generated by the pressure-reducing side refrigerant and the expansion of the passage cross-sectional area. As a result, the pressure of the mixed refrigerant increases.

[0125] The mixed refrigerant flowing out from the pressure-boosting section 22f on the depressurization side flows into the first heat-absorbing heat exchanger 15a. In the mixed refrigerant flowing into the first heat-absorbing heat exchanger 15a, refrigerant is desorbed from the adsorbent according to the pressure. At this time, the adsorbent absorbs heat from the supply air as desorption heat. Furthermore, if the mixed refrigerant contains liquid refrigerant, the liquid refrigerant evaporates and absorbs heat, thereby cooling the supply air blown by the blower.

[0126] Additionally, the mixed refrigerant flowing out from the space 26a below the high-pressure side extraction section 26 flows into the fixed throttling section 17. The mixed refrigerant, after being depressurized by the fixed throttling section 17, flows into the second heat-absorbing heat exchanger 15b. In the mixed refrigerant flowing into the second heat-absorbing heat exchanger 15b, due to the pressure reduction, the refrigerant desorbs from the adsorbent.

[0127] At this time, the adsorbent absorbs heat as desorption heat from the supply air passing through the first heat-absorbing heat exchanger 15a. Furthermore, if the mixed refrigerant includes a liquid refrigerant, the liquid refrigerant evaporates and absorbs heat, thereby cooling the supply air passing through the first heat-absorbing heat exchanger 15a. The remaining operations are the same as in the second embodiment.

[0128] As described above, the air conditioning unit 1b of this embodiment can cool the room by blowing the supply air cooled in the first heat-absorbing heat exchanger 15a and the second heat-absorbing heat exchanger 15b into the room.

[0129] Furthermore, the refrigeration cycle apparatus 10b of this embodiment achieves the same effects as the first and second embodiments. That is, compared to a conventional vapor compression refrigeration cycle apparatus that does not mix the adsorbent with the refrigerant, the refrigeration cycle apparatus 10b of this embodiment improves the cycle efficiency. Furthermore, it improves the reliability of refrigeration cycle apparatuses that circulate a mixed refrigerant in which the adsorbent is mixed with the refrigerant.

[0130] Furthermore, in the refrigeration cycle apparatus 10b of this embodiment, the mixed refrigerant outlet of the second heat-absorbing heat exchanger 15b is connected to the pressure-reducing side suction port 22c of the pressure-reducing side ejector 22. As a result, through the pressure-boosting effect of the pressure-reducing side ejector 22, the pressure of the mixed refrigerant in the second heat-absorbing heat exchanger 15b becomes lower than the pressure of the mixed refrigerant in the first heat-absorbing heat exchanger 15a.

[0131] Therefore, the cooling amount of the supply air in the second heat-absorbing heat exchanger 15b (i.e., the heat absorbed by the adsorbent) becomes greater than the cooling amount of the supply air in the first heat-absorbing heat exchanger 15a. Thus, in the refrigeration cycle device 10b, the supply air blown into the room can be cooled efficiently in sequence from the first heat-absorbing heat exchanger 15a to the second heat-absorbing heat exchanger 15b.

[0132] (Fourth Implementation)

[0133] In this embodiment, a variation of the refrigeration cycle apparatus 10 described in the first embodiment will be described. In the refrigeration cycle apparatus 10 of this embodiment, as... Figure 5 As shown in the overall structural diagram, compared to the first embodiment, a portion of the structure of the low-pressure side extraction section 16 has been changed, and a foreign matter filter 18 has been added.

[0134] like Figure 6 As shown, the low-pressure side extraction section 16 of this embodiment has a tapered section 16f at the lower end of the bottom cylindrical container, forming a frustum-shaped space that gradually tapers downwards. The lower space 16h of this embodiment is formed inside the tapered section 16f.

[0135] Furthermore, the mixed refrigerant inlet 16c is formed such that the refrigerant flows in along the tangential direction of the inner wall surface of the low-pressure side extraction section 16, which has a circular cross-section. The mixed refrigerant outlet 16d is formed at the center of the frustum-shaped bottom surface of the low-pressure side extraction section 16. Therefore, the lower space 16h in this embodiment constitutes a centrifugal separation section for extracting gaseous refrigerant from the mixed refrigerant by the action of centrifugal force.

[0136] Furthermore, the inner wall surface 16i of the low-pressure side extraction section 16, at least the portion forming the lower space 16h, is subjected to a surface treatment to improve the sliding properties of the adsorbent. Specifically, in this embodiment, the inner wall surface 16i is coated with a fluoropolymer resin.

[0137] A foreign object filter 18 is disposed in the refrigerant passage from the gaseous refrigerant outlet 16e of the low-pressure side extraction section 16 to the suction inlet of the compressor 11. The average opening diameter of the foreign object filter 18 is smaller than the average opening diameter of the adsorbent filter 161. In other words, the mesh size of the foreign object filter 18 is finer than the mesh size of the adsorbent filter 161. That is, the mesh size of the foreign object filter 18 is smaller than the mesh size of the adsorbent filter 161.

[0138] The remaining structure and operation of the refrigeration cycle device 10 and the air conditioning device 1 are the same as in the first embodiment. Therefore, the air conditioning device 1 according to this embodiment, like the first embodiment, is capable of cooling the room.

[0139] Furthermore, the refrigeration cycle apparatus 10 according to this embodiment can achieve the same effects as the first embodiment. That is, compared with a conventional vapor compression refrigeration cycle apparatus that does not mix the adsorbent with the refrigerant, the refrigeration cycle apparatus 10 according to this embodiment can improve the cycle efficiency. Furthermore, it can improve the reliability of refrigeration cycle apparatuses that circulate a mixed refrigerant in which the adsorbent is mixed with the refrigerant.

[0140] Here, the adsorbent contains foreign matter generated when part of its structure collapses during circulation. Furthermore, if the compressor draws in foreign matter along with the refrigerant, it may adversely affect the compressor's lifespan. In contrast, the refrigeration cycle apparatus 10 of this embodiment is equipped with a foreign matter filter 18, which prevents the compressor 11 from drawing in foreign matter.

[0141] Furthermore, in the low-pressure side extraction section 16 of this embodiment, the lower space 16h constitutes a centrifugal separation section. Thus, a low-pressure side extraction section for extracting gaseous refrigerant from a mixed refrigerant can be realized with a simple structure.

[0142] Furthermore, in the low-pressure side extraction section 16 of this embodiment, the mixed refrigerant outlet 16d is formed at the center of the frustum-shaped bottom surface of the low-pressure side extraction section 16. This allows powdered or particulate adsorbents to easily flow out from the mixed refrigerant outlet 16d.

[0143] Here, if the proportion of adsorbents in the mixed refrigerant stored in the lower space 16h of the low-pressure side extraction section 16 increases, there is a possibility that powdered or particulate adsorbents may become blocked in the lower space 16h. Furthermore, if the adsorbents become blocked in the lower space 16h, there is a possibility that the refrigeration cycle device 10 may be unable to stably perform its cooling function.

[0144] In contrast, in this embodiment, a fluoropolymer coating is applied to the inner wall surface of the low-pressure side extraction section 16 to improve the sliding properties of the adsorbent. This prevents powdery or particulate adsorbents from clogging the lower space 16h. Therefore, according to this embodiment, the reliability of the refrigeration cycle device 10 can be improved, and the refrigeration cycle device 10 can operate stably.

[0145] (Fifth implementation method)

[0146] In this embodiment, a variation of the refrigeration cycle apparatus 10 described in the first embodiment will be described. In the refrigeration cycle apparatus 10 of this embodiment, as... Figure 7 As shown in the overall structural diagram, an auxiliary adsorbent pump 27 has been added compared to the first embodiment.

[0147] The auxiliary adsorbent pump 27 is an auxiliary conveying unit that pressurizes the refrigerant contained in the mixed refrigerant flowing out of the mixed refrigerant outlet 16d from the low-pressure side extraction section 16 and conveys it to the discharge side suction port 12c side of the discharge side ejector 12.

[0148] Here, "the auxiliary adsorbent pump 27 does not increase the pressure of the refrigerant contained in the mixed refrigerant" means that, compared to the pressure of the refrigerant contained in the mixed refrigerant at the mixed refrigerant outlet 16d, the pressure of the refrigerant at the discharge-side suction port 12c is not increased in the auxiliary adsorbent pump 27. Therefore, when the auxiliary adsorbent pump 27 delivers the mixed refrigerant, the change in the packing density of the adsorbents contained in the mixed refrigerant and the resulting increase in the pressure of the surrounding gaseous refrigerant are not included in the case where the auxiliary adsorbent pump 27 increases the pressure of the refrigerant contained in the mixed refrigerant.

[0149] As the auxiliary adsorbent pump 27, an electric rotary positive displacement single-shaft eccentric screw pump, rotary pump, diaphragm pump, or similar type with minimal volume change can be used. The rotational speed (i.e., delivery capacity) of the auxiliary adsorbent pump 27 is controlled by a control signal output from the control device 20. The remaining structures of the refrigeration cycle device 10 and the air conditioning device 1 are the same as in the first embodiment.

[0150] Next, the operation of the air conditioning unit 1 in the above structure will be explained. In the refrigeration cycle device 10 of this embodiment, the control device 20 increases the delivery capacity of the auxiliary adsorbent pump 27 as the refrigerant discharge capacity of the compressor 11 increases.

[0151] The remaining operations are the same as in the first embodiment. Therefore, the air conditioning device 1 according to this embodiment, like the first embodiment, is capable of cooling the room. Furthermore, the cooling cycle device 10 according to this embodiment, like the first embodiment, can improve the cycle efficiency and reliability.

[0152] Here, in the discharge-side pressure boosting section 12f of the discharge-side injector 12, the pressure energy of the discharge refrigerant is used to increase the pressure of both the discharge-side injected refrigerant and the gaseous refrigerant contained in the mixed refrigerant drawn from the discharge-side suction port 12c. Therefore, reducing the amount of gaseous refrigerant contained in the mixed refrigerant drawn from the discharge-side suction port 12c is effective in reducing the power consumption of the compressor 11.

[0153] However, in order to transport the adsorbent contained in the mixed refrigerant flowing from the mixed refrigerant outlet 16d to the discharge-side suction port 12c by the suction effect of the discharge-side ejector 12, it is necessary to allow the gaseous refrigerant contained in the mixed refrigerant to flow, and to transport the adsorbent by the resistance of the gaseous refrigerant. Therefore, reducing the amount of refrigerant contained in the mixed refrigerant is not preferable in order to properly transport the adsorbent by the suction effect of the discharge-side ejector 12.

[0154] In contrast, the refrigeration cycle apparatus 10 of this embodiment includes an auxiliary adsorbent pump 27. Therefore, even if the amount of refrigerant in the mixed refrigerant is reduced, the adsorbent contained in the mixed refrigerant can still be transported by the conveying capacity of the auxiliary adsorbent pump 27. Thus, the amount of refrigerant in the mixed refrigerant can be reduced, thereby lowering the power consumption of the compressor 11.

[0155] Furthermore, the auxiliary adsorbent pump 27 in this embodiment does not pressurize the refrigerant contained in the mixed refrigerant. Therefore, the power consumption of the auxiliary adsorbent pump 27 can be suppressed, making it difficult to cause a deterioration in the operating efficiency due to the addition of the auxiliary adsorbent pump 27. Moreover, high sealing performance is not required for the auxiliary adsorbent pump 27. Therefore, it is difficult to cause a decrease in the reliability of the cycle due to the addition of the auxiliary adsorbent pump 27.

[0156] (Sixth Implementation Method)

[0157] In this embodiment, a variation of the refrigeration cycle apparatus 10 described in the first embodiment will be described. In the refrigeration cycle apparatus 10 of this embodiment, as... Figure 8 As shown in the explanatory diagram, compared to the first embodiment, the positional relationship between the low-pressure side extraction section 16 and the discharge side ejector 12 is clarified, and an adsorbent flow adjustment valve 28 is added.

[0158] In the discharge-side ejector 12 and low-pressure side extraction section 16 of this embodiment, a mixed refrigerant outlet 16d of the low-pressure side extraction section 16 is positioned above the discharge-side suction port 12c of the discharge-side ejector 12. Therefore, the discharge-side ejector 12 and low-pressure side extraction section 16 are configured such that the mixed refrigerant flowing out of the mixed refrigerant outlet 16d can flow through the mixed refrigerant passage 23 under the action of gravity and move towards the discharge-side suction port 12c.

[0159] The adsorbent flow regulating valve 28 is a powder flow regulating unit that adjusts the flow rate of the adsorbent flowing through the mixed refrigerant passage 23. The adsorbent flow regulating valve 28 does not block the mixed refrigerant passage 23, but 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.

[0160] As the adsorbent flow regulating valve 28, an electrically operated gate valve or similar device that operates with relatively small driving force can be used. The opening degree (opening area of ​​the passage cross-sectional area) of the adsorbent flow regulating valve 28 is controlled by a control signal output from the control device 20. The remaining structure of the refrigeration cycle device 10 and the air conditioning device 1 is the same as in the first embodiment.

[0161] Next, the operation of the air conditioning unit 1 in the above structure will be explained. In the refrigeration cycle device 10 of this embodiment, the control device 20 controls the operation of the adsorbent flow regulating valve 28 in such a way that the cross-sectional area of ​​the mixed refrigerant passage 23 increases as the refrigerant discharge capacity of the compressor 11 increases.

[0162] The remaining operations are the same as in the first embodiment. Therefore, the air conditioning device 1 according to this embodiment, like the first embodiment, is capable of cooling the room. Furthermore, the cooling cycle device 10 according to this embodiment, like the first embodiment, can improve the cycle efficiency and reliability.

[0163] Furthermore, in the refrigeration cycle apparatus 10 of this embodiment, the adsorbent contained in the mixed refrigerant flowing out of the mixed refrigerant outlet 16d can be transported to the discharge-side suction port 12c of the discharge-side ejector 12 by gravity. Therefore, similar to the fifth embodiment, the amount of refrigerant contained in the mixed refrigerant can be reduced, thereby reducing the power consumption of the compressor 11.

[0164] Furthermore, in the refrigeration cycle apparatus 10 of this embodiment, because it is equipped with an adsorbent flow regulating valve 28, the amount of adsorbent drawn from the discharge-side suction port 12c of the discharge-side ejector 12 can be adjusted to an appropriate amount. Moreover, since the adsorbent flow regulating valve 28 does not block the refrigerant mixing passage 23, wear on the sliding parts and sealing parts is less likely to occur. Therefore, it is less likely that the reliability of the cycle will be reduced due to the addition of the adsorbent flow regulating valve 28.

[0165] (Seventh Implementation)

[0166] In this embodiment, a variation of the refrigeration cycle apparatus 10 described in the first embodiment will be described. In the refrigeration cycle apparatus 10 of this embodiment, as... Figure 9 As shown in the overall structural diagram, compared to the first embodiment, an adsorbent heat exchanger 29 has been added.

[0167] The adsorbent heat exchanger 29 is an adsorbent heat exchange section that allows 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 to 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 to exchange heat.

[0168] More specifically, the adsorbent heat exchanger 29 of this embodiment allows the adsorbent contained in the mixed refrigerant flowing through the mixed refrigerant outlet of the heat dissipation heat exchanger 13 to the inlet of the electric expansion valve 14 to exchange heat with the adsorbent contained in the mixed refrigerant flowing through the mixed refrigerant passage 23. That is, the adsorbent heat exchanger 29 of this embodiment allows heat exchange between the adsorbent in the mixed refrigerant flowing through the mixed refrigerant passage 23 and the adsorbent in the mixed refrigerant flowing through the mixed refrigerant passage 23. Figure 9 The adsorbent contained in the mixed refrigerant flowing in region H1 exchanges heat with the adsorbent contained in the mixed refrigerant flowing in region L1.

[0169] Here, in the adsorbent heat exchanger 29, a mixed refrigerant containing powdered or particulate adsorbents is circulated. Therefore, the adsorbent heat exchanger 29 is preferably a structure with low flow resistance. Therefore, in this embodiment, as... Figure 10 As shown, a heat exchange section is formed by connecting a high-temperature side passage 29a and a low-temperature side passage 29b, which are formed by refrigerant piping made of metal, so that the adsorbents contained in the mixed refrigerant flowing in each passage can exchange heat with each other.

[0170] High-temperature side passage 29a is a refrigerant passage through which the mixed refrigerant flowing out of the mixed refrigerant outlet of the heat dissipation heat exchanger 13 flows. Low-temperature side passage 29b is a refrigerant passage through which the mixed refrigerant flowing out of the mixed refrigerant outlet of the heat absorption heat exchanger 15 flows. In the adsorber heat exchanger 29, as... Figure 10 As shown, a heat exchange section with a so-called counterflow pattern is formed, in which the flow direction of the adsorbent flowing in the high-temperature side passage 29a is opposite to the flow direction of the adsorbent flowing in the low-temperature side passage 29b.

[0171] The remaining structure and operation of the refrigeration cycle device 10 and the air conditioning device 1 are the same as in the first embodiment. Therefore, the air conditioning device 1 according to this embodiment, like the first embodiment, is capable of cooling the room. Furthermore, the refrigeration cycle device 10 according to this embodiment, like the first embodiment, can improve the cycle efficiency and reliability.

[0172] Here, as a powdery or particulate solid adsorbent, its volume and temperature remain unchanged even when the surrounding pressure changes. Therefore, if the low-temperature adsorbent flows into the heat exchanger 13, the adsorption heat dissipated in the heat exchanger 13 is not only dissipated to the outside air but also to the adsorbent itself, and is consumed to raise the temperature of the adsorbent.

[0173] Similarly, if a high-temperature adsorbent flows into the heat exchanger 15, the desorption heat absorbed in the heat exchanger 15 is consumed not only from the supply air but also from the adsorbent itself, thus lowering the temperature of the adsorbent. As a result, the cooling capacity of the supply air may not be sufficiently improved in the air conditioning unit 1.

[0174] In contrast, the refrigeration cycle apparatus 10 of this embodiment includes an adsorbent heat exchanger 29. In the adsorbent heat exchanger 29, heat from the adsorbent flowing into the heat-absorbing heat exchanger 15 can be transferred to the adsorbent flowing into the heat-dissipating heat exchanger 13. Furthermore, the temperature of the adsorbent flowing into the heat-dissipating heat exchanger 13 can be increased, while the temperature of the adsorbent flowing into the heat-absorbing heat exchanger 15 can be decreased.

[0175] Therefore, the change in sensible heat of the adsorbate in the heat exchanger 13 for heat dissipation can be suppressed, increasing the amount of heat dissipated to the outside air. Furthermore, the change in sensible heat of the adsorbate in the heat exchanger 15 for heat absorption can be suppressed, increasing the amount of heat absorbed from the supply air. As a result, the cooling capacity of the supply air can be significantly improved in the air conditioning unit 1.

[0176] Furthermore, in this embodiment, it is explained that the method of using... Figure 9 The adsorbent contained in the mixed refrigerant circulating in region H1 and in Figure 9 An example of an adsorbent heat exchanger 29 is provided, in which the adsorbents contained in the mixed refrigerant circulating in the L1 region exchange heat, but the adsorbent heat exchange section is not limited to this.

[0177] In the adsorbent heat exchange section, if the heat of the adsorbent flowing into the heat-absorbing heat exchanger 15 can be moved to the adsorbent flowing into the heat-dissipating heat exchanger 13, then different combinations of adsorbents can also exchange heat with each other.

[0178] For example, it can also be made in Figure 9 Any one of the adsorbents contained in the mixed refrigerant flowing in region H1 and region H2, exchanges heat with any one of the adsorbents contained in the mixed refrigerant flowing in region L1, region L2, and region L3.

[0179] Region L2 shows the flow path from the outlet of the discharge-side booster section 12f of the discharge-side injector 12 to the mixed refrigerant inlet of the heat exchanger 13. Region L3 shows the flow path from the mixed refrigerant outlet of the heat-absorbing heat exchanger 15 to the mixed refrigerant inlet 16c of the low-pressure side extraction section 16. Region H2 shows the flow path from the outlet of the electric expansion valve 14 to the mixed refrigerant inlet of the heat-absorbing heat exchanger 15.

[0180] In the refrigeration cycle device 10, in order to improve the efficiency of heat exchange between the adsorbents and suppress unnecessary heat exchange between the gaseous refrigerants contained in the mixed refrigerant, it is preferable to allow heat exchange between the adsorbents contained in the mixed refrigerant flowing in the L1 region and the adsorbents contained in the mixed refrigerant flowing in the H1 region in the adsorbent heat exchanger 29.

[0181] (Eighth Implementation)

[0182] In this embodiment, a variation of the refrigeration cycle apparatus 10a described in the second embodiment will be explained. For example... Figure 11 As shown in the overall structural diagram, the refrigeration cycle device 10a of this embodiment, compared with the second embodiment, adds an adsorbent heat exchanger 29, which is the same as that of the seventh embodiment.

[0183] The adsorbent heat exchanger 29 of this embodiment allows 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 throttling section 17 to exchange heat with the adsorbent contained in the mixed refrigerant flowing through the mixed refrigerant passage 23. That is, the adsorbent heat exchanger 29 of this embodiment allows heat exchange in the mixed refrigerant flowing through the mixed refrigerant passage 23. Figure 11 The adsorbent contained in the mixed refrigerant circulating in the H3 region and in Figure 11 The mixed refrigerant circulating in the L1 region undergoes heat exchange with the adsorbent contained therein.

[0184] The remaining structure and operation of the refrigeration cycle device 10a and the air conditioning device 1a are the same as in the second embodiment. Therefore, the air conditioning device 1a according to this embodiment, like the second embodiment, is capable of cooling the room. Furthermore, the refrigeration cycle device 10a according to this embodiment, like the second embodiment, can improve the cycle efficiency and reliability.

[0185] In addition, in the refrigeration cycle apparatus 10a of this embodiment, since it is equipped with an adsorbent heat exchanger 29, the cooling capacity of the supply air can be significantly improved, similar to that of the seventh embodiment.

[0186] Furthermore, in this embodiment, it is explained that the method of using... Figure 11 The adsorbent contained in the mixed refrigerant circulating in the H3 region and in Figure 11 An example of an adsorbent heat exchanger 29 is provided, in which the adsorbents contained in the mixed refrigerant circulating in the L1 region exchange heat, but the adsorbent heat exchange section is not limited to this.

[0187] For example, it can also be made in Figure 11 Any one of the adsorbents contained in the mixed refrigerant flowing in region H1, region H3, region H4, and region H5, exchanges heat with any one of the adsorbents contained in the mixed refrigerant flowing in region L1, region L2, and region L3.

[0188] Region H3 shows the flow path from the mixed refrigerant outlet 26d of the high-pressure side extraction section 26 to the inlet of the fixed throttling section 17. Region H4 shows the flow path from the outlet of the fixed throttling section 17 to the pressure-reducing side suction port 22c of the pressure-reducing side ejector 22. Region H5 shows the flow path from the outlet of the pressure-reducing side boosting section 22f of the pressure-reducing side ejector 22 to the mixed refrigerant inlet of the heat exchanger 15 for heat absorption.

[0189] In the refrigeration cycle device 10a, in order to improve the efficiency of heat exchange between the adsorbents and suppress unnecessary heat exchange between the gaseous refrigerants contained in the mixed refrigerant, it is preferable to allow the adsorbent contained in the mixed refrigerant flowing in the L1 region to exchange heat with the adsorbent contained in the mixed refrigerant flowing in the H3 region or the H4 region in the adsorbent heat exchanger 29.

[0190] (Ninth Implementation)

[0191] In this embodiment, a variation of the refrigeration cycle device 10b described in the third embodiment will be explained. For example... Figure 12As shown in the overall structural diagram, the refrigeration cycle device 10b of this embodiment, compared with the third embodiment, adds an adsorbent heat exchanger 29 that is the same as that of the seventh embodiment.

[0192] The adsorbent heat exchanger 29 in this embodiment is similar to that in the eighth embodiment, causing the adsorbent heat exchanger 29 to... Figure 12 The adsorbent contained in the mixed refrigerant circulating in the H3 region and in Figure 12 The mixed refrigerant circulating in the L1 region undergoes heat exchange with the adsorbent contained therein.

[0193] The remaining refrigeration cycle device 10b and air conditioning device 1b have the same structure and operation as in the third embodiment. Therefore, the air conditioning device 1b according to this embodiment, like in the third embodiment, is capable of cooling the room. Furthermore, the refrigeration cycle device 10b according to this embodiment, like in the third embodiment, can improve the cycle efficiency and reliability.

[0194] In addition, in the refrigeration cycle device 10b of this embodiment, since it is equipped with an adsorbent heat exchanger 29, the cooling capacity of the supply air can be significantly improved, similar to that of the seventh embodiment.

[0195] Furthermore, in this embodiment, it is explained that the method of using... Figure 12 The adsorbent contained in the mixed refrigerant circulating in the H3 region and in Figure 12 An example of an adsorbent heat exchanger 29 is provided, in which the adsorbents contained in the mixed refrigerant circulating in the L1 region exchange heat, but the adsorbent heat exchange section is not limited to this.

[0196] For example, it can also be made in Figure 12 Any one of the adsorbents contained in the mixed refrigerant flowing in region H1, region H3, and region H6, exchanges heat with any one of the adsorbents contained in the mixed refrigerant flowing in region L1, region L2, and region L3.

[0197] Region H6 illustrates the flow path from the outlet of the fixed throttling section 17 to the mixed refrigerant inlet of the second heat exchanger 15b.

[0198] In this embodiment, in order to minimize the impact of temperature changes of the gaseous refrigerant in the mixed refrigerant on the cooling capacity, it is preferable to allow the adsorbent contained in the mixed refrigerant flowing in the L1 region to exchange heat with the adsorbent contained in the mixed refrigerant flowing in the H3 region or the H6 region in the adsorbent heat exchanger 29.

[0199] (Tenth Implementation)

[0200] In this embodiment, a variation of the refrigeration cycle apparatus 10 described in the fourth embodiment will be described. In the refrigeration cycle apparatus 10 of this embodiment, as... Figure 13 As shown in the explanatory diagram, compared to the first embodiment, it has a vibration transmission rod 16j.

[0201] The vibration transmission rod 16j is a vibration transmission part that transmits the vibration of the compressor 11 to the low-pressure side extraction section 16. The vibration transmission rod 16j is a rigid metal body that directly connects both the compressor 11 and the low-pressure side extraction section 16. Therefore, the vibration transmission rod 16j is included in the vibration part that causes the low-pressure side extraction section 16 to vibrate. In addition, the compressor 11 in this embodiment also functions as a vibration part.

[0202] The remaining structure and operation of the refrigeration cycle device 10 and the air conditioning device 1 are the same as in the first embodiment. Therefore, the air conditioning device 1 according to this embodiment, like the first embodiment, is capable of cooling the room. Furthermore, the refrigeration cycle device 10 according to this embodiment, like the first embodiment, can improve the cycle efficiency and reliability.

[0203] 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 suppress the blockage of powdery or particulate adsorbents in the lower space 16h.

[0204] This disclosure is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of this disclosure.

[0205] In the above embodiments, examples of applying the refrigeration cycle devices 10, 10a, and 10b of this disclosure to air conditioning devices have been described, but the application of the refrigeration cycle devices 10, 10a, and 10b of this disclosure is not limited thereto. For example, they can also be applied to vehicle air conditioning devices, refrigeration devices, and cold storage devices.

[0206] Furthermore, in the above-described embodiments, an example was described in which the heat of the mixed refrigerant in the heat dissipation section is dissipated to the outside air, and the heat absorption section is described in which the mixed refrigerant absorbs heat from the supply air, which is the object to be cooled. However, this is not a limitation. It is also possible to dissipate the heat of the mixed refrigerant in the heat dissipation section to the object to be heated, and to absorb heat from the outside air in the heat absorption section. In this case, it can also be applied to heating devices that heat supply air, which is the object to be heated, and hot water supply devices that heat domestic water, etc., which are the objects to be heated.

[0207] The structure of the refrigeration cycle device is not limited to the structure disclosed in the above embodiments.

[0208] In the above embodiments, an example of using a discharge-side ejector 12 as a discharge-side conveying section has been described, but it is not limited to this. For example, as a discharge-side conveying section, an expander that converts the pressure energy of the refrigerant into mechanical energy for conveying the mixed refrigerant may also be used. The same applies to the pressure-reducing side conveying section.

[0209] Furthermore, in the second and third embodiments described above, examples using an electrically operated expansion valve 14a were described, but the electrically operated expansion valve 14a is not a necessary structure. Therefore, the refrigerant separated in the high-pressure side extraction section 26 can also flow directly into the pressure-reducing side nozzle section 22a of the pressure-reducing side injector 22.

[0210] Furthermore, the electric expansion valve 14a and the pressure-reducing injector 22 can be integrated. In this case, a needle-shaped or conical valve core can be arranged in the passage of the pressure-reducing nozzle section 22a of the pressure-reducing injector 22, and the same function as the electric expansion valve 14a can be achieved by displacing the valve core.

[0211] Furthermore, in the fourth embodiment described above, an example of using a fluoropolymer coating to improve the sliding properties of the inner wall surface of the low-pressure side extraction section 16 was given, but this is not a limitation. If the sliding properties of the inner wall surface of the low-pressure side extraction section 16 can be improved, titanium oxide coating, nickel-PTFE composite electroplating, ultrasonic surface polishing, etc., may also be used.

[0212] Furthermore, in the tenth embodiment described above, an example of a vibrating section being formed by a compressor 11 and a vibration transmission rod 16j was given, but it is not limited to this. For example, other vehicle-mounted devices that generate vibration during operation may also form the vibrating section. For example, an ultrasonic vibration device may also form the vibrating section. In this case, the ultrasonic vibration device, which serves as the vibrating section, may be directly installed in the low-pressure side extraction section 16, eliminating the need for the vibration transmission rod 16j.

[0213] Furthermore, in the tenth embodiment described above, an example was given of transmitting the vibration of the compressor 11 to the low-pressure side extraction section 16 via the vibration transmission rod 16j, but this is not a limitation. For example, the vibration of the compressor 11 can also be transmitted to the low-pressure side extraction section 16 via a refrigerant pipe connecting the gaseous refrigerant outlet 16e of the low-pressure side extraction section 16 and the suction port of the compressor 11.

[0214] Furthermore, the vibration transmission rod 16j is not limited to a rigid metal body, but can also be formed of an elastic material. Moreover, the vibration transmission rod 16j can also function as a frequency filter, transmitting vibrations at frequencies that effectively prevent blockage of the adsorbent and attenuating vibrations at other frequencies.

[0215] Alternatively, the refrigeration cycle devices 10a and 10b may also include a vibrating part for the high-pressure side extraction section that vibrates the high-pressure side extraction section 26.

[0216] Furthermore, while the above embodiments illustrate the use of metal-organic structures as adsorbents, the method is not limited to this. For example, activated carbon or hydrates can also be used as adsorbents.

[0217] Furthermore, in the above embodiments, an example of using carbon dioxide as the refrigerant in refrigeration cycle devices 10, 10a, and 10b was described, but it is not a limitation. For example, R1234yf, R134a, R600a, R410A, R404A, R32, R407C, R290 (propane), ammonia, or mixtures thereof may also be used as refrigerants.

[0218] Furthermore, in the space 16a below the low-pressure side extraction section 16 and the space 26a below the high-pressure side extraction section 26 of the above-described embodiment, a gas-liquid separation section can also be applied using an impact method where the mixed refrigerant is decelerated by colliding with an impact plate, and the denser liquid refrigerant falls downwards. Alternatively, a surface tension type gas-liquid separation section can be applied where the liquid refrigerant is attached to a corrugated attachment plate for gas-liquid separation.

[0219] The operating mode of the refrigeration cycle device is not limited to the operating mode disclosed in the above embodiments.

[0220] In the above embodiment, the low-pressure side extraction section 16 for extracting gaseous refrigerant from the mixed refrigerant has been described. However, the refrigerant extracted by the low-pressure side extraction section 16 is not limited to saturated gaseous refrigerant or gaseous refrigerant with superheat. For example, it may also be a gas-liquid two-phase refrigerant with a relatively high dryness and containing a moderate amount of liquid refrigerant for the lubrication of the compressor 11.

[0221] In the above embodiments, the state of the refrigerant discharged from the compressor 11 is not described, but the state of the discharged refrigerant varies depending on the type of refrigerant, the outside air temperature, etc. For example, there may be a case where the pressure of the discharged refrigerant is above the critical pressure of the refrigerant, or there may be a case where the pressure of the discharged refrigerant is below the critical pressure of the refrigerant, or ...

[0222] In the above embodiment, the state of the refrigerant in the mixed refrigerant flowing out of the discharge-side booster section 12f of the discharge-side injector 12 is not described. However, the state of the refrigerant in the mixed refrigerant flowing out of the discharge-side booster section 12f of the discharge-side injector 12 varies depending on the type of refrigerant, the outside air temperature, etc. For example, the state of the refrigerant in the mixed refrigerant flowing out of the discharge-side booster section 12f may be supercritical or subcritical.

[0223] In the above embodiments, detailed information regarding the state of the mixed refrigerant flowing out of the heat exchanger 13 is not described. However, the state of the mixed refrigerant flowing out of the heat exchanger 13 varies depending on the type of refrigerant, the outside air temperature, etc. For example, the mixed refrigerant flowing out of the heat exchanger 13 may be in a supercritical state, or it may be in a subcritical state as a liquid refrigerant, a gas-liquid two-phase refrigerant, or a gaseous refrigerant, depending on the type of refrigerant and the outside air temperature.

[0224] In other words, the mixed refrigerant flowing out of the heat exchanger 13 for heat dissipation may be a mixed refrigerant containing adsorbents in a supercritical state, a mixed refrigerant containing adsorbents in a liquid phase refrigerant, a mixed refrigerant containing adsorbents in a gas-liquid two-phase refrigerant with low specific enthalpy, or a mixed refrigerant containing adsorbents in a gas phase refrigerant, depending on the type of refrigerant and the outside air temperature.

[0225] In the above embodiments, an example was described where the mixed refrigerant flowing out of the heat exchanger 15 was a mixed refrigerant containing adsorbents in a gas-liquid two-phase refrigerant with a high specific enthalpy, but this is not a limitation. For example, depending on the type of refrigerant, the outside air temperature, etc., there may be cases where it is a mixed refrigerant containing adsorbents in a liquid phase refrigerant or a mixed refrigerant containing adsorbents in a gas phase refrigerant.

[0226] The mechanisms disclosed in the above embodiments can also be appropriately combined within the scope of what is feasible.

[0227] For example, the low-pressure side extraction section 16 with a tapered portion 16f described in the fourth embodiment can also 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, etc., can also have a structure with a tapered portion and a centrifugal separation portion, similar to the low-pressure side extraction section 16 described in the fourth embodiment. Moreover, the inner wall surface of the high-pressure side extraction section 26 can also be subjected to a surface treatment to improve the sliding properties of the adsorbent, similar to the fourth embodiment.

[0228] Furthermore, the configuration of the foreign matter filter 18 described in the fourth embodiment is not limited to the refrigerant passage from the gaseous refrigerant outlet 16e of the low-pressure side extraction section 16 to the suction port of the compressor 11. For example, it may be configured in the refrigerant passage from the discharge port of the compressor 11 to the inlet of the discharge side nozzle section 12a of the discharge side injector 12. As a result, it is possible to suppress the mixing of foreign matter into the discharge side nozzle section 12a.

[0229] For example, it can also be configured in the refrigerant passage from the refrigerant outlet 26e of the high-pressure side extraction section 26 to the electric expansion valve 14a. This prevents foreign matter from entering the electric expansion valve 14a.

[0230] For example, it can be configured in the refrigerant passage from the outlet of the electric expansion valve 14a to the inlet of the pressure-reducing nozzle section 22a of the pressure-reducing injector 22. This prevents foreign matter from entering the pressure-reducing nozzle section 22a. Of course, the configuration of the foreign matter filter 18 is not limited to one location and can be configured in multiple locations.

[0231] Alternatively, the auxiliary conveying unit described in the fifth embodiment may also be applied to the refrigeration cycle devices 10, 10a, and 10b described in the second to fourth and seventh to ninth embodiments.

[0232] Alternatively, the positional relationship between the low-pressure side extraction section 16 and the discharge side ejector 12, as well as the adsorbent flow adjustment valve, described in the sixth embodiment, can be applied to the refrigeration cycle devices 10, 10a, and 10b described in the second to fourth and seventh to ninth embodiments.

[0233] Alternatively, the vibration unit described in the tenth embodiment may be applied to the refrigeration cycle devices 10, 10a, and 10b described in the second to ninth embodiments.

[0234] The features of the refrigeration cycle apparatus disclosed in this specification are shown below.

[0235] (Project 1)

[0236] A refrigeration cycle apparatus that circulates a mixed refrigerant containing an adsorbent, wherein the adsorbent adsorbs and desorbs the refrigerant, comprises:

[0237] Low-pressure side extraction section (16) extracts the refrigerant from the mixed refrigerant;

[0238] The compression section (11) draws in the refrigerant extracted by the low-pressure side extraction section, compresses the refrigerant, and discharges it.

[0239] Discharge side conveying section (12) uses the pressure energy of the discharged refrigerant discharged from the compression section to convey the mixed refrigerant flowing out of the low-pressure side extraction section to the discharge refrigerant side;

[0240] Heat dissipation section (13) that dissipates heat from the mixed refrigerant flowing out from the discharge side delivery section;

[0241] A refrigerant pressure reducing section (14, 17) for reducing the pressure of the refrigerant flowing from the heat dissipation section; and

[0242] The heat-absorbing section (15, 15a, 15b) desorbs the refrigerant from the adsorbent contained in the mixed refrigerant after it has been depressurized by the mixed refrigerant depressurization section, causing the mixed refrigerant to flow out to the mixed refrigerant inlet side of the low-pressure side extraction section.

[0243] (Project 2)

[0244] According to the refrigeration cycle device described in Project 1,

[0245] The discharge-side delivery section is a discharge-side injector (12) having a discharge-side nozzle section (12a) and a discharge-side main body section (12b). The discharge-side nozzle section reduces the pressure of the discharged refrigerant, and the discharge-side main body section has a discharge-side suction port (12c) for attracting the mixed refrigerant flowing out from the low-pressure side extraction section.

[0246] A discharge-side mixing section (12e) is formed in the discharge-side main body, which mixes the discharge-side sprayed refrigerant injected from the discharge-side nozzle with the mixed refrigerant drawn from the discharge-side suction port.

[0247] (Project 3)

[0248] According to the refrigeration cycle device described in Project 2,

[0249] It is equipped with an auxiliary conveying unit (27) that does not pressurize the refrigerant contained in the mixed refrigerant flowing out from the low-pressure side extraction unit, but conveys the mixed refrigerant to the discharge side suction port side.

[0250] (Project 4)

[0251] The refrigeration cycle device described in any one of items 1 to 3 has the following features:

[0252] High-pressure side extraction section (26), which extracts the refrigerant from the mixed refrigerant flowing out of the heat dissipation section; and

[0253] The pressure-reducing side delivery section (22) uses the pressure energy of the refrigerant extracted by the high-pressure side extraction section to deliver the mixed refrigerant flowing out of the high-pressure side extraction section to the refrigerant side extracted by the high-pressure side extraction section.

[0254] (Project 5)

[0255] According to the refrigeration cycle device described in Project 4,

[0256] The pressure-reducing side delivery section is a pressure-reducing side ejector (22) having a pressure-reducing side nozzle section (22a) and a pressure-reducing side main body section (22b). The pressure-reducing side nozzle section reduces the pressure of the refrigerant extracted from the high-pressure side extraction section, and the pressure-reducing side main body section is formed with a pressure-reducing side suction port (22c) for attracting the mixed refrigerant flowing out from the high-pressure side extraction section.

[0257] A pressure-reducing side mixing section (22e) is formed in the pressure-reducing side main body, which mixes the pressure-reducing side sprayed refrigerant injected from the pressure-reducing side nozzle with the mixed refrigerant drawn from the pressure-reducing side suction port.

[0258] (Project 6)

[0259] According to the refrigeration cycle device described in Project 5,

[0260] The mixed refrigerant outlet of the heat absorption section (15b) is connected to the pressure-reducing side suction port.

[0261] (Project 7)

[0262] According to the refrigeration cycle device described in any one of items 1 to 6,

[0263] The low-pressure side extraction section has an adsorbent filter section (161) that allows the refrigerant separated from the mixed refrigerant to pass through, and at least prohibits the adsorbent from passing through.

[0264] (Project 8)

[0265] According to the refrigeration cycle device described in Project 7,

[0266] It is equipped with a foreign matter filter (18) that allows the refrigerant extracted by the low-pressure side extraction section to pass through, while preventing foreign matter contained in the refrigerant from passing through.

[0267] The average opening diameter of the foreign matter filtration section is smaller than the average opening diameter of the adsorbent filtration section.

[0268] (Project 9)

[0269] According to the refrigeration cycle device described in any one of items 1 to 8,

[0270] The low-pressure side extraction section has a centrifugal separation section (16h), which separates the refrigerant and the adsorbent by centrifugal force.

[0271] (Project 10)

[0272] According to the refrigeration cycle device described in any one of items 1 to 9,

[0273] The inner wall surface of the low-pressure side extraction section is treated with a surface finish to improve sliding properties.

[0274] (Project 11)

[0275] According to the refrigeration cycle devices described in items 1 to 10,

[0276] It has a vibration section that causes the low-pressure side extraction section to vibrate.

[0277] (Project 12)

[0278] According to the refrigeration cycle device described in any one of items 1 to 11,

[0279] The device includes an adsorbent heat exchange section that allows 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 to exchange heat with 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.

[0280] (Project 13)

[0281] According to the refrigeration cycle device described in any one of items 1 to 12,

[0282] The adsorbent comprises a metal-organic structure having metal ions and organic ligands.

[0283] This disclosure is based on embodiments, but should be understood as not being limited to those embodiments or structures. This disclosure also includes various modifications or variations within the same scope. Furthermore, various combinations or methods, including only one element therein, or more or fewer other combinations or methods, also fall within the scope and spirit of this disclosure.

Claims

1. A refrigeration cycle apparatus for circulating a mixed refrigerant containing an adsorbent, wherein the adsorbent adsorbs and desorbs the refrigerant, characterized in that, have: Low-pressure side extraction section (16) extracts the refrigerant from the mixed refrigerant; The compression section (11) draws in the refrigerant extracted by the low-pressure side extraction section, compresses the refrigerant, and discharges it. Discharge side conveying section (12) uses the pressure energy of the discharged refrigerant discharged from the compression section to convey the mixed refrigerant flowing out of the low-pressure side extraction section to the discharge refrigerant side; Heat dissipation section (13) that dissipates heat from the mixed refrigerant flowing out from the discharge side delivery section; A refrigerant pressure reducing section (14, 17) for reducing the pressure of the refrigerant flowing from the heat dissipation section; and The heat-absorbing section (15, 15a, 15b) desorbs the refrigerant from the adsorbent contained in the mixed refrigerant after it has been depressurized by the mixed refrigerant depressurization section, causing the mixed refrigerant to flow out to the mixed refrigerant inlet side of the low-pressure side extraction section.

2. The refrigeration cycle device according to claim 1, characterized in that, The discharge-side delivery section is a discharge-side injector (12) having a discharge-side nozzle section (12a) and a discharge-side main body section (12b). The discharge-side nozzle section reduces the pressure of the discharged refrigerant, and the discharge-side main body section has a discharge-side suction port (12c) for attracting the mixed refrigerant flowing out from the low-pressure side extraction section. A discharge-side mixing section (12e) is formed in the discharge-side main body, which mixes the discharge-side sprayed refrigerant injected from the discharge-side nozzle with the mixed refrigerant drawn from the discharge-side suction port.

3. The refrigeration cycle device according to claim 2, characterized in that, It is equipped with an auxiliary conveying unit (27) that does not pressurize the refrigerant contained in the mixed refrigerant flowing out from the low-pressure side extraction unit, but conveys the mixed refrigerant to the discharge side suction port side.

4. The refrigeration cycle device according to claim 1, characterized in that, have: High-pressure side extraction section (26), which extracts the refrigerant from the mixed refrigerant flowing out of the heat dissipation section; and The pressure-reducing side delivery section (22) uses the pressure energy of the refrigerant extracted by the high-pressure side extraction section to deliver the mixed refrigerant flowing out of the high-pressure side extraction section to the refrigerant side extracted by the high-pressure side extraction section.

5. The refrigeration cycle device according to claim 4, characterized in that, The pressure-reducing side delivery section is a pressure-reducing side ejector (22) having a pressure-reducing side nozzle section (22a) and a pressure-reducing side main body section (22b). The pressure-reducing side nozzle section reduces the pressure of the refrigerant extracted from the high-pressure side extraction section, and the pressure-reducing side main body section is formed with a pressure-reducing side suction port (22c) for attracting the mixed refrigerant flowing out from the high-pressure side extraction section. A pressure-reducing side mixing section (22e) is formed in the pressure-reducing side main body, which mixes the pressure-reducing side sprayed refrigerant injected from the pressure-reducing side nozzle with the mixed refrigerant drawn from the pressure-reducing side suction port.

6. The refrigeration cycle device according to claim 5, characterized in that, The mixed refrigerant outlet of the heat absorption section (15b) is connected to the pressure-reducing side suction port.

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

8. The refrigeration cycle device according to claim 7, characterized in that, It is equipped with a foreign matter filter (18) that allows the refrigerant extracted by the low-pressure side extraction section to pass through, while preventing foreign matter contained in the refrigerant from passing through. The average opening diameter of the foreign matter filtration section is smaller than the average opening diameter of the adsorbent filtration section.

9. The refrigeration cycle device according to claim 1, characterized in that, The low-pressure side extraction section has a centrifugal separation section (16h), which separates the refrigerant and the adsorbent by centrifugal force.

10. The refrigeration cycle device according to claim 1, characterized in that, The inner wall surface of the low-pressure side extraction section is treated with a surface finish to improve sliding properties.

11. The refrigeration cycle device according to claim 1, characterized in that, It has a vibration section that causes the low-pressure side extraction section to vibrate.

12. The refrigeration cycle device according to claim 1, characterized in that, The device includes an adsorbent heat exchange section (29) that allows 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 to exchange heat with 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. The refrigeration cycle apparatus according to any one of claims 1 to 11, characterized in that, The adsorbent comprises a metal-organic structure having metal ions and organic ligands.

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