Refrigeration cycle apparatus

Abstract

A refrigeration cycle apparatus for circulating a mixed refrigerant in which an adsorbent is mixed with a refrigerant comprises: pressure-increasing parts (11, 12, 16); a heat-radiating part (13) for radiating heat of the mixed refrigerant, which has been pressurized by the pressure-increasing parts (11, 12, 16), to a heat radiation target; pressure-reducing parts (14, 17, 22, 26); and heat-absorbing parts (15, 15a, 15b) for causing the mixed refrigerant, which has been depressurized by the pressure-reducing parts (14, 17, 22, 26), to absorb heat from a heat absorption target. The refrigerant includes at least a first refrigerant and a second refrigerant. The adsorbent adsorbs and desorbs the first refrigerant. The heat-radiating part (13) condenses the second refrigerant. The heat-absorbing parts (15, 15a, 15b) evaporate the second refrigerant.

Description

Refrigeration Cycle Equipment CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application is based on Japanese Patent Application No. 2024-086132 filed on May 28, 2024, the contents of which are incorporated herein by reference.

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

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

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

[0005] Furthermore, the refrigeration cycle device of Patent Document 1 uses carbon dioxide as the refrigerant, and therefore, under normal operating conditions, the refrigerant that is not adsorbed by the adsorbent circulates in the cycle in a gaseous state.

[0006] International Publication No. 2024 / 004971

[0007] However, as in the refrigeration cycle device of Patent Document 1, the refrigerant circulating in the cycle without being adsorbed by the adsorbent is in a gas phase, so when the heat of adsorption is radiated to the heat dissipation object in the heat dissipation section, heat transfer by condensation heat transfer, as in a typical vapor compression refrigeration cycle, cannot be performed.Similarly, when the heat of desorption from the heat absorption object in the heat absorption section, heat transfer by boiling heat transfer, as in a typical vapor compression refrigeration cycle, cannot be performed.

[0008] Therefore, in the refrigeration cycle device of Patent Document 1, the heat transfer coefficient between the mixed refrigerant and the heat radiating section and the heat transfer coefficient between the mixed refrigerant and the heat absorbing section are lower than those in a normal vapor compression refrigeration cycle. As a result, in the refrigeration cycle device of Patent Document 1, the amount of heat radiated by the mixed refrigerant in the heat radiating section and the amount of heat absorbed by the mixed refrigerant in the heat absorbing section may be insufficient, and the effect of improving operating efficiency by mixing the refrigerant with the adsorbent may not be fully achieved.

[0009] In view of the above, the present disclosure aims to provide a refrigeration cycle device that circulates a mixed refrigerant in which an adsorbent is mixed with a refrigerant, and that can achieve a sufficient improvement in operating efficiency.

[0010] A refrigeration cycle device according to a first aspect of the present disclosure is a refrigeration cycle device that circulates a mixed refrigerant obtained by mixing a refrigerant and an adsorbent. The refrigeration cycle device includes a pressure increasing unit, a heat radiating unit, a pressure reducing unit, and a heat absorbing unit.

[0011] The pressure increasing unit increases the pressure of the mixed refrigerant. The heat dissipation unit dissipates heat contained in the mixed refrigerant pressurized by the pressure increasing unit to a heat dissipation object. The pressure reducing unit depressurizes the mixed refrigerant flowing out from the heat dissipation unit. The heat absorption unit causes the mixed refrigerant depressurized by the pressure reducing unit to absorb heat contained in the heat absorption object.

[0012] The refrigerant includes at least a first refrigerant and a second refrigerant. The adsorbent adsorbs and desorbs the first refrigerant. The heat dissipation unit condenses the second refrigerant. The evaporation unit evaporates the second refrigerant.

[0013] According to this, the adsorbent adsorbs and desorbs the first refrigerant, so that a so-called hybrid refrigeration cycle device can be configured.

[0014] In the heat dissipation section, the second refrigerant dissipates heat to the heat dissipation object and condenses, so heat transfer by condensation heat transfer can be performed.In the heat dissipation section, the condensed second refrigerant is boiled by the heat of adsorption dissipated when the adsorbent adsorbs the first refrigerant, so heat transfer by boiling heat transfer can be performed.

[0015] Furthermore, since the heat of adsorption is used to boil the second refrigerant, the temperature rise of the adsorbent itself can be suppressed, so that the continuous adsorption of the adsorbent is not hindered, and in other words, the decrease in the adsorption rate at which the adsorbent adsorbs the first refrigerant can be suppressed.

[0016] In the heat absorption section, the second refrigerant absorbs heat from the heat absorption object and evaporates, so heat transfer by boiling heat transfer can be performed.In the heat absorption section, the evaporated second refrigerant is condensed by the heat of desorption absorbed when the adsorbent desorbs the first refrigerant, so heat transfer by condensation heat transfer can be performed.

[0017] Furthermore, since the heat of desorption is used to condense the second refrigerant, the temperature of the adsorbent itself is prevented from decreasing, which prevents the adsorbent from continuing to desorb the first refrigerant.

[0018] Therefore, the reduction in the heat transfer coefficient between the mixed refrigerant and the heat radiation part and the heat transfer coefficient between the mixed refrigerant and the heat absorption part can be suppressed, and as a result, the effect of improving the operating efficiency of the cycle by configuring a hybrid refrigeration cycle device can be fully obtained.

[0019] Here, the operating efficiency of a hybrid refrigeration cycle device can be defined as the value obtained by dividing the amount of heat absorbed in the heat absorption section by the power consumption required to raise the pressure of both the refrigerant and the adsorption material from low pressure to high pressure, or the value obtained by dividing the amount of heat dissipated in the heat dissipation section by the power consumption required to raise the pressure of both the refrigerant and the adsorption material from low pressure to high pressure, etc.

[0020] The above and other objects, features, and advantages of the present disclosure will become more apparent from the following detailed description taken in conjunction with the accompanying drawings. A schematic overall configuration diagram of a refrigeration cycle device of a first embodiment. An axial cross-sectional view of an ejector of the first embodiment. A Mollier diagram schematically showing changes in the state of a first refrigerant and changes in the state of a second refrigerant in the refrigeration cycle device of the first embodiment. A schematic overall configuration diagram of a refrigeration cycle device of a second embodiment. A schematic overall configuration diagram of a refrigeration cycle device of a third embodiment.

[0021] Hereinafter, multiple embodiments for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, parts corresponding to matters described in the preceding embodiment will be assigned the same reference numerals, and duplicate descriptions may be omitted. In each embodiment, when only a part of the configuration is described, other previously described embodiments may be applied to the other parts of the configuration. In addition to combinations of parts that are specifically specified as being combinable in each embodiment, it is also possible to partially combine embodiments even if not specified, as long as there is no particular problem with the combination.

[0022] 1 to 3, a first embodiment of a refrigeration cycle device according to the present disclosure will be described. In this embodiment, a refrigeration cycle device 10 shown in the overall configuration diagram of FIG. 1 is applied to an air conditioner 1. The air conditioner 1 includes the refrigeration cycle device 10, a control device 20, and the like. The refrigeration cycle device 10 constitutes a vapor compression refrigeration cycle in the air conditioner 1 that cools the air to be blown into a room, which is a space to be air-conditioned.

[0023] The refrigerant circulating through the refrigeration cycle apparatus 10 includes multiple types of refrigerant. Specifically, the refrigerant in this embodiment includes at least R744 (i.e., carbon dioxide) as a first refrigerant and R290 (i.e., propane) as a second refrigerant. Therefore, the saturation pressure of the first refrigerant at a predetermined reference temperature (25° C. in this embodiment) is higher than the saturation pressure of the second refrigerant at the reference temperature.

[0024] The refrigerant contains an adsorbent. The adsorbent adsorbs at least a first refrigerant under high pressure and desorbs (i.e., desorbs) the adsorbed refrigerant under low pressure. Furthermore, when adsorbing a refrigerant, the adsorbent releases heat (i.e., internal energy) contained in the adsorbed refrigerant as heat of adsorption, and when desorbing the refrigerant, it absorbs ambient heat as heat of desorption.

[0025] Specifically, in this embodiment, a metal-organic framework (MOF) is used as the adsorbent. MOF is a porous material obtained by reacting metal ions with organic ligands. MOF is a polymer structure that has numerous openings inside by linking metal ions with organic ligands.

[0026] The pore size of MOFs can be optimized by combining metal ions and organic ligands. By adjusting the pore size, MOFs can selectively adsorb the target substance. In this embodiment, a MOF suitable for adsorption of carbon dioxide, which is the first refrigerant, is used. Therefore, the first refrigerant is more easily adsorbed by the adsorbent than the second refrigerant.

[0027] In addition, in this embodiment, when the pressure at which the MOF starts adsorption is defined as the adsorption start pressure, the MOF used has an adsorption start pressure that is lower than the condensation pressure of the second refrigerant inside the heat dissipation heat exchanger 13, which will be described later. In other words, the condensation pressure of the second refrigerant inside the heat dissipation heat exchanger 13 is higher than the adsorption start pressure.

[0028] In addition, in this embodiment, when the pressure at which the MOF starts desorption is defined as the desorption start pressure, the MOF used has a desorption start pressure that is higher than the evaporation pressure of the second refrigerant inside the heat absorption heat exchanger 15, which will be described later. In other words, the evaporation pressure of the second refrigerant inside the heat absorption heat exchanger 15 is lower than the desorption start pressure.

[0029] Furthermore, the adsorbent of this embodiment does not dissolve in the refrigerant, but is mixed with the refrigerant in a powder or particulate solid state. Furthermore, the amount of adsorbent mixed with the refrigerant of this embodiment is less than the amount that can adsorb all of the refrigerant under normal operating conditions of the refrigeration cycle apparatus 10. Therefore, in the refrigeration cycle apparatus 10, only the adsorbent does not circulate within the cycle. Furthermore, under normal operating conditions of the refrigeration cycle apparatus 10, not all of the second refrigerant is adsorbed by the adsorbent.

[0030] In the following description, for the sake of clarity, a refrigerant mixed with an adsorbent will be referred to as a mixed refrigerant, and a refrigerant not mixed with an adsorbent will be referred to as a refrigerant, a discharged refrigerant, a discharge side injected refrigerant, a reduced pressure side injected refrigerant, etc., without using the term "mixed."

[0031] The compressor 11 is a refrigerant compression unit in the refrigeration cycle apparatus 10 that draws in, compresses, and discharges refrigerant extracted by a low-pressure side extractor 16 (described later). The compressor 11 is an electric compressor that uses an electric motor to rotate a fixed-displacement compression mechanism with a fixed discharge capacity. The compression mechanism may be a rotary compression mechanism, a scroll compression mechanism, or the like. The rotation speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the control device 20.

[0032] The inlet side of a discharge side nozzle portion 12 a of a discharge side ejector 12 is connected to the discharge port of the compressor 11 .

[0033] The discharge side ejector 12 sucks the mixed refrigerant flowing out from the low-pressure side extractor 16 through a discharge side suction port 12c formed in the discharge side body portion 12b by the suction action of the discharge side injection refrigerant injected from the discharge side nozzle portion 12a. Furthermore, the discharge side ejector 12 converts the velocity energy (i.e., expansion energy) of the mixed refrigerant, in which the adsorbent is mixed with the discharge side injection refrigerant, into pressure energy, thereby increasing the pressure of the mixed refrigerant.

[0034] The detailed configuration of the discharge side ejector 12 will be described with reference to Fig. 2. The discharge side ejector 12 has a discharge side nozzle portion 12a and a discharge side body portion 12b.

[0035] The discharge-side nozzle portion 12a is a nozzle that converts pressure energy of the refrigerant discharged from the compressor 11 into velocity energy and sprays the refrigerant. The discharge-side nozzle portion 12a is formed of a substantially cylindrical metal (stainless steel in this embodiment) member that gradually tapers in the direction of refrigerant flow.

[0036] The discharge-side nozzle 12a isentropically depressurizes the discharged refrigerant and accelerates it to supersonic speed, and then injects the discharge-side injection refrigerant into a discharge-side mixing section 12e formed in the discharge-side body 12b. A so-called Laval nozzle or a convergent nozzle can be used as the discharge-side nozzle 12a.

[0037] The discharge-side body portion 12b supports and fixes the discharge-side nozzle portion 12a and forms the outer shell of the discharge-side ejector 12. The discharge-side body portion 12b is formed of a substantially cylindrical member made of metal (aluminum alloy in this embodiment). The discharge-side nozzle portion 12a is fixed inside one longitudinal end of the discharge-side body portion 12b by means of press-fitting or the like. The discharge-side body portion 12b may be formed of resin.

[0038] The discharge-side body 12b has a cylindrical wall surface formed at a location corresponding to the outer periphery of the discharge-side nozzle 12a. The discharge-side suction port 12c penetrates the inside and outside of the discharge-side body 12b and communicates with the refrigerant injection port of the discharge-side nozzle 12a. The discharge-side suction port 12c is a through-hole that draws the mixed refrigerant flowing out from the low-pressure side extractor 16 into the discharge-side body 12b by the suction action of the discharge-side injection refrigerant injected from the discharge-side nozzle 12a.

[0039] The discharge-side body 12b is provided with a discharge-side suction passage 12d, a discharge-side mixing section 12e, and a discharge-side pressurization section 12f. The discharge-side suction passage 12d guides the mixed refrigerant drawn through the discharge-side suction port 12c to the discharge-side mixing section 12e. The discharge-side mixing section 12e is a space for mixing the mixed refrigerant drawn through the discharge-side suction port 12c with the discharge-side spray refrigerant. The discharge-side mixing section 12e is formed in a substantially cylindrical shape.

[0040] The discharge-side pressurization section 12f is a space for pressurizing the mixed refrigerant sucked through the discharge-side suction port 12c and the discharge-side spray refrigerant. The discharge-side pressurization section 12f is formed in a truncated cone shape whose cross-sectional area expands in the direction of the mixed refrigerant flow. In the discharge-side pressurization section 12f, the velocity energy of the mixed refrigerant is converted into pressure energy by the action of shock waves generated by the discharge-side spray refrigerant and the expansion of the passage cross-sectional area.

[0041] Therefore, the discharge side ejector 12 is a discharge side transport unit that transports the mixed refrigerant flowing out from the low-pressure side extractor 16 to the discharge refrigerant side by using the pressure energy of the discharge refrigerant discharged from the compressor 11. In other words, the discharge side ejector 12 uses the pressure energy of the discharge refrigerant to mix the mixed refrigerant flowing out from the low-pressure side extractor 16 with the discharge side injection refrigerant, which is the discharge refrigerant that has consumed the pressure energy.

[0042] The outlet of the discharge side pressure boosting section 12f of the discharge side ejector 12 is connected to the mixed refrigerant inlet side of the heat dissipation heat exchanger 13. The heat dissipation heat exchanger 13 is a heat dissipation section that exchanges heat between the mixed refrigerant flowing out of the discharge side ejector 12 and outside air blown by an outside air fan (not shown), thereby dissipating heat contained in the mixed refrigerant to the outside air. Therefore, the object of heat dissipation in this embodiment is the outside air.

[0043] The inlet side of an electric expansion valve 14 is connected to the mixed refrigerant outlet of the heat dissipation heat exchanger 13. The electric expansion valve 14 is a pressure reducing unit that reduces the pressure of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13. More specifically, the electric expansion valve 14 reduces the pressure of the refrigerant contained in the mixed refrigerant, thereby lowering the pressure of the ambient refrigerant in the adsorbent. Furthermore, the electric expansion valve 14 is a flow rate adjusting unit that adjusts the flow rate of the mixed refrigerant flowing into the heat absorption heat exchanger 15.

[0044] More specifically, the electric expansion valve 14 has a valve body and a drive unit. The valve body changes the throttle opening. The drive unit displaces the valve body. An electric actuator such as a stepping motor or a brushless DC motor can be used as the drive unit. The operation of the electric expansion valve 14 is controlled by a control signal output from the control device 20.

[0045] The outlet of the electric expansion valve 14 is connected to the mixed refrigerant inlet side of the heat absorption heat exchanger 15. The heat absorption heat exchanger 15 exchanges heat between the mixed refrigerant decompressed by the electric expansion valve 14 and the blown air blown into the room from a blower (not shown). The heat absorption heat exchanger 15 is a heat absorption unit that cools the blown air by desorbing the refrigerant from an adsorbent contained in the mixed refrigerant to exert a heat absorption effect. Therefore, the object of heat absorption in this embodiment is the blown air.

[0046] The mixed refrigerant outlet of the endothermic heat exchanger 15 is connected to the mixed refrigerant inlet 16c side of the low-pressure side extractor 16. The low-pressure side extractor 16 is a low-pressure side extraction unit that extracts a portion of the gas-phase refrigerant that does not contain adsorbent from the mixed refrigerant that has flowed out of the endothermic heat exchanger 15. The low-pressure side extractor 16 is a low-pressure side separation unit that separates the refrigerant that does not contain adsorbent from the mixed refrigerant.

[0047] The refrigerant extracted in the low-pressure side extractor 16 and not containing the adsorbent includes the first refrigerant and the second refrigerant. The remaining mixed refrigerant after the refrigerant has been extracted in the low-pressure side extractor 16 includes the first refrigerant, the second refrigerant, and the adsorbent.

[0048] The first refrigerant contained in the remaining mixed refrigerant in the low-pressure side extractor 16 is in a gas phase state. The state of the second refrigerant contained in the remaining mixed refrigerant in the low-pressure side extractor 16 is affected by the pressure of the mixed refrigerant flowing out from the endothermic heat exchanger 15, the ambient temperature at the location where the low-pressure side extractor 16 is located, the type of refrigerant, etc.

[0049] The low-pressure side extractor 16 is formed by a hollow, bottomed, cylindrical metallic container that defines an internal space. The low-pressure side extractor 16 is arranged so that its axial direction is vertical. The low-pressure side extractor 16 has a tapered portion that forms a truncated cone-shaped space that tapers downward, making it easier for the powdered or particulate adsorbent to flow out. A flat filter 161 is arranged in the internal space of the low-pressure side extractor 16.

[0050] The filter 161 vertically divides the internal space of the low-pressure side extractor 16 into an upper space 16b and a lower space 16a. The filter 161 has selective permeability that allows the low-pressure side gas phase refrigerant separated from the mixed refrigerant to pass through, while prohibiting at least the adsorbent from passing through. The low-pressure side gas phase refrigerant that can pass through the filter 161 includes the first refrigerant and the second refrigerant.

[0051] The lower space 16a is connected to a mixed refrigerant inlet 16c and a mixed refrigerant outlet 16d of the low-pressure side extractor 16. The lower space 16a is configured to extract gaseous refrigerant from the mixed refrigerant by utilizing the difference in specific gravity between the refrigerant and the adsorbent.

[0052] The volume of the lower space 16a is set so that when the mixed refrigerant in the lower space 16a becomes a mixed refrigerant in which the liquid-phase refrigerant is mixed with the adsorbent, the lower space 16a can be used as a liquid storage section for storing excess refrigerant in the cycle. As a result, in the low-pressure side extractor 16, the gas-phase refrigerant is extracted into the upper space 16b.

[0053] The mixed refrigerant outlet 16d is an outlet for discharging the mixed refrigerant stored in the lower space 16a, i.e., the remaining mixed refrigerant after the gas phase refrigerant has been extracted. The mixed refrigerant outlet 16d is formed in the center of the truncated cone-shaped bottom surface of the low-pressure-side extractor 16. The discharge-side suction port 12c side of the discharge-side ejector 12 is connected to the mixed refrigerant outlet 16d.

[0054] A gas phase refrigerant outlet 16e of the low-pressure side extractor 16 is connected to the upper space 16b. The gas phase refrigerant outlet 16e is an outlet through which the low-pressure side gas phase refrigerant that has passed through the filter 161 flows out. The gas phase refrigerant outlet 16e is formed on the top surface of the low-pressure side extractor 16. The low-pressure side extractor 16 is connected to the suction port side of the compressor 11.

[0055] For this reason, in this embodiment, the low-pressure side extractor 16, the compressor 11, and the discharge side ejector 12 form a pressure-boosting section that pressurizes the mixed refrigerant flowing out from the heat-absorbing heat exchanger 15 and causes the mixed refrigerant to flow out to the mixed refrigerant inlet side of the heat-dissipating heat exchanger 13, which is a heat-dissipating section. In other words, the pressure-boosting section of this embodiment includes the low-pressure side extractor 16, the compressor 11, and the discharge side ejector 12.

[0056] Next, the electrical control unit of the air conditioner 1 of this embodiment will be described. The control device 20 has a well-known microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuits. The control device 20 performs various calculations and processes based on control programs stored in the ROM. The control device 20 then controls the operation of various control target devices connected to the output side based on the results of the calculations and processes.

[0057] A group of various control sensors is connected to the input side of the control device 20. The group of control sensors includes an inside air temperature sensor, an outside air temperature sensor, a high-pressure pressure sensor, a high-pressure temperature sensor, an evaporator pressure sensor, an evaporator temperature sensor, and the like (not shown).

[0058] The inside air temperature sensor is an inside air temperature detector that detects the indoor air temperature (i.e., the inside air temperature) Tr. The outside air temperature sensor is an outside air temperature detector that detects the outside air temperature (i.e., the outside air temperature) Tam.

[0059] The high-pressure pressure sensor is a high-pressure pressure detection unit that detects a high-pressure pressure Pd, which is the pressure of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13. The high-pressure temperature sensor is a high-pressure temperature detection unit that detects a high-pressure temperature Td, which is the temperature of the mixed refrigerant flowing out from the heat dissipation heat exchanger 13.

[0060] The evaporator pressure sensor is an evaporator pressure detection unit that detects the evaporator pressure Pe, which is the pressure of the mixed refrigerant flowing out from the heat absorption heat exchanger 15. The evaporator temperature sensor is an evaporator temperature detection unit that detects the evaporator temperature Te, which is the temperature of the mixed refrigerant flowing out from the heat absorption heat exchanger 15.

[0061] An operation panel (not shown) is connected by wire or wirelessly to the input side of the control device 20. Operation signals are input to the control device 20 from various operation switches provided on the operation panel. The various operation switches provided on the operation panel include an activation switch, a temperature setting switch, an air volume setting switch, etc.

[0062] The control device 20 is an integrated unit that controls various control target devices connected to the output side. Therefore, the components (hardware and software) that control the operation of each control target device constitute the control unit that controls the operation of each control target device. For example, the component of the control device 20 that controls the refrigerant discharge capacity of the compressor 11 constitutes the discharge capacity control unit.

[0063] Next, we will explain the operation of the air conditioner 1 configured as described above. When the operation switch of the air conditioner 1 is turned on (i.e., ON), the control device 20 executes a control program. The control program reads detection signals from the above-mentioned control sensors and operation signals from the operation panel.

[0064] The operation of the various controlled devices is then controlled based on the detection signals and operation signals that have been read in. Thereafter, the control routine of reading the detection signals and operation signals and controlling the various controlled devices based on the detection signals and operation signals is repeated at each predetermined control period until the termination condition of the control program is met.

[0065] More specifically, the control program of this embodiment controls the refrigerant discharge capacity of the compressor 11 so that the evaporator temperature Te detected by the evaporator temperature sensor approaches the target evaporator temperature TEO. The target evaporator temperature TEO is calculated based on the inside air temperature Tr detected by the inside air temperature sensor, the outside air temperature Tam detected by the outside air temperature sensor, the set temperature Tset set by the temperature setting switch, etc.

[0066] The control program also controls the throttle opening of the electric expansion valve 14 so that the high-pressure pressure Pd detected by the high-pressure pressure sensor approaches the target high-pressure PDO. The target high-pressure PDO is determined based on the high-pressure temperature Td detected by the high-pressure temperature sensor so that the operating efficiency of the cycle approaches its maximum value.

[0067] Therefore, in the refrigeration cycle apparatus 10, the states of the first refrigerant and the second refrigerant change as shown schematically in the Mollier diagram of FIG.

[0068] For clarity, in Figure 3, the changes in the physical properties and state of the first refrigerant in the cycle when it is not adsorbed by the adsorber are shown by solid lines. In Figure 3, the isotherms of T1 (approximately 0°C) and T2 (approximately 60°C) of the first refrigerant are shown by thin lines. Furthermore, the changes in the physical properties and state of the second refrigerant in the cycle when it is not adsorbed by the adsorber are shown by dashed lines. In Figure 3, the isotherms of T1 (approximately 0°C) and T2 (approximately 60°C) of the second refrigerant are shown by thin dashed lines.

[0069] In addition, in FIG. 3, for clarity of illustration, the state of the refrigerant in the pressure increasing section (specifically, the state of the refrigerant in the discharge side ejector 12) is omitted.

[0070] First, the compressor 11 draws in, compresses, and discharges the gas-phase refrigerant extracted by the low-pressure side extractor 16. More specifically, the first gas-phase refrigerant extracted by the low-pressure side extractor 16 is represented by point a1 in Fig. 3. The second gas-phase refrigerant extracted by the low-pressure side extractor 16 is represented by point a2 in Fig. 3.

[0071] The refrigerant discharged from the compressor 11 flows into the discharge nozzle 12a of the discharge ejector 12. The refrigerant flowing into the discharge nozzle 12a is isentropically decompressed and injected into the discharge mixing section 12e of the discharge body 12b. The mixed refrigerant flowing out from the mixed refrigerant outlet 16d of the low-pressure side extractor 16 is then sucked into the discharge suction port 12c by the suction action of the discharge-side injected refrigerant injected from the discharge nozzle 12a.

[0072] The mixed refrigerant sucked through the discharge suction port 12c flows into the discharge mixing section 12e via the discharge suction passage 12d. In the discharge mixing section 12e, the discharge injection refrigerant and the mixed refrigerant sucked through the discharge suction port 12c are mixed to form a mixed refrigerant, which then flows into the discharge pressure increasing section 12f.

[0073] In the discharge-side pressurization section 12f, the velocity energy of the mixed refrigerant is converted into pressure energy by the action of the shock waves generated by the discharge-side injected refrigerant and the expansion of the cross-sectional area of ​​the passage. This increases the pressure of the mixed refrigerant. As the pressure of the mixed refrigerant increases in the discharge-side pressurization section 12f, the adsorbent adsorbs the first refrigerant.

[0074] The mixed refrigerant flowing out from the discharge side pressurization section 12f of the discharge side ejector 12 flows into the heat dissipation heat exchanger 13. More specifically, the first refrigerant contained in the mixed refrigerant flowing out from the discharge side pressurization section 12f and flowing into the heat dissipation heat exchanger 13 is represented by point b1 in Fig. 3. The second refrigerant contained in the mixed refrigerant flowing out from the discharge side pressurization section 12f and flowing into the heat dissipation heat exchanger 13 is represented by point b2 in Fig. 3.

[0075] The mixed refrigerant that flows into the heat dissipation heat exchanger 13 dissipates heat to the outside air. More specifically, in the heat dissipation heat exchanger 13, the second refrigerant contained in the mixed refrigerant dissipates heat to the outside air and condenses. Also, in the heat dissipation heat exchanger 13, the adsorbent contained in the mixed refrigerant dissipates internal energy stored when adsorbing the first refrigerant as heat of adsorption. The heat of adsorption dissipated from the adsorbent boils the condensed second refrigerant. The second refrigerant boiled by the heat of adsorption dissipates heat to the outside air and condenses.

[0076] In other words, in the mixed refrigerant that flows into the heat dissipation heat exchanger 13, the second refrigerant undergoes micro-boiling and condensation until the adsorption body completes adsorption of the first refrigerant, thereby absorbing the heat contained in the first refrigerant and the adsorption body and dissipating it to the outside air.

[0077] 3 indicates a change in the state of the first refrigerant that is not adsorbed by the adsorbent in the heat dissipation heat exchanger 13. Also, the change in the state from point b2 to point c2 in FIG. 3 indicates a change in the state of the second refrigerant in the heat dissipation heat exchanger 13.

[0078] The mixed refrigerant flowing out from the heat dissipation heat exchanger 13 flows into the electric expansion valve 14 and is reduced in pressure. More specifically, the first refrigerant contained in the mixed refrigerant flowing out from the heat dissipation heat exchanger 13 flows into the electric expansion valve 14 and is reduced in pressure (from point c1 to point d1 in FIG. 3 ). The second refrigerant contained in the mixed refrigerant flowing out from the heat dissipation heat exchanger 13 flows into the electric expansion valve 14 and is reduced in pressure to become a gas-liquid two-phase state (from point c2 to point d2 in FIG. 3 ). The mixed refrigerant reduced in pressure by the electric expansion valve 14 flows into the heat absorption heat exchanger 15.

[0079] The mixed refrigerant that flows into the heat absorption heat exchanger 15 absorbs heat from the blown air. More specifically, in the heat absorption heat exchanger 15, the second refrigerant contained in the mixed refrigerant absorbs heat from the blown air and evaporates. In addition, in the heat exchanger 15, when the adsorbent contained in the mixed refrigerant desorbs the first refrigerant, it absorbs the heat of the boiled second refrigerant as desorption heat, causing the second refrigerant to condense. The second refrigerant condensed by the desorption heat absorbs heat from the blown air and evaporates.

[0080] In other words, in the mixed refrigerant that flows into the heat absorption heat exchanger 15, the second refrigerant undergoes micro-boiling and condensation until the adsorption body completes desorption of the first refrigerant, causing the heat of the blown air to be absorbed by the second refrigerant and the adsorption body.

[0081] 3 represents a change in the state of the first refrigerant that is not adsorbed by the adsorbent in endothermic heat exchanger 15. Also, the change in state from point d2 to point a2 in FIG. 3 represents a change in the state of the second refrigerant in endothermic heat exchanger 15.

[0082] The mixed refrigerant flowing out from the endothermic heat exchanger 15 flows into the lower space 16a through the mixed refrigerant inlet 16c of the low-pressure side extractor 16. A portion of the first refrigerant and the second refrigerant contained in the mixed refrigerant flowing into the lower space 16a flows into the upper space 16b through the filter 161. The first refrigerant and the second refrigerant in a gas phase flowing out from the upper space 16b are drawn into the compressor 11 and compressed again. The mixed refrigerant flowing out from the lower space 16a is drawn through the discharge-side suction port 12c of the discharge-side ejector 12.

[0083] As described above, the air conditioner 1 of this embodiment can cool the room by blowing the blown air that has been cooled when passing through the heat-absorbing heat exchanger 15 into the room.

[0084] Furthermore, the refrigeration cycle device 10 of this embodiment employs a refrigerant containing a first refrigerant that is easily adsorbed by an adsorbent and a second refrigerant that is difficult to adsorb by an adsorbent. Therefore, a hybrid refrigeration cycle can be configured in which a mixed refrigerant, in which the first refrigerant is mixed with an adsorbent, is circulated. At the same time, a conventional vapor compression refrigeration cycle can be configured in which the second refrigerant is condensed in the heat-dissipating heat exchanger 13 and evaporated in the heat-absorbing heat exchanger 15.

[0085] In this configuration, the second refrigerant condenses by releasing heat to the outside air in the heat release heat exchanger 13, allowing heat transfer by condensation heat transfer. Also, in the heat release heat exchanger 13, the condensed second refrigerant is boiled by the heat of adsorption released when the adsorbent adsorbs the first refrigerant, allowing heat transfer by boiling heat transfer.

[0086] Furthermore, since the heat of adsorption is used to boil the second refrigerant, the temperature rise of the adsorbent itself can be suppressed, so that the continuous adsorption of the adsorbent is not hindered, and in other words, the decrease in the adsorption rate at which the adsorbent adsorbs the first refrigerant can be suppressed.

[0087] Therefore, the heat transfer coefficient between the mixed refrigerant and the heat-dissipating heat exchanger 13 can be improved more than in a hybrid refrigeration cycle that uses only the first refrigerant as the refrigerant.

[0088] In the endothermic heat exchanger 15, the second refrigerant absorbs heat from the blown air and evaporates, so heat transfer can be achieved by boiling heat transfer. In the endothermic heat exchanger 15, the evaporated second refrigerant is condensed by the heat of desorption absorbed when the adsorbent desorbs the first refrigerant, so heat transfer can be achieved by condensation heat transfer.

[0089] Furthermore, since the heat of desorption is used to condense the second refrigerant, the temperature of the adsorbent itself is prevented from decreasing, which prevents the adsorbent from continuing to desorb the first refrigerant.

[0090] Therefore, the heat transfer coefficient between the mixed refrigerant and the heat-absorbing heat exchanger 15 can be improved more than in a hybrid refrigeration cycle that uses only the first refrigerant as the refrigerant.

[0091] As a result, according to the refrigeration cycle device 10 of this embodiment, it is possible to obtain a sufficient effect of improving the operating efficiency of the cycle by configuring a hybrid refrigeration cycle device.

[0092] In addition, the refrigeration cycle apparatus 10 of this embodiment employs, as the first refrigerant and the second refrigerant, refrigerants whose saturation pressure at a reference temperature is higher than that of the second refrigerant at the reference temperature. This makes it easier for the adsorption sites of the adsorbent to match the molecular size of the first refrigerant, and makes it easier for the first refrigerant to be adsorbed by the adsorbent in the heat dissipation heat exchanger 13.

[0093] In the refrigeration cycle apparatus 10 of this embodiment, the condensation pressure of the second refrigerant in the heat dissipation heat exchanger 13 is higher than the adsorption start pressure, which allows the first refrigerant to be reliably adsorbed by the adsorbent in the heat dissipation heat exchanger 13.

[0094] In the refrigeration cycle apparatus 10 of this embodiment, the evaporation pressure of the second refrigerant in the endothermic heat exchanger 15 is lower than the desorption start pressure, which allows the first refrigerant to be reliably desorbed from the adsorbent in the endothermic heat exchanger 15.

[0095] Furthermore, in the refrigeration cycle apparatus 10 of this embodiment, the low-pressure side extractor 16, the compressor 11, and the discharge-side ejector 12 form a pressure-boosting section. This makes it possible to protect the compressor 11 by preventing the compressor 11 from absorbing the adsorbent. As a result, it is possible to improve the reliability of the refrigeration cycle apparatus that circulates a mixed refrigerant in which the adsorbent is mixed with the refrigerant.

[0096] Furthermore, in the refrigeration cycle apparatus 10 of the present embodiment, under normal operating conditions, the refrigerant in a gas phase can be reliably caused to flow into the discharge-side nozzle portion 12a of the discharge-side ejector 12. This makes it easier to determine appropriate dimensional specifications for the discharge-side nozzle portion 12a and to improve the nozzle efficiency of the pressure reduction-side nozzle portion 22a than in a refrigeration cycle apparatus in which the refrigerant flowing into the discharge-side nozzle portion 12a can change between a gas phase and a two-phase gas-liquid phase.

[0097] In the refrigeration cycle device 10 of this embodiment, the amount of adsorbent mixed with the refrigerant is less than the amount required to adsorb all of the refrigerant. Therefore, only the adsorbent that has adsorbed the refrigerant does not circulate within the cycle. Therefore, even if a powdered or granular adsorbent is used, it is easy to prevent the adsorbent from remaining in a specific location within the cycle.

[0098] Second Embodiment In this embodiment, an example will be described in which a refrigeration cycle apparatus 10a according to the present disclosure is applied to an air conditioner 1a. As shown in the overall configuration diagram of FIG. 4 , the refrigeration cycle apparatus 10a includes a high-pressure side extractor 26, a pressure-reducing side ejector 22, and a fixed throttle 17 in addition to the refrigeration cycle apparatus 10 described in the first embodiment.

[0099] In the refrigeration cycle apparatus 10a, the mixed refrigerant inlet 26c side of the high-pressure side extractor 26 is connected to the refrigerant outlet of the heat dissipation heat exchanger 13. The high-pressure side extractor 26 is a high-pressure side extraction unit that extracts a portion of the refrigerant that does not contain adsorbent from the mixed refrigerant that has flowed out from the heat dissipation heat exchanger 13. The high-pressure side extractor 26 is a high-pressure side separation unit that separates the refrigerant that does not contain adsorbent from the mixed refrigerant.

[0100] The high-pressure side extractor 26 has a basic configuration similar to that of the low-pressure side extractor 16. Therefore, the internal space of the high-pressure side extractor 26 is divided into an upper space 26b and a lower space 26a by a filter 261. A mixed refrigerant inlet 26c and a mixed refrigerant outlet 26d of the high-pressure side extractor 26 are connected to the lower space 26a. A refrigerant outlet 26e of the high-pressure side extractor 26 is connected to the upper space 26b.

[0101] Under normal operating conditions of the refrigeration cycle apparatus 10a of this embodiment, the refrigerant extracted by the high-pressure side extractor 26 contains the first refrigerant and the second refrigerant in a gas phase. The remaining mixed refrigerant after the refrigerant is extracted by the high-pressure side extractor 26 contains the second refrigerant in a liquid phase.

[0102] The inlet side of the electric expansion valve 14a is connected to the refrigerant outlet 26e of the high-pressure side extractor 26. The basic configuration of the electric expansion valve 14a is similar to that of the electric expansion valve 14 described in the first embodiment. The outlet of the electric expansion valve 14a is connected to the inlet side of the pressure reduction side nozzle portion 22a of the pressure reduction side ejector 22.

[0103] The inlet side of the fixed throttle 17 is connected to the mixed refrigerant outlet 26d of the high-pressure side extractor 26. The fixed throttle 17 is a mixed refrigerant decompression section that decompresses the mixed refrigerant that flows out from the mixed refrigerant outlet 26d of the high-pressure side extractor 26. More specifically, the fixed throttle 17 decompresses the refrigerant contained in the mixed refrigerant, thereby reducing the pressure of the ambient refrigerant around the adsorbent.

[0104] Furthermore, the fixed throttle 17 is a flow rate adjusting unit that adjusts the flow rate of the mixed refrigerant sucked into the decompression-side suction port 22c of the decompression-side ejector 22. More specifically, an orifice, a capillary tube, or the like can be used as the fixed throttle 17. The outlet of the fixed throttle 17 is connected to the decompression-side suction port 22c side of the decompression-side ejector 22.

[0105] The pressure reduction side ejector 22 sucks the mixed refrigerant decompressed by the fixed throttle 17 through a pressure reduction side suction port 22c formed in the pressure reduction side body portion 22b by the suction action of the pressure reduction side injection refrigerant injected from the pressure reduction side nozzle portion 22a. Furthermore, the pressure reduction side ejector 22 converts the velocity energy of the mixed refrigerant, in which the adsorbent is mixed with the pressure reduction side injection refrigerant, into pressure energy, thereby increasing the pressure of the mixed refrigerant.

[0106] The basic configuration of the pressure reduction side ejector 22 is the same as that of the discharge side ejector 12. Therefore, as shown in Fig. 4, the pressure reduction side ejector 22 has a pressure reduction side nozzle portion 22a and a pressure reduction side body portion 22b. The pressure reduction side body portion 22b is formed with a pressure reduction side suction port 22c, a pressure reduction side mixing portion 22e, a pressure reduction side pressure increasing portion 22f, etc.

[0107] The pressure-boosting performance of the pressure-reducing side pressure-boosting section 22f of the present embodiment is set lower than the pressure-boosting performance of the discharge-side pressure-boosting section 12f of the discharge-side ejector 12. The outlet of the pressure-reducing side pressure-boosting section 22f of the pressure-reducing side ejector 22 is connected to the refrigerant inlet side of the heat-absorbing heat exchanger 15.

[0108] Therefore, the pressure reduction side ejector 22 is a pressure reduction side transport unit that uses the pressure energy of the first refrigerant and the second refrigerant extracted by the high-pressure side extractor 26 to transport the mixed refrigerant flowing out from the high-pressure side extractor 26 to the refrigerant extracted by the high-pressure side extractor 26. In other words, the pressure reduction side ejector 22 uses the pressure energy of the refrigerant extracted by the high-pressure side extractor 26 to mix the mixed refrigerant flowing out from the high-pressure side extractor 26 with the pressure reduction side injection refrigerant, which is the refrigerant extracted by the high-pressure side extractor 26 that has consumed the pressure energy.

[0109] For this reason, in this embodiment, the high-pressure side extractor 26, the fixed throttle 17, and the pressure reduction side ejector 22 form a pressure reduction section that reduces the pressure of the mixed refrigerant that has flowed out from the heat dissipation heat exchanger 13. In other words, the pressure reduction section of this embodiment includes the high-pressure side extractor 26, the fixed throttle 17, and the pressure reduction side ejector 22.

[0110] Other configurations of the refrigeration cycle device 10a and the air conditioner 1a are similar to those of the refrigeration cycle device 10 and the air conditioner 1 described in the first embodiment.

[0111] Next, the operation of the air conditioner 1a having the above-described configuration will be described. The basic operation of the refrigeration cycle device 10a of this embodiment is the same as that of the first embodiment.

[0112] In the refrigeration cycle apparatus 10a, the mixed refrigerant flowing out from the heat dissipation heat exchanger 13 flows into the lower space 26a of the high-pressure side extractor 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.

[0113] The refrigerant flowing out from the upper space 26b passes through the electric expansion valve 14a and flows into the pressure reduction side nozzle portion 22a of the pressure reduction side ejector 22. The refrigerant flowing into the pressure reduction side nozzle portion 22a is isentropically decompressed and injected into the pressure reduction side mixing portion 22e of the pressure reduction side body portion 22b.

[0114] Then, due to the suction action of the decompression-side injected refrigerant injected from the decompression-side nozzle portion 22a, the mixed refrigerant decompressed by the fixed throttle 17 is sucked from the decompression-side suction port 22c of the decompression-side body portion 22b.

[0115] The mixed refrigerant sucked through the reduced pressure side suction port 22c flows into the reduced pressure side mixing section 22e, where the reduced pressure side refrigerant sprayed from the reduced pressure side nozzle section 22a and the mixed refrigerant sucked through the reduced pressure side suction port 22c are mixed.

[0116] The mixed refrigerant mixed in the pressure reduction side mixing section 22e flows out from the pressure reduction side pressure increasing section 22f and into the heat absorption heat exchanger 15. In the heat absorption heat exchanger 15, the blown air is cooled, as in the first embodiment. Other operations are the same as in the first embodiment.

[0117] As described above, the air conditioner 1a of this embodiment can cool the room by blowing the blown air that has been cooled when passing through the heat-absorbing heat exchanger 15 into the room.

[0118] Furthermore, the refrigeration cycle apparatus 10a of this embodiment can achieve the same effects as those of the first embodiment. That is, the refrigeration cycle apparatus 10a of this embodiment employs a refrigerant containing the first refrigerant and the second refrigerant, and therefore, the effect of improving the operating efficiency of the cycle by configuring a hybrid refrigeration cycle apparatus can be fully achieved.

[0119] The refrigeration cycle apparatus 10a of this embodiment is also provided with a high-pressure side extractor 26. This prevents the adsorbent from flowing into the electric expansion valve 14a. This protects the electric expansion valve 14a, further improving the reliability of the refrigeration cycle apparatus. This also improves the accuracy of adjusting the pressure reduction amount and the flow rate in the electric expansion valve 14a.

[0120] Furthermore, in the refrigeration cycle apparatus 10a of the present embodiment, under normal operating conditions, it is possible to reliably cause the refrigerant in a gas phase to flow into the pressure reduction side nozzle portion 22a of the pressure reduction side ejector 22. This makes it easier to determine appropriate dimensional specifications for the pressure reduction side nozzle portion 22a and to improve the nozzle efficiency of the pressure reduction side nozzle portion 22a than in a refrigeration cycle apparatus in which the refrigerant flowing into the pressure reduction side nozzle portion 22a can change between a gas phase and a two-phase gas-liquid phase.

[0121] Third Embodiment In this embodiment, an example will be described in which a refrigeration cycle apparatus 10b according to the present disclosure is applied to an air conditioning apparatus 1b. As shown in the overall configuration diagram of Fig. 5, the refrigeration cycle apparatus 10b includes a second heat absorption heat exchanger 15b in addition to the refrigeration cycle apparatus 10a described in the second embodiment. In this embodiment, for clarity of explanation, the heat absorption heat exchanger 15 described in the first embodiment will be referred to as a first heat absorption heat exchanger 15a.

[0122] The second heat absorption heat exchanger 15b exchanges heat between the mixed refrigerant decompressed by the fixed throttle 17, which is a mixed refrigerant pressure reducing section, and the blown air that has passed through the first heat absorption heat exchanger 15a. The second heat absorption heat exchanger 15b is a heat absorption section that cools the blown air by desorbing the refrigerant from the adsorbent contained in the mixed refrigerant to exert a heat absorption effect.

[0123] The second heat absorption heat exchanger 15b has a basic configuration similar to that of the first heat absorption heat exchanger 15a. In this embodiment, the mixed refrigerant inlet of the second heat absorption heat exchanger 15b is connected to the outlet of the fixed throttle 17. The mixed refrigerant outlet of the second heat absorption heat exchanger 15b is connected to the pressure reduction suction port 22c of the pressure reduction ejector 22.

[0124] In the pressure reduction side ejector 22 of this embodiment, the dimensional specifications of the pressure reduction side pressure boosting section 22 f are set so as to achieve appropriate pressure boosting performance. The rest of the configuration of the refrigeration cycle apparatus 10 b and the air conditioner 1 b is the same as that of the refrigeration cycle apparatus 10 a and the air conditioner 1 a described in the second embodiment.

[0125] Next, the operation of the air conditioner 1b having the above-described configuration will be described. The basic operation of the refrigeration cycle apparatus 10b of this embodiment is the same as that of the second embodiment.

[0126] In the refrigeration cycle apparatus 10b, the refrigerant flowing out from the upper space 26b of the high-pressure side extractor 26 flows through the electric expansion valve 14a into the pressure reduction side nozzle portion 22a of the pressure reduction side ejector 22. The refrigerant flowing into the pressure reduction side nozzle portion 22a is isentropically decompressed and injected into the pressure reduction side mixing portion 22e of the pressure reduction side body portion 22b.

[0127] Then, due to the suction action of the reduced pressure side injected refrigerant sprayed from the reduced pressure side nozzle portion 22a, the mixed refrigerant flowing out from the second heat absorption heat exchanger 15b is sucked from the reduced pressure side suction port 22c of the reduced pressure side body portion 22b.

[0128] In the pressure reduction side mixing section 22e, the pressure reduction side refrigerant injected from the pressure reduction side nozzle section 22a and the mixed refrigerant sucked from the pressure reduction side suction port 22c are mixed. The mixed refrigerant mixed in the pressure reduction side mixing section 22e flows into the pressure reduction side pressurization section 22f. In the pressure reduction side pressurization section 22f, the velocity energy of the mixed refrigerant is converted into pressure energy by the action of shock waves generated by the pressure reduction side injected refrigerant and the expansion of the passage cross-sectional area. This increases the pressure of the mixed refrigerant.

[0129] The mixed refrigerant flowing out of the pressure reduction side pressure increasing section 22f flows into the first heat absorption heat exchanger 15a. The mixed refrigerant flowing into the first heat absorption heat exchanger 15a absorbs heat from the blown air. This cools the blown air blown by the blower.

[0130] More specifically, in first heat absorption heat exchanger 15a, the second refrigerant contained in the mixed refrigerant absorbs heat from the blown air and evaporates. Also, in first heat absorption heat exchanger 15a, when the adsorbent contained in the mixed refrigerant desorbs the first refrigerant, it absorbs the heat of desorption. At this time, the adsorbent absorbs the heat of the evaporated second refrigerant as desorption heat, causing the second refrigerant to condense. The second refrigerant condensed by the desorption heat absorbs heat from the blown air and evaporates.

[0131] In other words, in the mixed refrigerant that flows into the first heat absorption heat exchanger 15a, the second refrigerant undergoes micro-boiling and condensation until the adsorption body completes desorption of the first refrigerant, causing the heat of the blown air to be absorbed by the second refrigerant and the adsorption body.

[0132] The mixed refrigerant that flows out from the lower space 26a of the high-pressure side extractor 26 flows into the fixed throttle 17. The mixed refrigerant that has been decompressed by the fixed throttle 17 flows into the second heat absorption heat exchanger 15b. The mixed refrigerant that flows into the second heat absorption heat exchanger 15b absorbs heat from the blown air. This cools the blown air that has passed through the first heat absorption heat exchanger 15a.

[0133] More specifically, in second heat absorption heat exchanger 15b, the second refrigerant contained in the mixed refrigerant absorbs heat from the blown air and evaporates. Also, in second heat absorption heat exchanger 15b, when the adsorbent contained in the mixed refrigerant desorbs the first refrigerant, it absorbs the heat of desorption. At this time, the adsorbent absorbs the heat of the evaporated second refrigerant as desorption heat, causing the second refrigerant to condense. The second refrigerant condensed by the desorption heat absorbs heat from the blown air and evaporates.

[0134] In other words, in the mixed refrigerant that has flowed into the second heat absorption heat exchanger 15b, the second refrigerant undergoes micro-boiling and condensation until the adsorbent completes desorption of the first refrigerant, causing the heat of the blown air to be absorbed by the second refrigerant and the adsorbent. Other operations are the same as those in the second embodiment.

[0135] As described above, the air conditioning device 1b of this embodiment can cool the room by blowing the ventilation air cooled in the first heat absorption heat exchanger 15a and the second heat absorption heat exchanger 15b into the room.

[0136] Furthermore, the refrigeration cycle apparatus 10b of this embodiment can achieve the same effects as those of the first and second embodiments. That is, the refrigeration cycle apparatus 10b of this embodiment employs a refrigerant containing the first refrigerant and the second refrigerant, and therefore can fully achieve the effect of improving the cycle operating efficiency by configuring a hybrid refrigeration cycle apparatus.

[0137] In the refrigeration cycle apparatus 10b of this embodiment, the mixed refrigerant outlet of the second heat absorption heat exchanger 15b is connected to the decompression-side suction port 22c of the decompression-side ejector 22. As a result, the pressure of the mixed refrigerant in the second heat absorption heat exchanger 15b becomes lower than the pressure of the mixed refrigerant in the first heat absorption heat exchanger 15a due to the pressure increase action of the decompression-side ejector 22.

[0138] Therefore, the amount of cooling of the blown air in the second heat absorption heat exchanger 15b (i.e., the amount of heat absorbed by the adsorbent) is greater than the amount of cooling of the blown air in the first heat absorption heat exchanger 15a. Therefore, in the refrigeration cycle apparatus 10b, the blown air to be blown into the room can be efficiently cooled in the order of the first heat absorption heat exchanger 15a to the second heat absorption heat exchanger 15b.

[0139] The present disclosure is not limited to the above-described embodiments, and various modifications can be made as follows within the scope of the present disclosure.

[0140] In the above-described embodiment, the refrigeration cycle apparatus 10, 10a, 10b according to the present disclosure is applied to an air conditioner, but the application of the refrigeration cycle apparatus 10, 10a, 10b according to the present disclosure is not limited to this. For example, the refrigeration cycle apparatus 10, 10a, 10b may be applied to a vehicle air conditioner, a freezing apparatus, a refrigerator, etc.

[0141] In the above-described embodiment, the heat radiating section radiates heat from the refrigerant mixture to the outside air, which is the heat radiating object, and the heat absorbing section causes the refrigerant mixture to absorb heat from the ventilation air, which is the heat absorbing object. However, the present invention is not limited to this. The heat radiating section may radiate heat from the refrigerant mixture to the heating object, and the heat absorbing section may cause the refrigerant mixture to absorb heat from the outside air, which is the heat absorbing object. In this case, the present invention may be applied to a heating device that heats ventilation air, which is the heating object, or a hot water heater that heats domestic water, etc., which is the heating object.

[0142] The configuration of the refrigeration cycle device is not limited to the configuration disclosed in the above-described embodiment.

[0143] In the above embodiment, the discharge-side ejector 12 is used as the discharge-side transport unit, but this is not limiting. For example, the discharge-side transport unit may be an expander that converts the pressure energy of the refrigerant into mechanical energy for transporting the mixed refrigerant. The same applies to the pressure-reducing-side transport unit.

[0144] In the second and third embodiments, the electric expansion valve 14 a is used, but the electric expansion valve 14 a is not an essential component. Therefore, the refrigerant extracted by the high-pressure side extractor 26 may be directly introduced into the pressure-reducing side nozzle portion 22 a of the pressure-reducing side ejector 22.

[0145] Furthermore, the electric expansion valve 14a may be integrated with the pressure-reducing side ejector 22. In this case, a needle-shaped or conical valve element may be disposed in the passage of the pressure-reducing side nozzle portion 22a of the pressure-reducing side ejector 22, and the same function as that of the electric expansion valve 14a may be achieved by displacing the valve element.

[0146] In the above embodiment, an example in which R744 is used as the first refrigerant, R290 is used as the second refrigerant, and MOF is used as the adsorbent is described, but the present invention is not limited to this.

[0147] It is desirable that the first and second refrigerants have a saturation pressure higher than that of the second refrigerant at a predetermined reference temperature. It is also desirable that the condensation pressure of the second refrigerant in the heat-dissipating heat exchanger 13 is higher than the adsorption start pressure. It is also desirable that the evaporation pressure of the second refrigerant in the heat-absorbing heat exchanger 15 is lower than the desorption start pressure.

[0148] As the first refrigerant, in addition to R744, R1234yf, R134a, R600a, R410A, R404A, R32, R407C, R290, ammonia, R1234ze, or a mixed refrigerant of these may be used as long as the above conditions are met.

[0149] As the second refrigerant, in addition to R290, R744, R1234yf, R134a, R600a, R410A, R404A, R32, R407C, ammonia, R1234ze, or a mixture thereof may be used as long as the above conditions are met. Furthermore, the refrigerant may contain other types of refrigerants in addition to the first and second refrigerants.

[0150] As the adsorbent, in addition to MOF, zeolite, activated carbon, and hydrates may also be used as long as they satisfy the above conditions.

[0151] In an adsorbent having pores, when the representative opening diameter of the pores on the surface of the adsorbent is defined as the average opening diameter, it is desirable that the first representative diameter of the molecules constituting the first refrigerant is smaller than the average opening diameter, and it is desirable that the second representative diameter of the molecules constituting the second refrigerant is larger than the average opening diameter.

[0152] The representative opening diameter of a pore can be defined as the diameter of a circle having the average opening area of ​​the pore. The representative diameter of a refrigerant molecule can be defined as the diameter of a sphere having the average volume of the refrigerant molecule. The average volume of one molecule can be calculated by dividing the molecular weight of the refrigerant by the density of the refrigerant in the liquid phase at a predetermined reference temperature and Avogadro's constant.

[0153] The features of the refrigeration cycle device disclosed in this specification are as follows: (Item 1) A refrigeration cycle device that circulates a mixed refrigerant obtained by mixing a refrigerant and an adsorbent, comprising: a pressure-increasing section (11, 12, 16) that increases the pressure of the mixed refrigerant, a heat-radiating section (13) that radiates heat possessed by the mixed refrigerant pressurized in the pressure-increasing section to a heat-radiating object, a pressure-reducing section (14, 17, 22, 26) that reduces the pressure of the mixed refrigerant flowing out from the heat-radiating section, and a heat-absorbing section (15, 15a, 15b) that causes the mixed refrigerant depressurized in the pressure-reducing section to absorb heat possessed by a heat-absorbing object, wherein the refrigerant includes at least a first refrigerant and a second refrigerant, the adsorbent adsorbs and desorbs the first refrigerant, the heat-radiating section condenses the second refrigerant, and the heat-absorbing section evaporates the second refrigerant. (Item 2) The refrigeration cycle apparatus of item 1, wherein a saturation pressure of the first refrigerant at a predetermined reference temperature is higher than a saturation pressure of the second refrigerant at the reference temperature. (Item 3) The refrigeration cycle apparatus of item 1 or 2, wherein, when a pressure at which the adsorbent starts adsorption of the first refrigerant is defined as an adsorption start pressure, the condensation pressure of the second refrigerant in the heat dissipation section is higher than the adsorption start pressure. (Item 4) The refrigeration cycle apparatus of any one of items 1 to 3, wherein, when a pressure at which the adsorbent starts desorption of the first refrigerant is defined as a desorption start pressure, the evaporation pressure of the second refrigerant in the heat absorption section is lower than the desorption start pressure. (Item 5) The refrigeration cycle device according to any one of Items 1 to 4, wherein the pressurization unit includes a low-pressure side extraction unit (16) that extracts the first refrigerant and the second refrigerant from the mixed refrigerant flowing out from the heat absorption unit, a refrigerant compression unit (11) that compresses and discharges the first refrigerant and the second refrigerant extracted by the low-pressure side extraction unit, and a discharge side transport unit (12) that mixes the mixed refrigerant flowing out from the low-pressure side extraction unit with the first refrigerant and the second refrigerant discharged from the refrigerant compression unit, using pressure energy of the first refrigerant and the second refrigerant discharged from the refrigerant compression unit.(Item 6) The refrigeration cycle apparatus according to any one of Items 1 to 5, wherein the pressure reduction unit includes a high-pressure side extraction unit (26) that extracts the first refrigerant and the second refrigerant from the mixed refrigerant flowing out from the heat dissipation unit, a mixed refrigerant pressure reduction unit (17) that reduces the pressure of the mixed refrigerant flowing out from the high-pressure side extraction unit, and a pressure reduction side transport unit (22) that uses pressure energy of the first refrigerant and the second refrigerant extracted in the high-pressure side extraction unit to mix the mixed refrigerant decompressed in the mixed refrigerant pressure reduction unit with the first refrigerant and the second refrigerant extracted in the high-pressure side extraction unit.

[0154] Although the present disclosure has been described with reference to the embodiments, it is understood that the present disclosure is not limited to the embodiments or structures. The present disclosure also encompasses various modifications and equivalent modifications. In addition, various combinations and forms, including only one element, more than one element, or less than one element, are also within the scope and spirit of the present disclosure.

Claims

1. A refrigeration cycle device that circulates a mixed refrigerant obtained by mixing a refrigerant and an adsorbent, comprising: a pressure-increasing section (11, 12, 16) that increases the pressure of the mixed refrigerant; a heat-dissipating section (13) that dissipates heat contained in the mixed refrigerant pressurized in the pressure-increasing section to a heat-dissipating object; a pressure-reducing section (14, 17, 22, 26) that reduces the pressure of the mixed refrigerant flowing out from the heat-dissipating section; and a heat-absorbing section (15, 15a, 15b) that causes the mixed refrigerant depressurized in the pressure-reducing section to absorb heat contained in a heat-absorbing object, wherein the refrigerant includes at least a first refrigerant and a second refrigerant; the adsorbent adsorbs and desorbs the first refrigerant; the heat-dissipating section condenses the second refrigerant; and the heat-absorbing section evaporates the second refrigerant.

2. The refrigeration cycle device according to claim 1, wherein the saturation pressure of the first refrigerant at a predetermined reference temperature is higher than the saturation pressure of the second refrigerant at the reference temperature.

3. A refrigeration cycle device as described in claim 1, wherein when the pressure at which the adsorbent starts to adsorb the first refrigerant is defined as an adsorption start pressure, the condensation pressure of the second refrigerant in the heat dissipation section is higher than the adsorption start pressure.

4. A refrigeration cycle device as described in claim 1, wherein when the pressure at which the adsorbent starts to desorb the first refrigerant is defined as the desorption start pressure, the evaporation pressure of the second refrigerant in the heat absorption section is lower than the desorption start pressure.

5. A refrigeration cycle device as described in any one of claims 1 to 4, wherein the pressure-boosting section has a low-pressure side extraction section (16) that extracts the first refrigerant and the second refrigerant from the mixed refrigerant flowing out from the heat absorption section, a refrigerant compression section (11) that compresses and discharges the first refrigerant and the second refrigerant extracted in the low-pressure side extraction section, and a discharge side transport section (12) that uses pressure energy of the first refrigerant and the second refrigerant discharged from the refrigerant compression section to mix the mixed refrigerant flowing out from the low-pressure side extraction section with the first refrigerant and the second refrigerant discharged from the refrigerant compression section.

6. A refrigeration cycle device as described in any one of claims 1 to 4, wherein the pressure reduction section comprises a high-pressure side extraction section (26) that extracts the first refrigerant and the second refrigerant from the mixed refrigerant flowing out from the heat dissipation section, a mixed refrigerant pressure reduction section (17) that reduces the pressure of the mixed refrigerant flowing out from the high-pressure side extraction section, and a pressure reduction side transport section (22) that uses pressure energy of the first refrigerant and the second refrigerant extracted in the high-pressure side extraction section to mix the mixed refrigerant pressure reduced in the mixed refrigerant pressure reduction section with the first refrigerant and the second refrigerant extracted in the high-pressure side extraction section.

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