Refrigeration apparatus

Abstract

In a circulating-type refrigeration apparatus, heating energy of a refrigerant and a part of heating energy generated when the refrigerant is adsorbed by an adsorbent in a high pressure region are used for heating the adsorbent, and heat loss occurs. This refrigeration apparatus (100), in which a refrigerant and an adsorbent are circulated, comprises a compressor (131), a first adsorber (133), a second adsorber (134), an expansion mechanism (132), and an internal heat exchanger (138). The first adsorber (133) recovers heating energy generated when the adsorbent adsorbs the refrigerant. The second adsorber (134) recovers cooling energy generated when the adsorbent desorbs the refrigerant. The expansion mechanism (132) decompresses the refrigerant. The internal heat exchanger (138) is provided between the first adsorber (133) and the expansion mechanism (132). The internal heat exchanger (138) exchanges heat between the refrigerant and adsorbent located between the first adsorber (133) and the expansion mechanism (132), and the decompressed refrigerant and adsorbent that have passed through the internal heat exchanger (138). The refrigeration apparatus (100) has a COP of 1 or more.

Description

Refrigeration equipment

[0001] Regarding refrigeration equipment.

[0002] Conventionally, as disclosed in Patent Document 1 (U.S. Patent Application Publication No. 2023 / 0417459), refrigeration systems equipped with an adsorption-type refrigeration cycle that utilizes the heat generated when a refrigerant is adsorbed and desorbed onto an adsorbent such as a porous metal complex have been used. As such refrigeration systems, a circulating type refrigeration system is known that has a refrigerant channel through which a mixture of refrigerant and adsorbent is circulated.

[0003] In a circulating refrigeration system, a mixture of refrigerant and an adsorbent that does not adsorb refrigerant passes through a compressor and flows from the low-pressure region to the high-pressure region of the refrigerant flow path. During this process, the refrigerant is heated by compression, but the adsorbent is not. As a result, some of the heat from the refrigerant, as well as some of the heat generated when the refrigerant adsorbs onto the adsorbent in the high-pressure region, is used to heat the adsorbent, leading to heat loss.

[0004] The first refrigeration system is a refrigeration system in which a refrigerant and an adsorbent that adsorbs and desorbs the refrigerant in accordance with changes in the pressure of the refrigerant are circulated. The refrigeration system comprises a transport mechanism, a first heat recovery unit, a second heat recovery unit, a pressure reduction unit, and a heat exchange unit. The transport mechanism includes a compressor. The first heat recovery unit recovers the heat generated when the adsorbent adsorbs the refrigerant. The second heat recovery unit recovers the cold energy generated when the adsorbent desorbs the refrigerant. The pressure reduction unit reduces the pressure of the refrigerant. The heat exchange unit is provided between the first heat recovery unit and the pressure reduction unit. The heat exchange unit performs heat exchange between the refrigerant and adsorbent between the first heat recovery unit and the pressure reduction unit, and the refrigerant and adsorbent that have passed through the heat exchange unit and have been reduced in pressure. The refrigeration system has a COP of 1 or more, calculated by the following formula (I). Formula (I): COP = (Q ａｄｓ - Q ｌｇ＿ｍａｘ × (1-r) ｌｇ )) / W (in the formula, Q ａｄｓ Q is the amount of heat generated when the adsorbent adsorbs the refrigerant in the first heat recovery unit. ｌｇ＿ｍａｘ r is the amount of thermal energy recovered from the refrigerant and adsorbent in the heat exchange section, the reduced pressure section, and the second heat recovery section, and r ｌｇQ is the amount of heat recovered from the refrigerant and adsorbent in the heat exchange section. ｌｇ＿ｍａｘ This is the value obtained by dividing by , where W is the input to the transport mechanism.

[0005] The refrigeration system described in the first aspect can reduce the decrease in refrigeration capacity by reducing heat loss caused by the heating of the adsorbent material that has passed through the compressor due to the compressed refrigerant and the heat of adsorption.

[0006] The refrigeration apparatus of the second aspect is the refrigeration apparatus of the first aspect, further comprising a confluence section. The confluence section combines the refrigerant discharged from the compressor with the adsorbent that has undergone heat exchange in the heat exchange section.

[0007] In the second aspect of the refrigeration system, a confluence section allows the adsorbent, for example, which has undergone heat exchange in the heat exchange section, to be combined with the refrigerant discharged from the compressor without being drawn into the compressor. As a result, the second aspect of the refrigeration system can reduce the work performed by the compressor and thus reduce energy consumption.

[0008] The refrigeration apparatus of the third aspect is the refrigeration apparatus of the first aspect, wherein the conveying mechanism further includes a delivery section. The delivery section sends the adsorbent, which has undergone heat exchange in the heat exchange section, to the discharge side of the compressor.

[0009] The third type of refrigeration system allows for the efficient combination of the adsorbent, which has undergone heat exchange in the heat exchange section, and the refrigerant discharged from the compressor, via a discharge section.

[0010] The refrigeration apparatus of the fourth aspect is a refrigeration apparatus of any one of the first to third aspects, wherein the heat exchange section performs heat exchange between the refrigerant and adsorbent between the first heat recovery section and the reduced pressure section, and between the refrigerant and adsorbent between the second heat recovery section and the suction side of the transport mechanism.

[0011] The refrigeration apparatus of the fifth aspect is the refrigeration apparatus of the fourth aspect, further comprising a separation section. The separation section separates the refrigerant that has passed through the second heat recovery section from the adsorbent. The heat exchange section performs heat exchange between the refrigerant and adsorbent between the first heat recovery section and the reduced pressure section, and the refrigerant and adsorbent separated in the separation section.

[0012] The refrigeration system according to the fifth perspective can maintain a low temperature of the refrigerant drawn into the compressor by supplying most of the refrigerant separated in the separation unit to the suction side of the compressor. As a result, the refrigeration system according to the fifth perspective can prevent the temperature of the refrigerant discharged from the compressor from exceeding a predetermined upper limit.

[0013] The refrigeration apparatus of the sixth aspect is a refrigeration apparatus according to any one of the first to third aspects, further comprising a first flow path and a second pressure reducing section. The first flow path branches off from the refrigerant flow path between the first heat recovery section and the pressure reducing section, passes through the heat exchange section, and is connected to the suction side of the transport mechanism. The second pressure reducing section is provided in the first flow path. The heat exchange section performs heat exchange between the refrigerant and adsorbent between the first heat recovery section and the pressure reducing section, and the refrigerant and adsorbent that flows into the first flow path and is depressurized by the second pressure reducing section.

[0014] The refrigeration system described in the sixth aspect can reduce the decrease in refrigeration capacity by reducing heat loss caused by the heating of the adsorbent material that has passed through the compressor due to the compressed refrigerant and the heat of adsorption.

[0015] The refrigeration apparatus of the seventh aspect is the refrigeration apparatus of the sixth aspect, further comprising a separation section. The separation section separates the refrigerant and the adsorbent between the first heat recovery section and the depressurization section. The separation section is connected to the first flow path. The second depressurization section depressurizes the refrigerant that has flowed out of the separation section.

[0016] In the seventh aspect of the refrigeration system, the separation unit allows the refrigerant, which has been depressurized in the second depressurization unit, to be efficiently heated in the heat exchange unit. As a result, the seventh aspect of the refrigeration system can reduce the decrease in refrigeration capacity.

[0017] The refrigeration system in the eighth aspect is a refrigeration system that meets any one of the first to seventh aspects and has a COP of 1.67 or higher.

[0018] The refrigeration apparatus of the ninth aspect is a refrigeration apparatus of any one of the first to eighth aspects, wherein the adsorbent includes a metal-organic structure containing a metal ion and an organic ligand.

[0019] The refrigeration device according to the 10th aspect is any one of the refrigeration devices according to the 1st to 9th aspects, and the refrigerant contains at least one of carbon dioxide, hydrocarbon, ammonia, water, HFC, and HFO.

[0020] The refrigeration device according to the 11th aspect is a refrigeration device in which a refrigerant and an adsorbent that adsorbs and desorbs the refrigerant in response to a change in the pressure of the refrigerant circulate. The refrigeration device includes a transport mechanism, a first heat recovery unit, a second heat recovery unit, a decompression unit, a first heat exchange unit, and a second heat exchange unit. The transport mechanism includes a compressor. In the first heat recovery unit, the heat generated when the adsorbent adsorbs the refrigerant is recovered. In the second heat recovery unit, the cold heat generated when the adsorbent desorbs the refrigerant is recovered. The decompression unit decompresses the refrigerant. The first heat exchange unit recovers the heat of the refrigerant discharged from the compressor and the heat of the adsorbent. The second heat exchange unit passes through the first heat exchange unit and recovers the cold heat from the decompressed refrigerant and the adsorbent. The refrigeration device has a COP calculated by the following formula (I) of 1 or more. Formula (I): COP = (Q ａｄｓ - Q ｌｇ＿ｍａｘ × (1 - r ｌｇ )) / W (where Q ａｄｓ is the amount of heat of the heat generated when the adsorbent adsorbs the refrigerant in the first heat recovery unit, Q ｌｇ＿ｍａｘ is the amount of heat of the heat recovered from the refrigerant and the adsorbent in the first heat exchange unit, the decompression unit, and the second heat recovery unit, r ｌｇ is the value obtained by dividing the amount of heat of the heat recovered from the refrigerant and the adsorbent in the first heat exchange unit by Q ｌｇ＿ｍａｘ and W is the input of the transport mechanism.)

[0021] The refrigeration device according to the 11th aspect can reduce the reduction of the refrigerating capacity by reducing the heat loss caused by heating the adsorbent that has passed through the compressor by the compressed refrigerant and the adsorption heat.

[0022] This is a conceptual diagram of a refrigeration system equipped with a circulating refrigeration cycle. This is a graph showing the relationship between the amount of adsorption by the adsorbent and the pressure of the refrigerant. This is a graph showing the relationship between the amount of adsorption by the adsorbent and the enthalpy of the refrigerant. This is a schematic diagram of the refrigeration system 100 of the first embodiment. This is a block diagram of the refrigeration system 100 of the first embodiment. This is a flowchart for determining the heat transfer area of ​​the internal heat exchanger 138 of the first embodiment. This is a schematic diagram of the refrigeration system 200 of the second embodiment. This is a schematic diagram of the refrigeration system 300 of the third embodiment. This is a schematic diagram of the refrigeration system 400 of the fourth embodiment. This is a schematic diagram of the refrigeration system 500 of the fifth embodiment. This is a schematic diagram of the refrigeration system 600 of modification A. This is a schematic diagram of the refrigeration system 700 of modification B. This is a schematic diagram of the refrigeration system 800 of modification F. This is a schematic diagram of the refrigeration system 900 of modification G.

[0023] (1) Overview of the Refrigeration Cycle The refrigeration system of this embodiment is equipped with a refrigeration cycle that utilizes the heat generated when the adsorbent adsorbs the refrigerant and when the adsorbent desorbs the refrigerant. The refrigeration system is, for example, an air conditioning system. The adsorbent is a powder of an adsorbent material.

[0024] The refrigeration system of this embodiment is a circulating type refrigeration system in which an adsorbent and a refrigerant circulate. As shown in Figure 1, the circulating type refrigeration system 1 includes a refrigerant circuit 11 through which the refrigerant circulates, and an adsorption circuit 12 through which the adsorbent circulates. In Figure 1, the refrigerant circuit 11 and the adsorption circuit 12 are described as separate circuits. The refrigeration system 1 may also have a configuration in which the refrigerant circuit 11 and the adsorption circuit 12 merge into a flow path. In this case, the refrigeration system 1 is part of the refrigerant circuit 11 and the adsorption circuit 12 and has a flow path through which a mixture of the refrigerant and the adsorbent circulates. Alternatively, the refrigeration system 1 may have only one circuit through which a mixture of the refrigerant and the adsorbent circulates.

[0025] The refrigeration device 1 has an adsorption section 21 and a desorption section 22. Both the adsorption section 21 and the desorption section 22 include a part of the refrigerant circuit 11 and a part of the adsorption circuit 12. In the adsorption section 21, the refrigerant from the refrigerant circuit 11 is adsorbed onto the adsorbent material flowing through the adsorption circuit 12. In the desorption section 22, the refrigerant adsorbed in the adsorption section 21 is desorbed from the adsorbent material flowing through the adsorption circuit 12.

[0026] The refrigerant circuit 11 includes a compressor 31 and an expansion mechanism 32. The compressor 31 compresses the refrigerant circulating within the refrigerant circuit 11. The expansion mechanism 32 reduces the pressure of the refrigerant circulating within the refrigerant circuit 11. The compressor 31 is, for example, a rotary compressor. The expansion mechanism 32 is, for example, an electronic expansion valve. In the refrigerant circuit 11, the refrigerant is compressed by the compressor 31, passes through the adsorption section 21, is reduced in pressure by the expansion mechanism 32, passes through the desorption section 22, and is compressed again by the compressor 31.

[0027] The refrigerant circuit 11 has a high-pressure region and a low-pressure region. In the high-pressure region, the refrigerant flows after being compressed by the compressor 31 and before being depressurized by the expansion mechanism 32. In the low-pressure region, the refrigerant flows after being depressurized by the expansion mechanism 32 and before being compressed by the compressor 31. The high-pressure region is included in the adsorption section 21. The low-pressure region is included in the desorption section 22.

[0028] The refrigerant circulating within the refrigerant circuit 11 includes at least one of carbon dioxide, hydrocarbons, ammonia, water, HFCs (hydrofluorocarbons), and HFOs (hydrofluoroolefins). The hydrocarbons are selected from the group consisting of, for example, propane, butane, and isobutane.

[0029] The adsorption circuit 12 includes a booster 41 and a pressure reducer 42. The booster 41 transports the adsorbent material to the adsorption section 21 in the adsorption circuit 12. The pressure reducer 42 transports the adsorbent material to the attachment / detachment section 22 in the adsorption circuit 12. The booster 41 is, for example, a powder pump. The pressure reducer 42 is, for example, a powder valve. In the adsorption circuit 12, the adsorbent material passes through the adsorption section 21 via the booster 41 and through the attachment / detachment section 22 via the pressure reducer 42.

[0030] The adsorption circuit 12 may further include a heat exchanger 43. The heat exchanger 43 performs heat exchange between the upstream side of the booster 41 and the upstream side of the depressurizer 42. The heat exchanger 43 transfers a portion of the heat from the adsorbent flowing between the adsorption section 21 and the depressurizer 42 to the adsorbent flowing between the desorption section 22 and the booster 41.

[0031] The adsorbent circulating in the adsorption circuit 12 includes a metal-organic structure containing metal ions and organic ligands. A metal-organic structure (MOF) is a porous material with a very large specific surface area obtained by the reaction of metal ions and organic ligands. In a metal-organic structure, a polymer structure with countless openings inside is obtained by the linkage of organic ligands with metal ions. The opening diameter and topology of the metal-organic structure can be adjusted by selecting and combining metal ions and organic ligands. By selecting and combining metal ions and organic ligands, the opening diameter of the metal-organic structure can be adjusted, making it possible to selectively adsorb target substances. For example, the metal-organic structure is used as a porous material having the function of selective storage and separation of molecules and ions. In this embodiment, the metal-organic structure is used as an adsorbent for adsorbing and desorbing a refrigerant. Examples of metal-organic structures include MOF-5, MOF-200, UiO-66, and MIL-101. The adsorbent is, for example, a powder of the metal-organic structure.

[0032] (2) Operation of the refrigeration system 1 The operation of the circulating refrigeration system 1 will be explained with reference to the drawings. The adsorbent adsorbs and desorbs the refrigerant circulating in the refrigerant circuit 11. The adsorbent adsorbs and desorbs the refrigerant in response to changes in the pressure of the refrigerant circulating in the refrigerant circuit 11. Specifically, the adsorbent adsorbs the refrigerant under high pressure and desorbs the refrigerant under low pressure.

[0033] Assume that the high-pressure region of the refrigerant circuit 11 is filled with refrigerant at pressure pH and temperature TH. Assume that the low-pressure region of the refrigerant circuit 11 is filled with refrigerant at pressure pL and temperature TL. Pressure pH is higher than pressure pL. Temperature TH is higher than temperature TL. The adsorbent adsorbs refrigerant in the high-pressure region of the refrigerant circuit 11. The adsorbent desorbs refrigerant in the low-pressure region of the refrigerant circuit 11. In the adsorption section 21, the refrigerant flowing in the high-pressure region of the refrigerant circuit 11 is adsorbed onto the adsorbent of the adsorption circuit 12. In the desorption section 22, the refrigerant is desorbed from the adsorbent flowing through the adsorption circuit 12.

[0034] The operation of the heat pump cycle of the refrigeration system 1 will be explained with reference to Figure 1-3. Figure 1-3 shows the refrigerant cycle a→b→c→d→a in the refrigerant circuit 11, and the adsorbent cycle a'→b'→c'→d'→a' in the adsorption circuit 12. The graph in Figure 2 shows the adsorption amount, which is the mass of refrigerant adsorbed on the adsorbent per unit mass, and the change in the pressure of the refrigerant adsorbed on the adsorbent, in the heat pump cycle. The graph in Figure 3 shows the adsorption amount of the adsorbent and the change in the enthalpy of the refrigerant adsorbed on the adsorbent, in the heat pump cycle. In the refrigeration system 1, it is assumed that heat can flow freely between the refrigerant circuit 11 and the adsorption circuit 12.

[0035] In the refrigerant circuit 11, the refrigerant is compressed by the compressor 31 (a→b). In the adsorption circuit 12, the adsorbent is circulated using the booster 41 (a'→b'). As a result, the pressure of the refrigerant rises from pL to pH. During this process, some of the heat Q1 generated by the adiabatic compression of the refrigerant is transferred to the adsorbent. In other words, the refrigerant is cooled by transferring heat to the adsorbent while being compressed. As a result, the temperature of the adsorbent rises from TL to TH.

[0036] Next, in the adsorption section 21, the refrigerant is gradually adsorbed onto the adsorbent while releasing heat Q2 (b'→c'). During this process, the amount of adsorption by the adsorbent increases from mL to mH. As a result, in the adsorption section 21, the refrigerant from the refrigerant circuit 11 is adsorbed onto the adsorbent of the adsorption circuit 12. In Figure 1, as indicated by the hatched arrows within the adsorption section 21, the refrigerant from the refrigerant circuit 11 is adsorbed onto the adsorbent circulating in the adsorption circuit 12.

[0037] Next, in the refrigerant circuit 11, the refrigerant is depressurized by the expansion mechanism 32 (c→d). In the adsorption circuit 12, the adsorbent is circulated by the pressure reducer 42 (c'→d'). As a result, the refrigerant pressure decreases from pH to pL. During this process, the temperature of the adsorbent decreases from TH to TL due to the isenthalpic expansion of the refrigerant desorbed from the adsorbent. Also, due to the temperature difference between the refrigerant and the adsorbent, the adsorbent in the adsorption circuit 12 is cooled, transferring heat Q3 to the refrigerant in the refrigerant circuit 11. Furthermore, heat Q5 is transferred from the adsorbent before it passes through the pressure reducer 42 to the adsorbent before it passes through the pressure booster 41 by the heat exchanger 43.

[0038] Next, in the desorption section 22, the refrigerant is gradually desorbed from the adsorbent while absorbing heat Q4 (d'→a'). During this process, the amount of adsorbed material decreases from mH to mL. As a result, the refrigerant adsorbed on the adsorbent in the adsorption circuit 12 is desorbed. In Figure 1, as indicated by the hatched arrows within the desorption section 22, the refrigerant is desorbed from the adsorbent in the adsorption circuit 12 in the desorption section 22.

[0039] As shown in Figure 2, during the adsorption process (b'→c') in which the refrigerant is adsorbed onto the adsorbent, the pressure of the refrigerant is pH, and the amount of adsorbed by the adsorbent increases from mL to mH. During the desorption process (d'→a') in which the refrigerant is desorbed from the adsorbent, the pressure of the refrigerant is pL, and the amount of adsorbed by the adsorbent decreases from mH to mL. As shown in Figure 3, during the adsorption process, the enthalpy decreases by Δh1. During the desorption process, the enthalpy increases by Δh2. During the adsorption process, the heat Q2 released from the adsorption part 21 is proportional to Δh1. During the desorption process, the heat Q4 absorbed by the desorption part 22 is proportional to Δh2.

[0040] In the refrigeration device 1, heat Q2 is released in the adsorption section 21 (first heat recovery section), generating warmth, and heat Q4 is absorbed in the desorption section 22 (second heat recovery section), generating coldness. When the warmth generated in the adsorption section 21 is recovered by another heat transfer medium, the temperature of that heat transfer medium rises. When the coldness generated in the desorption section 22 is recovered by another heat transfer medium, the temperature of that heat transfer medium decreases.

[0041] (3) Detailed Configuration (3-1) The specific configuration of the circulating refrigeration system 100 of the first embodiment will be described with reference to the drawings.

[0042] (3-1-1) Configuration of the Refrigeration System 100 The refrigeration system 100 of the first embodiment includes a refrigerant flow path 111 through which the refrigerant circulates, as shown in Figure 4. The refrigerant flow path 111 has the functions of both the refrigerant circuit 11 and the adsorption circuit 12 of Figure 1. The adsorbent circulates within the refrigerant flow path 111 together with the refrigerant. In other words, in the refrigeration system 100, a mixture of the refrigerant and the adsorbent (hereinafter referred to as the "mixed fluid") flows within the refrigerant flow path 111.

[0043] The refrigeration system 100 includes a compressor 131, an expansion mechanism 132, a first adsorbent 133, a second adsorbent 134, and an internal heat exchanger 138. The refrigeration system 100 further includes a switching mechanism 135, a first fan 136, and a second fan 137.

[0044] The compressor 131 incorporates the functions of both the compressor 31 and the booster 41 shown in Figure 1. The compressor 131 is a transport mechanism that transports the refrigerant and adsorbent within the refrigerant flow path 111. The expansion mechanism 132 incorporates the functions of both the expansion mechanism 32 and the pressure reducer 42 shown in Figure 1. The expansion mechanism 132 has the function of adjusting the amount of mixed fluid passing through the refrigerant flow path 111 by adjusting its opening. The expansion mechanism 132 is an example of a pressure reducer, such as an electronic expansion valve.

[0045] The switching mechanism 135 switches the flow direction of the mixed fluid circulating in the refrigerant flow path 111. The switching mechanism 135 is, for example, a four-way switching valve. The switching mechanism 135 is configured to switch the refrigerant flow path 111 between a first state with a flow direction shown by the solid line in Figure 4 and a second state with a flow direction shown by the dashed line in Figure 4. When the refrigerant flow path 111 is in the first state, the discharge side of the compressor 131 is connected to the first adsorbent 133, and the suction side of the compressor 131 is connected to the second adsorbent 134. When the refrigerant flow path 111 is in the second state, the discharge side of the compressor 131 is connected to the second adsorbent 134, and the suction side of the compressor 131 is connected to the first adsorbent 133.

[0046] In the first adsorbent 133, the refrigerant is adsorbed onto the adsorbent while the refrigerant flow path 111 is in the first state, and the refrigerant is desorbed from the adsorbent while the refrigerant flow path 111 is in the second state. In the second adsorbent 134, the refrigerant is desorbed from the adsorbent while the refrigerant flow path 111 is in the first state, and the refrigerant is adsorbed onto the adsorbent while the refrigerant flow path 111 is in the second state.

[0047] While the refrigerant flow path 111 is in the first state, heat of adsorption is generated in the first adsorbent 133 and heat of desorption is generated in the second adsorbent 134. While the refrigerant flow path 111 is in the second state, heat of desorption is generated in the first adsorbent 133 and heat of adsorption is generated in the second adsorbent 134. Heat of adsorption is the thermal heat generated when the adsorbent adsorbs the refrigerant. Heat of desorption is the cold heat generated when the adsorbent desorbs the refrigerant.

[0048] The heat of adsorption or desorption generated in the first adsorbent 133 and the second adsorbent 134 is recovered into the air surrounding the first adsorbent 133 and the second adsorbent 134. Therefore, the air surrounding the first adsorbent 133 and the second adsorbent 134 is heated by the heat of adsorption or cooled by the heat of desorption. The first fan 136 sends the air heated or cooled by the first adsorbent 133 to a predetermined location. The second fan 137 sends the air heated or cooled by the second adsorbent 134 to a predetermined location. The first adsorbent 133 and the second adsorbent 134 are, for example, microchannel heat exchangers or finned tube heat exchangers.

[0049] Thus, in the refrigeration system 100, as the mixed fluid circulates through the refrigerant flow path 111, air heated by the heat of adsorption or air cooled by the heat of cooling is sent to a predetermined location. If the refrigeration system 100 is an air conditioning system, for example, the first adsorbent 133 corresponds to an indoor heat exchanger, and the second adsorbent 134 corresponds to an outdoor heat exchanger. In this case, by switching the refrigerant flow path 111 to a first state, the refrigerant is adsorbed onto the adsorbent material in the first adsorbent 133, generating heat of adsorption. The air heated by the heat of adsorption is sent to a predetermined location by the first fan 136.

[0050] The internal heat exchanger 138 performs heat exchange between a high-pressure mixed fluid flowing in the refrigerant flow path 111 and a low-pressure mixed fluid flowing in the refrigerant flow path 111. The internal heat exchanger 138 has a high-pressure side flow path 138a through which the high-pressure mixed fluid flows, and a low-pressure side flow path 138b through which the low-pressure mixed fluid flows. The type of internal heat exchanger 138 is not limited as long as it has a high-pressure side flow path 138a and a low-pressure side flow path 138b. For example, the internal heat exchanger 138 can be a double-tube heat exchanger or a plate heat exchanger. As shown in Figure 4, the direction in which the high-pressure mixed fluid flows in the high-pressure side flow path 138a and the direction in which the low-pressure mixed fluid flows in the low-pressure side flow path 138b are opposite to each other. In the internal heat exchanger 138, the high-pressure mixed fluid and the low-pressure mixed fluid flow in opposing directions.

[0051] The internal heat exchanger 138 is provided between the first adsorbent 133 and the expansion mechanism 132. The internal heat exchanger 138 performs heat exchange between the refrigerant and adsorbent (mixed fluid) between the first adsorbent 133 and the expansion mechanism 132 and the refrigerant and adsorbent (mixed fluid) that has passed through the internal heat exchanger 138 and been depressurized. Specifically, the internal heat exchanger 138 performs heat exchange between the refrigerant and adsorbent between the first adsorbent 133 and the expansion mechanism 132 and the refrigerant and adsorbent between the second adsorbent 134 and the suction side of the conveying mechanism (compressor 131).

[0052] When the refrigerant flow path 111 is in the first state, the high-pressure mixed fluid that has passed through the compressor 131 and the first adsorbent 133 flows through the high-pressure side flow path 138a of the internal heat exchanger 138, and the low-pressure mixed fluid that has passed through the expansion mechanism 132 and the second adsorbent 134 flows through the low-pressure side flow path 138b of the internal heat exchanger 138. When the refrigerant flow path 111 is in the first state, the high-pressure side flow path 138a is connected to the outlet side of the first adsorbent 133 and the expansion mechanism 132. When the refrigerant flow path 111 is in the first state, the low-pressure side flow path 138b is connected to the outlet side of the second adsorbent 134 and the suction side of the compressor 131. The internal heat exchanger 138 is designed such that the volume of the low-pressure side flow path 138b is greater than the volume of the high-pressure side flow path 138a.

[0053] The refrigeration system 100 further comprises a control unit 105. The control unit 105 controls the operation of each component of the refrigeration system 100. Here, a processor is given as an example of the control unit 105. The processor consists of various computing devices such as a CPU (Central Processing Unit), a DSP (Digital Signal Processor), an FPGA (Field-Programmable Gate Array), and a GPU (Graphics Processing Unit). The processor reads various programs of the device into memory and executes them. The processor loads the programs stored in memory into the working area of ​​the memory and executes them, and by controlling each component through the execution of the programs, it realizes functions that match a predetermined purpose.

[0054] As shown in Figure 5, the control unit 105 controls the compressor 131, the expansion mechanism 132, the switching mechanism 135, the first fan 136, and the second fan 137. The control unit 105 controls the rotational speed of the compressor 131. The control unit 105 controls the timing for starting the compressor 131 and the timing for stopping the compressor 131. The control unit 105 controls the opening degree of the expansion mechanism 132. The control unit 105 controls the switching mechanism 135 to switch the refrigerant flow path 111 between a first state and a second state. The control unit 105 controls the rotational speed of the first fan 136 and the second fan 137.

[0055] (3-1-2) When the refrigerant flow path 111 of the refrigeration device 100 is in the first state, the discharge side of the compressor 131 is connected to the first adsorbent 133 (first heat recovery unit) to create a high-pressure state inside the first adsorbent 133, and the suction side of the compressor 131 is connected to the second adsorbent 134 (second heat recovery unit) to create a low-pressure state inside the second adsorbent 134. Therefore, the adsorbent flowing through the refrigerant flow path 111 mainly adsorbs refrigerant in the first adsorbent 133 (first heat recovery unit) and mainly desorbs refrigerant in the second adsorbent 134 (second heat recovery unit).

[0056] When the refrigerant flow path 111 is in the first state, the internal heat exchanger 138 performs heat exchange between the high-pressure mixed fluid that has passed through the compressor 131 and the first adsorbent 133 in that order, and the low-pressure mixed fluid that has passed through the internal heat exchanger 138, the expansion mechanism 132, and the second adsorbent 134 in that order.

[0057] Therefore, when the refrigerant flow path 111 is in the first state, the mixed fluid discharged from the compressor 131 passes through the first adsorbent 133, the high-pressure side flow path 138a of the internal heat exchanger 138, the expansion mechanism 132, the second adsorbent 134, and the low-pressure side flow path 138b of the internal heat exchanger 138 in this order before being drawn into the compressor 131.

[0058] When the refrigerant flow path 111 is in the second state, the suction side of the compressor 131 is connected to the first adsorbent 133 (second heat recovery unit) to create a low-pressure state inside the first adsorbent 133, and the discharge side of the compressor 131 is connected to the second adsorbent 134 (first heat recovery unit) to create a high-pressure state inside the second adsorbent 134. Therefore, the adsorbent flowing through the refrigerant flow path 111 mainly adsorbs refrigerant in the second adsorbent 134 (first heat recovery unit) and mainly desorbs refrigerant in the first adsorbent 133 (second heat recovery unit).

[0059] When the refrigerant flow path 111 is in the second state, the internal heat exchanger 138 performs heat exchange between the mixed fluid that has passed through the second adsorbent 134 and the expansion mechanism 132 in that order, and the mixed fluid that has passed through the internal heat exchanger 138 and the first adsorbent 133.

[0060] Therefore, when the refrigerant flow path 111 is in the second state, the mixed fluid discharged from the compressor 131 passes through the second adsorbent 134, the expansion mechanism 132, the high-pressure side flow path 138a of the internal heat exchanger 138, the first adsorbent 133, and the low-pressure side flow path 138b of the internal heat exchanger 138 in this order before being drawn into the compressor 131.

[0061] (3-1-3) Details of the Refrigeration System 100 In the following description, the refrigeration system 100 is an air conditioning system in which the first adsorbent 133 is an outdoor heat exchanger and the second adsorbent 134 is an indoor heat exchanger. When the refrigerant flow path 111 is in the first state, the refrigeration system 100 performs cooling operation. When the refrigerant flow path 111 is in the second state, the refrigeration system 100 performs heating operation.

[0062] The refrigerant sealed in the refrigerant flow path 111 is, for example, carbon dioxide (CO2). ２ The adsorbent sealed in the refrigerant flow path 111 is, for example, a metal-organic frame (MOF). The first adsorbent 133 and the second adsorbent 134 have the same heat transfer area.

[0063] The refrigeration system 100 has a coefficient of performance (COP) of 1 or greater, calculated by the following formula (1). COP is a dimensionless index representing the energy efficiency of the refrigeration system 100. Formula (1): COP = Q / W

[0064] In equation (1), Q is the cooling capacity [kW] of the refrigeration system 100 when the refrigerant flow path 111 is in the first state. Q is the heating capacity [kW] of the refrigeration system 100 when the refrigerant flow path 111 is in the second state.

[0065] In equation (1), W is the energy consumption [kW] of the refrigeration device 100. W is the power input to the conveying mechanism including the compressor 131.

[0066] Q is calculated using the following equation (2): Equation (2): Q = Q ａｄｓ - Q ｌｇ＿ｍａｘ × (1-r) ｌｇ ) = Q ｄｅｓ - Q ｌｇ＿ｍａｘ × (1-r) ｌｇ )

[0067] In equation (2), Q ａｄｓ Q is an index representing the heat exchange capacity of the refrigeration device 100, and is the heat of adsorption [kW] generated in the first adsorbent 133. In other words, Q ａｄｓ This is the amount of heat generated when the adsorbent material adsorbs the refrigerant in the first adsorbent 133.

[0068] In equation (2), Q ｄｅｓ Q is an index representing the heat exchange capacity of the refrigeration device 100, and is the heat of desorption [kW] generated in the second adsorbent 134. In other words, Q ｄｅｓ This is the amount of heat generated when the adsorbent desorbs the refrigerant in the second adsorbent 134.

[0069] In equation (2), Q ｌｇ＿ｍａｘ × (1-r) ｌｇThe term ) represents the heat loss [kW] generated in the refrigeration device 100. Heat loss is the amount of heat used to heat the adsorbent that has passed through the compressor 131 and not used for heat exchange in the first adsorbent 133 or the second adsorbent 134. Alternatively, heat loss is the amount of cold energy used to cool the adsorbent that has passed through the expansion mechanism 132 and not used for heat exchange in the first adsorbent 133 or the second adsorbent 134.

[0070] In equation (2), Q ｌｇ＿ｍａｘ Q is an index that represents the maximum heat recovery capacity of the refrigeration device 100. ａｄｓ - Q ｌｇ＿ｍａｘ × (1-r) ｌｇ In ) Q ｌｇ＿ｍａｘ Q is the amount of thermal energy [kW] recovered from the refrigerant and adsorbent in the internal heat exchanger 138, expansion mechanism 132, and second adsorbent 134. ｄｅｓ - Q ｌｇ＿ｍａｘ × (1-r) ｌｇ In ) Q ｌｇ＿ｍａｘ Q is the amount of heat [kW] of cold energy recovered from the refrigerant and adsorbent in the internal heat exchanger 138, expansion mechanism 132, and first adsorbent 133. ｌｇ＿ｍａｘ This corresponds to the maximum heat loss [kW] generated in the refrigeration device 100.

[0071] In equation (2), r ｌｇ This is the heat recovery rate [dimensionless] of the refrigeration device 100.

[0072] r ｌｇ This is calculated by the following formula (3): Formula (3): r ｌｇ = Q ｌｇ / Q ｌｇ＿ｍａｘ

[0073] In equation (3), Q ｌｇ This is an indicator representing the heat recovery capacity of the internal heat exchanger 138. Q ｌｇ is the amount of heat [kW] of heat or cold recovered from the refrigerant and adsorbent in the internal heat exchanger 138. If the refrigeration system 100 does not have an internal heat exchanger 138, r ｌｇ When r becomes 0, the heat loss is maximized. When all the heat or cold is recovered in the internal heat exchanger 138, r ｌｇ The result is 1, and no heat loss occurs.

[0074] Q ａｄｓ It is calculated by the following formula (4). Formula (4): Q ａｄｓ = Δm × Gr ＭＯＦ ×Δh ａｄｓ

[0075] In equation (4), Δm is the amount of adsorption of the adsorbent [kg(CO2) ２ The formula is [m / kg (MOF)]. In other words, Δm is the weight of refrigerant that 1 kg of adsorbent can adsorb.

[0076] In equation (4), Gr ＭＯＦ This is the circulation rate of the adsorbent [kg(MOF) / s]. In other words, Gr ＭＯＦ This is the weight of the adsorbent flowing through the refrigerant flow path 111 per second.

[0077] In equation (4), Δh ａｄｓ The heat of adsorption of the refrigerant [kJ / kg (CO2)] ２ )]. In other words, Δh ａｄｓ This is the amount of heat generated when 1 kg of refrigerant is adsorbed onto the adsorbent.

[0078] Q ｄｅｓ Q is calculated using the following formula (5). Formula (5): Q ｄｅｓ = Δm × Gr ＭＯＦ ×Δh ｄｅｓ

[0079] In equation (5), Δh ｄｅｓ The heat of desorption of the refrigerant [kJ / kg (CO2)] is ２ )]. In other words, Δh ｄｅｓ This is the amount of heat generated when 1 kg of refrigerant is desorbed from the adsorbent.

[0080] Q ｌｇ Q is calculated using the following formula (6). Formula (6): Q ｌｇ = Q ｌｇ＿ｍａｘ ×r ｌｇ = (Q ｌｇ＿ＭＯＦ＿ｍａｘ +Q ｌｇ＿ＣＯ２＿ｍａｘ ) × r ｌｇ

[0081] In equation (6), Q ｌｇ＿ｍａｘ Q ｌｇ＿ＭＯＦ＿ｍａｘ and Q ｌｇ＿ＣＯ２＿ｍａｘ It is the sum of the two.

[0082] In formula (6), Q ｌｇ＿ＭＯＦ＿ｍａｘ is the maximum value [kW] of the amount of heat of warm or cold heat that can be recovered from the adsorbent.

[0083] In formula (6), Q ｌｇ＿ＣＯ２＿ｍａｘ is the maximum value [kW] of the amount of heat of warm or cold heat that can be recovered from the refrigerant.

[0084] Q ｌｇ＿ＭＯＦ＿ｍａｘ is calculated by the following formula (7). Formula (7): Q ｌｇ＿ＭＯＦ＿ｍａｘ = Gr ＭＯＦ × C ＭＯＦ × (T ａｄｓ＿ｏｕｔ＿ＭＯＦ − T ｄｅｓ＿ｏｕｔ＿ＭＯＦ )

[0085] In formula (7), C ＭＯＦ is the specific heat [kJ / (kg·K)] of the adsorbent.

[0086] In formula (7), T ａｄｓ＿ｏｕｔ＿ＭＯＦ is the outlet temperature [K] of the first adsorber 133. In other words, T ａｄｓ＿ｏｕｔ＿ＭＯＦ is the temperature of the adsorbent immediately after flowing out from the first adsorber 133.

[0087] In formula (7), T[[ID=,40]] ｄｅｓ＿ｏｕｔ＿ＭＯＦ [[ID=,41]]is the outlet temperature [K] of the second adsorber 134. In other words, T ｄｅｓ＿ｏｕｔ＿ＭＯＦ is the temperature of the adsorbent immediately after flowing out from the second adsorber 134.

[0088] Q ｌｇ＿ＣＯ２＿ｍａｘ is calculated by the following formula (8). Formula (8): Q ｌｇ＿ＣＯ２＿ｍａｘ = Gr ＣＯ２ × C ＣＯ２ × (T ａｄｓ＿ｏｕｔ＿ＣＯ２ − T ｄｅｓ＿ｏｕｔ＿ＣＯ２ )

[0089] In formula (8), Gr ＣＯ２ is the circulation amount [kg / s] of the refrigerant. In other words, Gr ＣＯ２ is the weight of the refrigerant flowing in the refrigerant flow path 111 per second.

[0090] In formula (8), C ＣＯ２ is the specific heat [kJ / (kg·K)] of the refrigerant.

[0091] In formula (8), Tａｄｓ＿ｏｕｔ＿ＣＯ２ is the outlet temperature [K] of the first adsorber 133. In other words, T ａｄｓ＿ｏｕｔ＿ＣＯ２ is the temperature of the refrigerant immediately after flowing out from the first adsorber 133.

[0092] In Equation (8), T ｄｅｓ＿ｏｕｔ＿ＣＯ２ is the outlet temperature [K] of the second adsorber 134. In other words, T ｄｅｓ＿ｏｕｔ＿ＣＯ２ is the temperature of the refrigerant immediately after flowing out from the second adsorber 134.

[0093] W is calculated by the following Equation (9). Equation (9): W = Gr ＣＯ２ × (h ｃｏｍｐ＿ｏｕｔ − h ｃｏｍｐ＿ｉｎ ) + W ＭＯＦ

[0094] In Equation (9), h ｃｏｍｐ＿ｏｕｔ is the specific enthalpy [kJ / kg] of the refrigerant discharged from the compressor 131.

[0095] In Equation (9), h ｃｏｍｐ＿ｉｎ is the specific enthalpy [kJ / kg] of the refrigerant sucked into the compressor 131.

[0096] In Equation (9), W ＭＯＦ is the work [kW] received by the adsorbent in the process of circulating through the refrigerant flow path 111. W ＭＯＦ represents the electric power input to the conveying mechanism to convey the adsorbent in the refrigerant flow path 111.

[0097] In the present embodiment, W ＭＯＦ is calculated by the following Equation (10). Equation (10): W ＭＯＦ = Gr ＭＯＦ × (h ｃｏｍｐ＿ｏｕｔ − h ｃｏｍｐ＿ｉｎ )

[0098] The refrigeration device 100 is designed such that the COP is 1 or more. The heat transfer area of the internal heat exchanger 138 is determined by using Equations (1) to (10) in accordance with steps S11 to S16 of the flowchart shown in FIG. 6 so that the COP of the refrigeration device 100 is 1 or more.

[0099] In step S11, the heat exchange capacity Q ａｄｓ or Q ｄｅｓ, and the maximum value Q of the heat recovery capacity of the refrigeration device 100 ｌｇ＿ｍａｘ This will be decided.

[0100] In step S12, the energy consumption W of the refrigeration device 100 is determined.

[0101] In step S13, the heat recovery rate r of the refrigeration device 100 ｌｇ A provisional value is determined.

[0102] In step S14, the COP of the refrigeration unit 100 is calculated.

[0103] In step S15, it is determined whether the COP calculated in step S14 is 1 or greater. If the COP is 1 or greater, the process proceeds to step S16. If the COP calculated in step S14 is not 1 or greater, in step S13, the heat recovery rate r ｌｇ A different value is determined as a provisional value, and in step S14, the COP is recalculated.

[0104] In step S16, the heat transfer area of ​​the internal heat exchanger 138 is determined. Specifically, the heat transfer area of ​​the internal heat exchanger 138 [m²] ２ ] and the heat transfer area of ​​the first adsorbent 133 or the second adsorbent 134 [m ２ The heat transfer area ratio [dimensionless], which is the ratio of ] to , is calculated.

[0105] The heat transfer area A of the first adsorbent 133 is calculated by the following formula (11a): Formula (11a): A = Q ａｄｓ / (K × ΔT)

[0106] In equation (11a), K is the heat transfer coefficient of the first adsorbent 133 [kW / (m²). ２ • K) is a specific value determined by the material properties of the first adsorbent 133.

[0107] In equation (11a), ΔT is the difference [K] between the temperature of the refrigerant and adsorbent inside the first adsorbent 133 and the temperature of the air surrounding the first adsorbent 133.

[0108] The heat transfer area A of the second adsorbent 134 is calculated by the following equation (11b): Equation (11b): A = Q ａｄｓ / (K × ΔT)

[0109] In equation (11b), K is the heat transfer coefficient of the second adsorbent 134 [kW / (m²). ２ ・K) is a specific value determined by the material properties of the second adsorbent 134.

[0110] In equation (11b), ΔT is the difference [K] between the temperature of the refrigerant and adsorbent inside the second adsorbent 134 and the temperature of the air surrounding the second adsorbent 134.

[0111] The heat transfer area A' of the internal heat exchanger 138 is calculated by the following equation (12): Equation (12): A' = Q ｌｇ / (K'×ΔT')

[0112] In equation (12), K' is the heat transfer coefficient of the internal heat exchanger 138 [kW / (m²) ２ ・K) ]. K' is a specific value determined by the material properties of the internal heat exchanger 138.

[0113] In equation (12), ΔT' is the difference [K] between the temperature of the high-pressure side flow path 138a and the temperature of the low-pressure side flow path 138b of the internal heat exchanger 138.

[0114] From equation (11a) or equation (11b), and equation (12), the heat transfer area ratio A' / A is calculated by the following equation (13): Equation (13): A' / A = (K / K') × (Q ｌｇ / Q ａｄｓ ) × (ΔT / ΔT')

[0115] In equation (13), K / K' is a specific value, and Q ｌｇ / Q ａｄｓ This takes a predetermined value during the rated operation of the refrigeration unit 100. Therefore, the heat transfer area ratio A' / A can be calculated by setting a provisional value for ΔT / ΔT'. The smaller ΔT / ΔT' is, the smaller the heat transfer area ratio A' / A becomes. Consequently, if the first adsorbent 133 has predetermined A and ΔT, the size of the internal heat exchanger 138 can be reduced while decreasing the heat transfer area A' of the internal heat exchanger 138 by designing the internal heat exchanger 138 to increase ΔT'.

[0116] (3-1-4) Characteristics: When the refrigeration system 100 does not have an internal heat exchanger 138, a mixed fluid containing a low-temperature adsorbent flowing through the low-pressure region of the refrigerant flow path 111 is drawn into the compressor 131. As the mixed fluid passes through the compressor 131, the refrigerant is compressed and heated, but the adsorbent is not heated. Therefore, some of the heat of adsorption generated when the refrigerant that has passed through the compressor 131 adsorbs onto the adsorbent is used to heat the low-temperature adsorbent that has passed through the compressor 131. Also, some of the heat from the high-temperature refrigerant that has passed through the compressor 131 is used to heat the low-temperature adsorbent that has passed through the compressor 131, and as the temperature of the refrigerant decreases, the heat of adsorption becomes smaller. Thus, in a circulating refrigeration system, there is a risk of heat loss due to the low-temperature adsorbent contained in the mixed fluid drawn into the compressor 131.

[0117] In the refrigeration system 100, when the refrigerant flow path 111 is in a first state, the internal heat exchanger 138 performs heat exchange between the refrigerant contained in the mixed fluid that has passed through the first adsorbent 133 and the adsorbent contained in the mixed fluid that has passed through the first adsorbent 133 and been depressurized. In other words, the internal heat exchanger 138 performs heat exchange between the high-temperature refrigerant that has passed through the first adsorbent 133 and the low-temperature adsorbent that has passed through the second adsorbent 134. As a result, heat exchange takes place in the internal heat exchanger 138 between the high-temperature refrigerant flowing in the high-pressure region of the refrigerant flow path 111 and the low-temperature adsorbent flowing in the low-pressure region of the refrigerant flow path 111. Therefore, the adsorbent flowing in the low-pressure region of the refrigerant flow path 111 is heated by the heat exchange in the internal heat exchanger 138. The mixed fluid containing the adsorbent heated in the internal heat exchanger 138 is drawn into the compressor 131. Therefore, the refrigeration system 100 can reduce the decrease in refrigeration capacity by reducing heat loss caused by the heating of the adsorbent material that has passed through the compressor 131 due to the compressed refrigerant and the heat of adsorption.

[0118] Furthermore, in the refrigeration system 100, the heat transfer area of ​​the internal heat exchanger 138 is determined so that the COP is 1 or greater. Therefore, the refrigeration system 100 can be designed taking into account both the refrigeration capacity of the refrigeration system 100 and the size of the internal heat exchanger 138.

[0119] (3-2) The specific configuration of the circulating refrigeration system 200 of the second embodiment will be described with reference to the drawings. The basic configuration and operation of the refrigeration system 200 of the second embodiment are the same as those of the refrigeration system 100 of the first embodiment, so the differences between the refrigeration system 100 and the refrigeration system 200 will be explained in detail.

[0120] (3-2-1) Configuration of the Refrigeration System 200 The refrigeration system 200 of the second embodiment includes a refrigerant flow path 111 through which the refrigerant circulates, as shown in Figure 7. The refrigerant flow path 111 has the functions of both the refrigerant circuit 11 and the adsorption circuit 12 of Figure 1. The adsorbent flows together with the refrigerant through a portion of the refrigerant flow path 111. In other words, in the refrigeration system 200, the mixed fluid flows through the refrigerant flow path 111.

[0121] The refrigeration system 200 includes a compressor 131, an expansion mechanism 132, a first adsorbent 133, a second adsorbent 134, and an internal heat exchanger 138. The refrigeration system 200 further includes a switching mechanism 135, a first fan 136, a second fan 137, a first separation unit 141, and a merging unit 151. The refrigeration system 200 has a configuration in which the first separation unit 141 and the merging unit 151 are added to the refrigeration system 100 of the first embodiment.

[0122] The first separation unit 141 is a container or device that separates the mixed fluid in the refrigerant flow path 111 into refrigerant and adsorbent. The first separation unit 141 is, for example, a container having a mechanism for centrifuging the adsorbent by swirling the mixed fluid inside. The first separation unit 141 is connected to the first pipe 111a, the second pipe 111b, and the third pipe 111c. The first pipe 111a, the second pipe 111b, and the third pipe 111c are part of the refrigerant flow path 111. The first pipe 111a is connected to the outlet side of the low-pressure side flow path 138b of the internal heat exchanger 138 when the refrigerant flow path 111 is in the first state. The second pipe 111b is connected to the suction side of the compressor 131. The third pipe 111c is connected to the junction 151.

[0123] The confluence section 151 is a mechanism that combines the refrigerant discharged from the compressor 131 with the adsorbent that has undergone heat exchange in the internal heat exchanger 138. The confluence section 151 is, for example, an ejector mechanism. In other words, the confluence section 151 is configured to draw in the adsorbent by ejecting the refrigerant and causing it to expand under reduced pressure, and then mix the drawn-in adsorbent with the ejected refrigerant. The confluence section 151 is connected to the third pipe 111c, the fourth pipe 111d, and the fifth pipe 111e. The fourth pipe 111d and the fifth pipe 111e are part of the refrigerant flow path 111. The fourth pipe 111d is connected to the discharge side of the compressor 131. The fifth pipe 111e is connected to the inlet side of the first adsorbent 133 via a switching mechanism 135 when the refrigerant flow path 111 is in the first state.

[0124] The internal heat exchanger 138 performs heat exchange between the refrigerant and adsorbent between the first adsorbent 133 and the expansion mechanism 132, and between the refrigerant and adsorbent between the second adsorbent 134 and the suction side of the conveying mechanism (compressor 131).

[0125] (3-2-2) Operation of the refrigeration device 200: Assume that the refrigerant flow path 111 is in a first state. The mixed fluid, which has undergone heat exchange in the low-pressure side flow path 138b of the internal heat exchanger 138 after passing through the expansion mechanism 132 and the second adsorbent 134 in that order, flows through the first pipe 111a and into the first separation section 141. In the first separation section 141, the mixed fluid is separated into refrigerant and adsorbent. In addition, in the first separation section 141, the mixed fluid may be separated into a mixed fluid with a high proportion of refrigerant and a mixed fluid with a high proportion of adsorbent. In this case, a mixed fluid with a high proportion of refrigerant means a mixed fluid with a higher proportion of refrigerant than the mixed fluid with a higher proportion of refrigerant in the mixed fluid flowing through the first pipe 111a. A mixed fluid with a high proportion of adsorbent means a mixed fluid with a higher proportion of adsorbent than the mixed fluid with a higher proportion of adsorbent in the mixed fluid with a higher proportion of adsorbent in the mixed fluid flowing through the first pipe 111a. The mixed fluid with a high proportion of refrigerant separated in the first separation section 141 flows through the second pipe 111b and is supplied to the suction side of the compressor 131. The mixed fluid with a high proportion of adsorbent separated in the first separation section 141 flows through the third pipe 111c and is supplied to the confluence section 151. The high-pressure refrigerant compressed by the compressor 131 flows through the fourth pipe 111d and is supplied to the confluence section 151.

[0126] At the confluence 151, the refrigerant supplied from the fourth pipe 111d is depressurized and expanded. As a result, the adsorbent supplied from the third pipe 111c is drawn in and mixed with the depressurized and expanded refrigerant. The mixed fluid generated by the confluence of the refrigerant and adsorbent at the confluence 151 flows out into the fifth pipe 111e.

[0127] (3-2-3) Details of the refrigeration device 200 Similar to the first embodiment, the refrigeration device 200 has a coefficient of performance (COP) of 1 or more calculated by formula (1). The difference from the first embodiment is W ＭＯＦ This is the method for calculating the following. In the second embodiment, instead of formula (10), W ＭＯＦ This is calculated by the following formula (14). Formula (14): W ＭＯＦ =Gr ＣＯ２ × (h') Ｈ -h ｃｏｍｐ＿ｏｕｔ )

[0128] In equation (14), h' Ｈ This is the specific enthalpy [kJ / kg] of the refrigerant discharged from the confluence section 151. Ｈ This is calculated by the following formula (15): Formula (15): h' Ｈ =Ref(P') Ｈ )

[0129] In equation (15), P' Ｈ This is the pressure [Pa] of the refrigerant discharged from the confluence section 151.

[0130] In equation (15), Ref is a refrigerant property function that takes the pressure of the refrigerant as an argument and outputs the specific enthalpy of the refrigerant.

[0131] P' Ｈ This is calculated by the following formula (16): Formula (16): P' Ｈ = Fn(x)

[0132] In equation (16), x is the mixing ratio of the adsorbent and the refrigerant [dimensionless]. x is Gr ＭＯＦ / Gr ＣＯ２ It is calculated by . For the refrigerant to circulate within the refrigerant flow path 111, it is necessary that the amount of refrigerant sealed in the refrigerant flow path 111 is greater than the maximum amount of refrigerant that can be adsorbed by the adsorbent in the refrigerant flow path 111. Therefore, GrＣＯ２ , Gr ＭＯＦ It must be greater than ×Δm. Therefore, the upper limit of x is 1 / Δm.

[0133] In equation (16), Fn is P' Ｈ This is the inverse function of a function that takes as an argument and outputs x. Fn is a function that represents the characteristics of the merging section 151.

[0134] (3-2-4) Features In the refrigeration system 200, the adsorbent separated in the first separation unit 141 is not supplied to the suction side of the compressor 131. Specifically, the adsorbent separated in the first separation unit 141 bypasses the compressor 131 and merges with the refrigerant compressed by the compressor 131 on the discharge side of the compressor 131. As a result, the work performed by the compressor 131 on the mixed fluid is reduced, and the energy consumption of the refrigeration system 200 (W in equation (1)) is reduced. Consequently, the decrease in the COP of the refrigeration system 100 is reduced.

[0135] (3-3) The specific configuration of the circulating refrigeration system 300 of the third embodiment will be described with reference to the drawings. The basic configuration and operation of the refrigeration system 300 of the third embodiment are the same as those of the refrigeration system 100 of the first embodiment, so the differences between the refrigeration system 100 and the refrigeration system 300 will be explained in detail.

[0136] (3-3-1) Configuration of the Refrigeration System 300 The refrigeration system 300 of the third embodiment includes a refrigerant flow path 111 through which the refrigerant circulates, as shown in Figure 8. The refrigerant flow path 111 has the functions of both the refrigerant circuit 11 and the adsorption circuit 12 of Figure 1. The adsorbent flows together with the refrigerant through a portion of the refrigerant flow path 111. In other words, in the refrigeration system 300, the mixed fluid flows through the refrigerant flow path 111.

[0137] The refrigeration device 300 includes a compressor 131, an expansion mechanism 132, a first adsorbent 133, a second adsorbent 134, and an internal heat exchanger 138. The refrigeration device 300 further includes a switching mechanism 135, a first fan 136, a second fan 137, a first separation unit 141, and a discharge unit 152. The refrigeration device 300 has a configuration in which the first separation unit 141 and the discharge unit 152 are added to the refrigeration device 100 of the first embodiment.

[0138] The first separation unit 141 is a container or device that separates the mixed fluid in the refrigerant flow path 111 into refrigerant and adsorbent. The first separation unit 141 is, for example, a container having a mechanism for centrifuging the adsorbent by swirling the mixed fluid inside. The first separation unit 141 is connected to the first pipe 111a, the second pipe 111b, and the third pipe 111c. The first pipe 111a, the second pipe 111b, and the third pipe 111c are part of the refrigerant flow path 111. The first pipe 111a is connected to the outlet side of the low-pressure side flow path 138b of the internal heat exchanger 138 when the refrigerant flow path 111 is in a first state. The second pipe 111b is connected to the suction side of the compressor 131. The third pipe 111c is provided with a discharge unit 152. The third pipe 111c is connected to the sixth pipe 111f, which connects the discharge side of the compressor 131 to the switching mechanism 135. The sixth pipe 111f is part of the refrigerant flow path 111.

[0139] The delivery unit 152 is a transport mechanism that transports the adsorbent within the refrigerant flow path 111. For example, the delivery unit 152 is a powder pump that sucks in and discharges the adsorbent. The delivery unit 152 sends the adsorbent separated from the mixed fluid in the first separation unit 141 to the sixth pipe 111f. The delivery unit 152 sends the adsorbent, which has undergone heat exchange in the internal heat exchanger 138, to the discharge side of the compressor 131.

[0140] The internal heat exchanger 138 performs heat exchange between the refrigerant and adsorbent between the first adsorbent 133 and the expansion mechanism 132, and between the refrigerant and adsorbent between the second adsorbent 134 and the suction side of the transport mechanism (compressor 131 and delivery unit 152).

[0141] (3-3-2) Operation of the refrigeration device 300: Assume that the refrigerant flow path 111 is in a first state. The mixed fluid, which has undergone heat exchange in the low-pressure side flow path 138b of the internal heat exchanger 138 after passing through the expansion mechanism 132 and the second adsorbent 134 in that order, flows through the first pipe 111a and into the first separation section 141. In the first separation section 141, the mixed fluid is separated into refrigerant and adsorbent. The refrigerant separated in the first separation section 141 flows through the second pipe 111b and is supplied to the suction side of the compressor 131. The adsorbent separated in the first separation section 141 flows through the third pipe 111c and is sent to the sixth pipe 111f by the discharge section 152. The high-pressure refrigerant compressed by the compressor 131 flows through the sixth pipe 111f. Therefore, in the sixth pipe 111f, the refrigerant discharged from the compressor 131 and the adsorbent delivered by the delivery unit 152 merge to form a mixed fluid.

[0142] (3-3-3) Details of the refrigeration device 300 Similar to the first embodiment, the refrigeration device 300 has a coefficient of performance (COP) of 1 or more calculated by formula (1). The difference from the first embodiment is W ＭＯＦ This is the method for calculating the following. In the third embodiment, instead of formula (10), W ＭＯＦ This is calculated by the following formula (17). Formula (17): W ＭＯＦ = (Gr ＭＯＦ / ρ ＭＯＦ ) × (P ｃｏｍｐ＿ｏｕｔ -P ｃｏｍｐ＿ｉｎ )

[0143] In equation (17), ρ ＭＯＦ The density of the adsorbent [kg / m³] ３ ]

[0144] In equation (17), P ｃｏｍｐ＿ｏｕｔ This is the pressure [Pa] on the discharge side of the delivery unit 152.

[0145] In equation (17), P ｃｏｍｐ＿ｉｎ This is the pressure [Pa] on the suction side of the discharge unit 152.

[0146] (3-3-4) Features In the refrigeration system 300, the adsorbent separated in the first separation unit 141 is not supplied to the suction side of the compressor 131. Specifically, the adsorbent separated in the first separation unit 141 bypasses the compressor 131 and merges with the refrigerant compressed by the compressor 131 on the discharge side of the compressor 131. As a result, the work performed by the compressor 131 on the mixed fluid is reduced, and the energy consumption of the refrigeration system 300 (W in equation (1)) is reduced. Consequently, the decrease in the COP of the refrigeration system 100 is reduced.

[0147] Furthermore, the refrigeration device 300 can efficiently combine the adsorbent, which has been heat-exchanged in the internal heat exchanger 138 and separated in the first separation unit 141, with the refrigerant discharged from the compressor 131, via the discharge unit 152.

[0148] (3-4) The specific configuration of the circulating refrigeration system 400 of the fourth embodiment will be described with reference to the drawings. The basic configuration and operation of the refrigeration system 400 of the fourth embodiment are the same as those of the refrigeration system 200 of the second embodiment, so the differences between the refrigeration system 200 and the refrigeration system 400 will be explained in detail.

[0149] (3-4-1) Configuration of the refrigeration device 400 The refrigeration device 400 of the fourth embodiment has a configuration in which a second separation unit 142 is added to the refrigeration device 200 of the second embodiment, as shown in Figure 9.

[0150] The second separation unit 142 is a container or device that separates the mixed fluid in the refrigerant flow path 111 into the refrigerant and the adsorbent. The second separation unit 142 has the same mechanism as the first separation unit 141.

[0151] The second separation section 142 separates the refrigerant that has passed through the second adsorbent 134 from the adsorbent material. The second separation section 142 is connected to the seventh pipe 111g, the eighth pipe 111h, and the ninth pipe 111i. The seventh pipe 111g, the eighth pipe 111h, and the ninth pipe 111i are part of the refrigerant flow path 111. The seventh pipe 111g is connected to the outlet side of the second adsorbent 134 when the refrigerant flow path 111 is in the first state. The eighth pipe 111h is connected to the suction side of the compressor 131. The ninth pipe 111i is connected to the inlet side of the low-pressure side flow path 138b of the internal heat exchanger 138 via the switching mechanism 135. The second pipe 111b and the eighth pipe 111h are connected to each other on the suction side of the compressor 131.

[0152] The internal heat exchanger 138 performs heat exchange between the refrigerant and adsorbent between the first adsorbent 133 and the expansion mechanism 132, and the refrigerant and adsorbent separated in the second separation section 142.

[0153] (3-4-2) Operation of the refrigeration device 400: Assume that the refrigerant flow path 111 is in a first state. The mixed fluid that has passed through the expansion mechanism 132 and the second adsorbent 134 in this order flows through the seventh pipe 111g and into the second separation section 142. In the second separation section 142, the mixed fluid is separated into refrigerant and adsorbent. In addition, in the second separation section 142, the mixed fluid may be separated into a mixed fluid with a high proportion of refrigerant and a mixed fluid with a high proportion of adsorbent. In this case, a mixed fluid with a high proportion of refrigerant means a mixed fluid with a higher proportion of refrigerant than the mixed fluid with a higher proportion of refrigerant in the mixed fluid flowing through the seventh pipe 111g. A mixed fluid with a high proportion of adsorbent means a mixed fluid with a higher proportion of adsorbent than the mixed fluid with a higher proportion of adsorbent in the mixed fluid flowing through the seventh pipe 111g. The mixed fluid with a high proportion of refrigerant separated in the second separation section 142 flows through the eighth pipe 111h and is supplied to the suction side of the compressor 131. The mixed fluid with a high proportion of adsorbent separated in the second separation section 142 flows through the ninth pipe 111i as a mixed fluid mixed with a small amount of refrigerant and enters the low-pressure side flow path 138b of the internal heat exchanger 138. The mixed fluid that has undergone heat exchange in the low-pressure side flow path 138b of the internal heat exchanger 138 flows through the first pipe 111a and enters the first separation section 141. The adsorbent content of the mixed fluid flowing through the ninth pipe 111i is higher than that of the mixed fluid flowing through the seventh pipe 111g.

[0154] (3-4-3) Features In the refrigeration system 400, most of the low-temperature refrigerant that has passed through the second adsorbent 134 is supplied to the suction side of the compressor 131 without passing through the low-pressure side passage 138b of the internal heat exchanger 138. This keeps the temperature of the refrigerant drawn into the compressor 131 low, thus preventing the temperature of the refrigerant discharged from the compressor 131 from exceeding a predetermined upper limit. In addition, the mixed fluid supplied from the second separation unit 142 to the low-pressure side passage 138b of the internal heat exchanger 138 has a high adsorbent content. Therefore, the adsorbent is efficiently heated in the low-pressure side passage 138b of the internal heat exchanger 138 and merges with the refrigerant discharged from the compressor 131, effectively reducing heat loss.

[0155] (3-5) The specific configuration of the circulating refrigeration system 500 of the fifth embodiment will be described with reference to the drawings. The basic configuration and operation of the refrigeration system 500 of the fifth embodiment are the same as those of the refrigeration system 300 of the third embodiment. The same reference numerals are used for the same components, and detailed explanations are omitted as appropriate. The following explanation will focus on the differences between the refrigeration system 300 and the refrigeration system 500.

[0156] (3-5-1) Configuration of the Refrigeration System 500 The refrigeration system 500 of the fifth embodiment has a configuration in which a second separation unit 142 is added to the refrigeration system 300 of the third embodiment, as shown in Figure 10.

[0157] (3-5-2) Operation of the refrigeration device 500: Assume that the refrigerant flow path 111 is in the first state. The mixed fluid that has passed through the expansion mechanism 132 and the second adsorbent 134 in this order flows through the seventh pipe 111g and into the second separation section 142. In the second separation section 142, the mixed fluid is separated into refrigerant and adsorbent. The refrigerant separated in the second separation section 142 flows through the eighth pipe 111h and is supplied to the suction side of the compressor 131. The adsorbent separated in the second separation section 142, as a mixed fluid mixed with a small amount of refrigerant, flows through the ninth pipe 111i and into the low-pressure side flow path 138b of the internal heat exchanger 138. The mixed fluid that has undergone heat exchange in the low-pressure side flow path 138b of the internal heat exchanger 138 flows through the first pipe 111a and into the first separation section 141. The adsorbent content of the mixed fluid flowing through the ninth pipe 111i is higher than that of the adsorbent content of the mixed fluid flowing through the seventh pipe 111g.

[0158] (3-5-3) Features In the refrigeration system 500, most of the low-temperature refrigerant that has passed through the second adsorbent 134 is supplied to the suction side of the compressor 131 without passing through the low-pressure side passage 138b of the internal heat exchanger 138. This keeps the temperature of the refrigerant drawn into the compressor 131 low, thus preventing the temperature of the refrigerant discharged from the compressor 131 from exceeding a predetermined upper limit. In addition, the mixed fluid supplied from the second separation unit 142 to the low-pressure side passage 138b of the internal heat exchanger 138 has a high adsorbent content and contains almost no refrigerant. Therefore, the adsorbent is efficiently heated in the low-pressure side passage 138b of the internal heat exchanger 138 and merges with the refrigerant discharged from the compressor 131, effectively reducing heat loss.

[0159] (4) Modified Examples (4-1) Modified Example A The specific configuration of the circulating refrigeration system 600 will be explained with reference to the drawings. The basic configuration and operation of the refrigeration system 600 in this modified example are the same as those of the refrigeration system 100 in the first embodiment, so the differences between the refrigeration system 100 and the refrigeration system 600 will be explained in detail.

[0160] (4-1-1) Configuration of the Refrigeration System 600 The refrigeration system 600 of this modified example, as shown in Figure 11, is equipped with an economizer 139 instead of an internal heat exchanger 138, and further includes a pressure reduction mechanism 140. The economizer 139 is a heat exchanger that, like the internal heat exchanger 138, has a high-pressure side flow path 139a and a low-pressure side flow path 139b inside. When the refrigerant flow path 111 is in a first state, the economizer 139 performs heat exchange between the high-pressure mixed fluid that has passed through the first adsorbent 133 and the low-pressure mixed fluid that has been heat-exchanged in the economizer 139 and reduced in pressure by the pressure reduction mechanism 140.

[0161] In the following, the refrigerant flow path 111 is assumed to be in a first state. The refrigeration device 600 has a tenth pipe 111j which is part of the refrigerant flow path 111. The tenth pipe 111j branches off from between the outlet side of the high-pressure side flow path 139a of the economizer 139 and the expansion mechanism 132, and is connected to the inlet side of the low-pressure side flow path 139b of the economizer 139. The outlet side of the low-pressure side flow path 139b of the economizer 139 is connected between the switching mechanism 135 and the suction side of the compressor 131. The pressure reducing mechanism 140 is provided in the tenth pipe 111j.

[0162] The economizer 139 performs heat exchange between the refrigerant and adsorbent between the first adsorbent 133 and the expansion mechanism 132, and the refrigerant and adsorbent that flows into the tenth pipe 111j and is depressurized by the depressurization mechanism 140.

[0163] In the refrigeration system 600, the heat transfer area of ​​the economizer 139 is determined such that the COP is 1 or greater.

[0164] (4-1-2) Operation of the refrigeration device 600: Assume that the refrigerant flow path 111 is in the first state. A portion of the high-pressure mixed fluid that flows out from the outlet side of the high-pressure side flow path 139a of the economizer 139 flows through the 10th pipe 111j and is depressurized by the depressurization mechanism 140. The low-pressure mixed fluid that has been depressurized by the depressurization mechanism 140 flows into the inlet side of the low-pressure side flow path 139b of the economizer 139. In the economizer 139, the adsorbent contained in the mixed fluid flowing through the low-pressure side flow path 139b is heated by the mixed fluid flowing through the high-pressure side flow path 139a. The mixed fluid that flows out from the outlet side of the low-pressure side flow path 139b of the economizer 139 merges with the mixed fluid that has passed through the second adsorbent 134 and is drawn into the compressor 131.

[0165] (4-1-3) Features In the refrigeration system 600, when the refrigerant flow path 111 is in the first state, the mixed fluid flowing through the low-pressure side flow path 139b of the economizer 139 is heated by heat exchange with the mixed fluid flowing through the high-pressure side flow path 139a of the economizer 139. Therefore, similar to the refrigeration system 100 of the first embodiment, the adsorbent flowing in the low-pressure region of the refrigerant flow path 111 is heated by heat exchange with the mixed fluid flowing in the high-pressure region and is drawn into the compressor 131. Thus, the refrigeration system 600 can reduce the decrease in refrigeration capacity by reducing heat loss caused by the adsorbent being heated by the compressed refrigerant and heat of adsorption after passing through the compressor 131.

[0166] In this modified example, the tenth pipe 111j may branch off between the outlet side of the first adsorbent 133 and the inlet side of the high-pressure side flow path 139a of the economizer 139 and be connected to the inlet side of the low-pressure side flow path 139b of the economizer 139.

[0167] Furthermore, the refrigeration systems 200, 300, 400, and 500 of the second to fifth embodiments may be equipped with an economizer 139 instead of an internal heat exchanger 138.

[0168] (4-2) Modification B The specific configuration of the circulating refrigeration system 700 will be explained with reference to the drawings. The basic configuration and operation of the refrigeration system 700 of this modification are the same as those of the refrigeration system 100 of the first embodiment, so the differences between the refrigeration system 100 and the refrigeration system 700 will be explained in detail.

[0169] (4-2-1) Configuration of the Refrigeration System 700 As shown in Figure 12, the refrigeration system 700 of this modified example is equipped with an economizer 139 instead of an internal heat exchanger 138, and further includes a pressure reduction mechanism 140 and a third separation unit 143. The economizer 139 is a heat exchanger that, like the internal heat exchanger 138, has a high-pressure side flow path 139a and a low-pressure side flow path 139b inside. When the refrigerant flow path 111 is in a first state, the economizer 139 performs heat exchange between the high-pressure mixed fluid that has passed through the first adsorbent 133 and the low-pressure mixed fluid that has been heat-exchanged in the economizer 139 and reduced in pressure by the pressure reduction mechanism 140.

[0170] The third separation unit 143 is a container or device that separates the mixed fluid in the refrigerant flow path 111 into the refrigerant and the adsorbent. The third separation unit 143 has the same mechanism as the first separation unit 141 and the second separation unit 142.

[0171] The third separation section 143 separates the refrigerant and the adsorbent between the first adsorbent 133 and the expansion mechanism 132. The third separation section 143 is connected to the 11th pipe 111k, the 12th pipe 111l, and the 13th pipe 111m. The 11th pipe 111k, the 12th pipe 111l, and the 13th pipe 111m are all part of the refrigerant flow path 111. The 11th pipe 111k is connected to the outlet side of the high-pressure side flow path 139a of the economizer 139 when the refrigerant flow path 111 is in the first state. The 12th pipe 111l is connected to the expansion mechanism 132. The 13th pipe 111m is connected to the inlet side of the low-pressure side flow path 139b of the economizer 139. The outlet side of the low-pressure side flow path 139b of the economizer 139 is connected between the switching mechanism 135 and the suction side of the compressor 131. The pressure reducing mechanism 140 is installed in the 13th pipe 111m.

[0172] The economizer 139 performs heat exchange between the refrigerant and adsorbent between the first adsorbent 133 and the expansion mechanism 132, and the refrigerant that flows into the 13th pipe 111m and is depressurized by the depressurization mechanism 140.

[0173] In the refrigeration system 700, the heat transfer area of ​​the economizer 139 is determined such that the COP is 1 or greater.

[0174] (4-2-2) Operation of the refrigeration device 700: Assume that the refrigerant flow path 111 is in a first state. The high-pressure mixed fluid that flows out from the high-pressure outlet of the economizer 139 flows through the 11th pipe 111k and into the third separation section 143. In the third separation section 143, the mixed fluid is separated into refrigerant and adsorbent. In the third separation section 143, the mixed fluid may be separated into a mixed fluid with a high proportion of refrigerant and a mixed fluid with a high proportion of adsorbent. In this case, the mixed fluid with a high proportion of refrigerant means a mixed fluid with a higher proportion of refrigerant than the mixed fluid with a higher proportion of refrigerant in the mixed fluid flowing through the 11th pipe 111k. The mixed fluid with a high proportion of adsorbent separated in the third separation section 143 flows through the 12th pipe 111l and is supplied to the expansion mechanism 132. The mixed fluid with a high proportion of refrigerant separated in the third separation section 143 flows through the thirteenth pipe 111m, is depressurized by the pressure reducing mechanism 140, and flows into the inlet side of the low-pressure side flow path 139b of the economizer 139. In the economizer 139, the refrigerant flowing through the low-pressure side flow path 139b is heated by the mixed fluid flowing through the high-pressure side flow path 139a. The refrigerant that flows out from the outlet side of the low-pressure side flow path 139b of the economizer 139 merges with the mixed fluid that has passed through the second adsorbent 134 and is drawn into the compressor 131.

[0175] (4-2-3) Features In the refrigeration system 700, when the refrigerant flow path 111 is in the first state, the refrigerant flowing through the low-pressure side flow path 139b of the economizer 139 is heated by heat exchange with the mixed fluid flowing through the high-pressure side flow path 139a of the economizer 139. As a result, the low-pressure refrigerant heated in the low-pressure side flow path 139b of the economizer 139 merges with the low-pressure mixed fluid that has passed through the second adsorbent 134. As a result, the adsorbent contained in the low-pressure mixed fluid that has passed through the second adsorbent 134 is heated and drawn into the compressor 131. Therefore, the refrigeration system 700 can reduce the decrease in refrigeration capacity by reducing heat loss caused by the adsorbent being heated by the compressed refrigerant and heat of adsorption after passing through the compressor 131.

[0176] In this modified example, a third separation unit 143 may be positioned between the outlet side of the first adsorbent 133 and the inlet side of the high-pressure side flow path 139a of the economizer 139. In this case, the mixed fluid flowing out of the first adsorbent 133 is separated into refrigerant and adsorbent in the third separation unit 143. The mixed fluid with a high proportion of adsorbent separated in the third separation unit 143 flows into the inlet side of the high-pressure side flow path 139a of the economizer 139. The mixed fluid with a high proportion of refrigerant separated in the third separation unit 143 is depressurized by the depressurization mechanism 140 and flows into the inlet side of the low-pressure side flow path 139b of the economizer 139.

[0177] Furthermore, the refrigeration systems 200, 300, 400, and 500 of the second to fifth embodiments may be equipped with an economizer 139 instead of an internal heat exchanger 138.

[0178] (4-3) Modification C In each of the first to fifth embodiments of the refrigeration system, the COP calculated by formula (1) is 1 or more. In these refrigeration systems, the heat transfer area of ​​the internal heat exchanger 138 is determined so that the COP is 1 or more. However, in these refrigeration systems, the heat transfer area of ​​the internal heat exchanger 138 may be determined so that the COP is 1.67 or more. In this case, the COP of each of the first to fifth embodiments of the refrigeration system is 1.67 or more.

[0179] Furthermore, this modification is also applicable to modifications A and B.

[0180] (4-4) Modification D Each of the first to fifth embodiments of the refrigeration apparatus uses MOF powder as the adsorbent. However, these refrigeration apparatuses may also use liquid MOF as the adsorbent. Liquid MOF is a mixture of MOF powder and a solvent. The concentration of MOF contained in the liquid MOF is preferably 50 wt% or more.

[0181] When using liquid MOF as an adsorbent, Q ｌｇ Q is calculated using the following formula (18). Formula (18): Q ｌｇ = Q ｌｇ＿ｍａｘ ×r ｌｇ = (Q ｌｇ＿ＭＯＦ＿ｍａｘ +Q ｌｇ＿ＣＯ２＿ｍａｘ +Q ｌｇ＿ｓｏｌｖｅｎｔ＿ｍａｘ ) × r ｌｇ

[0182] In equation (18), Q ｌｇ＿ｍａｘ Q ｌｇ＿ＭＯＦ＿ｍａｘ and Q ｌｇ＿ＣＯ２＿ｍａｘ and Q ｌｇ＿ｓｏｌｖｅｎｔ＿ｍａｘ It is the sum of the two.

[0183] In equation (18), Q ｌｇ＿ｓｏｌｖｅｎｔ＿ｍａｘ This is the maximum amount of thermal or cold energy [kW] that can be recovered from the solvent contained in the liquid MOF.

[0184] Q ｌｇ＿ｓｏｌｖｅｎｔ＿ｍａｘ Q is calculated using the following formula (19). Formula (19): Q ｌｇ＿ｓｏｌｖｅｎｔ＿ｍａｘ =Gr ｓｏｌｖｅｎｔ ×C ｓｏｌｖｅｎｔ × (T ａｄｓ＿ｏｕｔ＿ｓｏｌｖｅｎｔ -T ｄｅｓ＿ｏｕｔ＿ｓｏｌｖｅｎｔ )

[0185] In equation (19), Gr ｓｏｌｖｅｎｔ This is the solvent circulation rate [kg(solvent) / s]. In other words, Gr ｓｏｌｖｅｎｔ This is the weight of the solvent flowing through the refrigerant channel 111 per second.

[0186] In equation (19), C ｓｏｌｖｅｎｔ This is the specific heat of the solvent [kJ / (kg·K)].

[0187] In equation (19), T ａｄｓ＿ｏｕｔ＿ｓｏｌｖｅｎｔ This is the outlet temperature [K] of the first adsorbent 133. In other words, T ａｄｓ＿ｏｕｔ＿ｓｏｌｖｅｎｔ This is the temperature of the solvent immediately after it flows out of the first adsorbent 133.

[0188] In equation (19), T ｄｅｓ＿ｏｕｔ＿ｓｏｌｖｅｎｔ This is the outlet temperature [K] of the second adsorbent 134. In other words, T ｄｅｓ＿ｏｕｔ＿ｓｏｌｖｅｎｔ This is the temperature of the solvent immediately after it flows out of the second adsorbent 134.

[0189] When using liquid MOF as the adsorbent, W in the third embodiment ＭＯＦ This is calculated by the following formula (20). Formula (20): W ＭＯＦ = (Gr ＭＯＦ / ρ ＭＯＦ +Gr ｓｏｌｖｅｎｔ / ρ ｓｏｌｖｅｎｔ ) × (P ｃｏｍｐ＿ｏｕｔ -P ｃｏｍｐ＿ｉｎ )

[0190] In equation (20), ρ ｓｏｌｖｅｎｔ This is the density of the solvent [kg / m³] ３ ]

[0191] Furthermore, this modification is also applicable to modifications A and B.

[0192] (4-5) Modification E The adsorbent used in the refrigeration units 100, 200, 300, 400, 500, 600, and 700 is a metal-organic structure. However, materials other than metal-organic structures may be used as the adsorbent. Examples of materials other than metal-organic structures include activated carbon, zeolite-based materials, silica-based materials, and alumina-based materials.

[0193] (4-6) Modification F The specific configuration of the circulating refrigeration system 800 will be explained with reference to the drawings. The basic configuration and operation of the refrigeration system 800 of this modification are the same as those of the refrigeration system 100 of the first embodiment, so the differences between the refrigeration system 100 and the refrigeration system 800 will be explained in detail.

[0194] (4-6-1) Configuration of the Refrigeration System 800 The refrigeration system 800 of this modified example comprises a refrigerant flow path 111 and a heat transfer medium flow path 112, as shown in Figure 13. The refrigerant flow path 111 has the same functions as the refrigerant circuit 11 and adsorption circuit 12 of Figure 1. A mixed fluid flows through the refrigerant flow path 111. A heat transfer medium circulates through the heat transfer medium flow path 112. The heat transfer medium is, for example, water.

[0195] The refrigeration system 800 includes a first heat exchanger 161 and a second heat exchanger 162 instead of an internal heat exchanger 138. The refrigeration system 800 further includes a heat transfer medium pump 171.

[0196] The first heat exchanger 161 performs heat exchange between a mixed fluid flowing through a refrigerant flow path 111 and a heat transfer medium flowing through a heat transfer medium flow path 112. The first heat exchanger 161 has a first heat exchange flow path 161a connected to the refrigerant flow path 111 through which the mixed fluid flows, and a second heat exchange flow path 161b connected to the heat transfer medium flow path 112 through which the heat transfer medium flows. The type of the first heat exchanger 161 is not limited as long as it has a first heat exchange flow path 161a and a second heat exchange flow path 161b inside. For example, the first heat exchanger 161 is a double-tube heat exchanger and a plate heat exchanger.

[0197] The second heat exchanger 162 performs heat exchange between the mixed fluid flowing in the refrigerant flow path 111 and the heat transfer medium flowing in the heat transfer medium flow path 112. The second heat exchanger 162 has a third heat exchange flow path 162a connected to the refrigerant flow path 111 through which the mixed fluid flows, and a fourth heat exchange flow path 162b connected to the heat transfer medium flow path 112 through which the heat transfer medium flows. The type of the second heat exchanger 162 is not limited as long as it has the third heat exchange flow path 162a and the fourth heat exchange flow path 162b inside. For example, the second heat exchanger 162 can be a double-tube heat exchanger or a plate heat exchanger.

[0198] In the refrigerant flow path 111, the first heat exchanger 161 is provided between the first adsorbent 133 and the expansion mechanism 132. In other words, the first heat exchange flow path 161a is connected to the first adsorbent 133 and the expansion mechanism 132. In the refrigerant flow path 111, the second heat exchanger 162 is provided between the second adsorbent 134 and the switching mechanism 135. In other words, the third heat exchange flow path 162a is connected to the second adsorbent 134 and the switching mechanism 135.

[0199] In the heat transfer medium flow path 112, the first heat exchanger 161 and the second heat exchanger 162 are connected in a ring. In other words, the second heat exchange flow path 161b and the fourth heat exchange flow path 162b form an annular flow path. The heat transfer medium pump 171 is installed between the second heat exchange flow path 161b and the fourth heat exchange flow path 162b. The heat transfer medium pump 171 delivers the heat transfer medium in the heat transfer medium flow path 112 and supplies the heat transfer medium to the first heat exchanger 161 and the second heat exchanger 162.

[0200] The control unit 105 further controls the rotation speed of the heat transfer fluid pump 171. The control unit 105 further controls the timing for starting the heat transfer fluid pump 171 and the timing for stopping the heat transfer fluid pump 171.

[0201] In the refrigeration system 800, the heat transfer area of ​​the first heat exchanger 161 and the second heat exchanger 162 is determined such that the COP is 1 or greater. Alternatively, in the refrigeration system 800, the heat transfer area of ​​the first heat exchanger 161 and the second heat exchanger 162 may be determined such that the COP is 1.67 or greater.

[0202] (4-6-2) When the refrigerant flow path 111 of the refrigeration system 800 is in the first state, the first heat exchanger 161 performs heat exchange between the high-pressure mixed fluid that has passed through the compressor 131 and the first adsorbent 133 in that order and the heat transfer medium circulating in the heat transfer medium flow path 112. When the refrigerant flow path 111 is in the first state, the second heat exchanger 162 performs heat exchange between the low-pressure mixed fluid that has passed through the expansion mechanism 132 and the second adsorbent 134 in that order and the heat transfer medium circulating in the heat transfer medium flow path 112. Therefore, the first heat exchanger 161 and the second heat exchanger 162 perform heat exchange between the mixed fluid between the first adsorbent 133 and the expansion mechanism 132 and the mixed fluid containing the refrigerant that has passed through the first heat exchanger 161 and been depressurized, via the heat transfer medium.

[0203] When the refrigerant flow path 111 is in the second state, the first heat exchanger 161 performs heat exchange between the low-pressure mixed fluid that has passed through the second adsorbent 134 and the expansion mechanism 132 in that order and the heat transfer medium circulating in the heat transfer medium flow path 112. When the refrigerant flow path 111 is in the second state, the second heat exchanger 162 performs heat exchange between the high-pressure mixed fluid that has passed through the first adsorbent 133 and the compressor 131 in that order and the heat transfer medium circulating in the heat transfer medium flow path 112. Therefore, the first heat exchanger 161 and the second heat exchanger 162 perform heat exchange between the mixed fluid between the compressor 131 and the second adsorbent 134 and the mixed fluid containing the refrigerant that has passed through the second heat exchanger 162 and been depressurized, via the heat transfer medium.

[0204] (4-6-3) Features When the refrigerant flow path 111 is in the first state, in the first heat exchanger 161, the heat transfer medium flowing through the second heat exchange flow path 161b is heated by heat exchange with the high-pressure mixed fluid flowing through the first heat exchange flow path 161a. The heat transfer medium heated in the first heat exchanger 161 is supplied to the second heat exchanger 162. In the second heat exchanger 162, the adsorbent contained in the low-pressure mixed fluid flowing through the third heat exchange flow path 162a is heated by heat exchange with the heat transfer medium heated in the first heat exchanger 161 and flowing through the fourth heat exchange flow path 162b. The mixed fluid containing the adsorbent heated in the second heat exchanger 162 is drawn into the compressor 131. Therefore, the refrigeration system 800 can reduce the decrease in refrigeration capacity by reducing heat loss due to the adsorbent being heated by the compressed refrigerant and heat of adsorption after passing through the compressor 131.

[0205] Furthermore, this modification is also applicable to the second to fifth embodiments and modifications A and B. When applied to the second to fifth embodiments, as shown in Figure 13, the internal heat exchanger 138 is replaced with the first heat exchanger 161 and the second heat exchanger 162 to provide a heat medium flow path 112 having a heat medium pump 171. When applied to modifications A and B, as shown in Figure 13, the economizer 139 is replaced with the first heat exchanger 161 and the second heat exchanger 162 to provide a heat medium flow path 112 having a heat medium pump 171.

[0206] (4-7) Modification G The specific configuration of the circulating refrigeration system 900 will be explained with reference to the drawings. The basic configuration and operation of the refrigeration system 900 of this modification are the same as those of the refrigeration system 100 of the first embodiment, so the differences between the refrigeration system 100 and the refrigeration system 900 will be explained in detail.

[0207] (4-7-1) Configuration of the Refrigeration Device 900 The refrigeration device 900 of this modified example comprises a refrigerant flow path 111, a first heat transfer medium flow path 113, and a second heat transfer medium flow path 114, as shown in Figure 14. The refrigerant flow path 111 has the same functions as the refrigerant circuit 11 and adsorption circuit 12 of Figure 1. A mixed fluid flows through the refrigerant flow path 111. A heat transfer medium flows through the first heat transfer medium flow path 113 and the second heat transfer medium flow path 114. The heat transfer medium is, for example, water.

[0208] The refrigeration system 900 includes a first heat exchanger 181 and a second heat exchanger 182 instead of an internal heat exchanger 138. The refrigeration system 900 further includes a first heat transfer fluid pump 191 and a second heat transfer fluid pump 192.

[0209] The first heat exchanger 181 performs heat exchange between a mixed fluid flowing through a refrigerant flow path 111 and a heat transfer medium flowing through a first heat transfer medium flow path 113. The first heat exchanger 181 has a first heat exchange flow path 181a connected to the refrigerant flow path 111 through which the mixed fluid flows, and a second heat exchange flow path 181b connected to the first heat transfer medium flow path 113 through which the heat transfer medium flows. The type of the first heat exchanger 181 is not limited as long as it has a first heat exchange flow path 181a and a second heat exchange flow path 181b inside. For example, the first heat exchanger 181 is a double-tube heat exchanger and a plate heat exchanger.

[0210] The second heat exchanger 182 performs heat exchange between the mixed fluid flowing in the refrigerant flow path 111 and the heat transfer medium flowing in the second heat transfer medium flow path 114. The second heat exchanger 182 has a third heat exchange flow path 182a connected to the refrigerant flow path 111 through which the mixed fluid flows, and a fourth heat exchange flow path 182b connected to the second heat transfer medium flow path 114 through which the heat transfer medium flows. The type of the second heat exchanger 182 is not limited as long as it has the third heat exchange flow path 182a and the fourth heat exchange flow path 182b inside. For example, the second heat exchanger 182 is a double-tube heat exchanger and a plate heat exchanger.

[0211] In the refrigerant flow path 111, the first heat exchanger 181 is provided between the first adsorbent 133 and the expansion mechanism 132. In other words, the first heat exchange flow path 181a is connected to the first adsorbent 133 and the expansion mechanism 132. In the refrigerant flow path 111, the second heat exchanger 182 is provided between the second adsorbent 134 and the switching mechanism 135. In other words, the third heat exchange flow path 182a is connected to the second adsorbent 134 and the switching mechanism 135.

[0212] The first heat transfer medium channel 113 is connected to a heat transfer medium supply source located outside the refrigeration device 900. The first heat transfer medium channel 113 is, for example, a channel through which the heat transfer medium circulates. The second heat exchange channel 181b of the first heat exchanger 181 is connected to the first heat transfer medium channel 113. The first heat transfer medium pump 191 is provided in the first heat transfer medium channel 113. The first heat transfer medium pump 191 delivers the heat transfer medium in the first heat transfer medium channel 113 and supplies the heat transfer medium to the first heat exchanger 181.

[0213] The second heat transfer medium passage 114 is connected to a heat transfer medium supply source located outside the refrigeration unit 900. The second heat transfer medium passage 114 is, for example, a passage through which the heat transfer medium circulates. The fourth heat exchange passage 182b of the second heat exchanger 182 is connected to the second heat transfer medium passage 114. The second heat transfer medium pump 192 is provided in the second heat transfer medium passage 114. The second heat transfer medium pump 192 delivers the heat transfer medium in the second heat transfer medium passage 114 and supplies the heat transfer medium to the second heat exchanger 182.

[0214] The control unit 105 further controls the rotational speed of the first heat transfer fluid pump 191 and the second heat transfer fluid pump 192. The control unit 105 further controls the timing for starting the first heat transfer fluid pump 191 and the second heat transfer fluid pump 192, and the timing for stopping the first heat transfer fluid pump 191 and the second heat transfer fluid pump 192.

[0215] In the refrigeration system 900, the heat transfer area of ​​the first heat exchanger 181 and the second heat exchanger 182 is determined such that the COP is 1 or greater. Alternatively, in the refrigeration system 900, the heat transfer area of ​​the first heat exchanger 181 and the second heat exchanger 182 may be determined such that the COP is 1.67 or greater.

[0216] (4-7-2) When the refrigerant flow path 111 of the refrigeration system 900 is in the first state, the first heat exchanger 181 performs heat exchange between the high-pressure mixed fluid that has passed through the compressor 131 and the first adsorbent 133 in that order and the heat transfer medium flowing through the first heat transfer medium flow path 113. The temperature of the heat transfer medium flowing through the second heat exchange flow path 181b is lower than the temperature of the mixed fluid flowing through the first heat exchange flow path 181a. Therefore, in the first heat exchanger 181, the heat transfer medium recovers heat from the high-pressure mixed fluid. When the refrigerant flow path 111 is in the first state, the second heat exchanger 182 performs heat exchange between the low-pressure mixed fluid that has passed through the expansion mechanism 132 and the second adsorbent 134 in that order and the heat transfer medium flowing through the second heat transfer medium flow path 114. The temperature of the heat transfer medium flowing through the fourth heat exchange flow path 182b is higher than the temperature of the mixed fluid flowing through the third heat exchange flow path 182a. Therefore, in the second heat exchanger 182, the heat transfer medium recovers cold energy from a low-pressure mixed fluid.

[0217] When the refrigerant flow path 111 is in the second state, the first heat exchanger 181 performs heat exchange between the low-pressure mixed fluid that has passed through the second adsorbent 134 and the expansion mechanism 132 in that order, and the heat transfer medium flowing through the first heat transfer medium flow path 113. The temperature of the heat transfer medium flowing through the second heat exchange flow path 181b is higher than the temperature of the mixed fluid flowing through the first heat exchange flow path 181a. Therefore, in the first heat exchanger 181, the heat transfer medium recovers cold energy from the low-pressure mixed fluid. When the refrigerant flow path 111 is in the second state, the second heat exchanger 182 performs heat exchange between the high-pressure mixed fluid that has passed through the first adsorbent 133 and the compressor 131 in that order, and the heat transfer medium flowing through the second heat transfer medium flow path 114. The temperature of the heat transfer medium flowing through the fourth heat exchange flow path 182b is lower than the temperature of the mixed fluid flowing through the third heat exchange flow path 182a. Therefore, in the second heat exchanger 182, the heat transfer medium recovers heat from a high-pressure mixed fluid.

[0218] (4-7-3) Features When the refrigerant flow path 111 is in the first state, in the second heat exchanger 182, the adsorbent contained in the low-pressure mixed fluid flowing through the third heat exchange flow path 182a is heated by the heat transfer medium flowing through the fourth heat exchange flow path 182b. The mixed fluid containing the adsorbent heated in the second heat exchanger 182 is drawn into the compressor 131. Therefore, the refrigeration system 900 can reduce the decrease in refrigeration capacity by reducing heat loss caused by the adsorbent being heated by the compressed refrigerant and heat of adsorption after passing through the compressor 131.

[0219] Furthermore, in this modified example, the refrigeration device 900 does not need to include the first heat exchanger 181, the first heat transfer medium flow path 113, and the first heat transfer medium pump 191.

[0220] Furthermore, this modification is also applicable to the second to fifth embodiments and modifications A and B. When applied to the second to fifth embodiments, as shown in Figure 14, the internal heat exchanger 138 is replaced with the first heat exchanger 181 and the second heat exchanger 182, and a first heat medium flow path 113 having a first heat medium pump 191 and a second heat medium flow path 114 having a second heat medium pump 192 are provided. When applied to modifications A and B, as shown in Figure 14, the economizer 139 is replaced with the first heat exchanger 181 and the second heat exchanger 182, and a first heat medium flow path 113 having a first heat medium pump 191 and a second heat medium flow path 114 having a second heat medium pump 192 are provided.

[0221] While embodiments of this disclosure have been described above, it should be understood that various modifications to the form and details are possible without departing from the spirit and scope of this disclosure as described in the claims.

[0222] 100: Refrigeration unit 111j: 10th piping (1st flow path) 111m: 13th piping (1st flow path) 131: Compressor (transport mechanism) 132: Expansion mechanism (pressure reduction section) 133: 1st adsorber (1st heat recovery section, 2nd heat recovery section) 134: 2nd adsorber (1st heat recovery section, 2nd heat recovery section) 138: Internal heat exchanger (heat exchange section) 139: Economizer (heat exchange section) 140: Pressure reduction mechanism (2nd pressure reduction section) 142: 2nd separation section (separation section) 143: 3rd separation section (separation section) 151: Confluence section 152: Discharge section 200: Refrigeration unit 300: Refrigeration unit 400: Refrigeration unit 500: Refrigeration unit 600: Refrigeration unit 700 Refrigeration equipment

[0223] U.S. Patent Application Publication No. 2023 / 0417459

Claims

1. A refrigeration system comprising: a transport mechanism including a compressor (131); a first heat recovery unit (133, 134) from which heat generated when the adsorbent material adsorbs the refrigerant is recovered; a second heat recovery unit (133, 134) from which cold energy generated when the adsorbent material desorbs the refrigerant is recovered; a depressurization unit (132) from which the refrigerant is depressurized; and a heat exchange unit (138, 139) provided between the first heat recovery unit and the depressurization unit, wherein the heat exchange unit performs heat exchange between the refrigerant and the adsorbent between the first heat recovery unit and the depressurization unit, and the refrigerant and the adsorbent that have passed through the heat exchange unit and been depressurized, and the COP calculated by the following formula (I) is 1 or more. Refrigeration equipment (100, 200, 300, 400, 500, 600, 700). Formula (I): COP=(Q ａｄｓ - Q ｌｇ＿ｍａｘ × (1-r) ｌｇ )) / W (in the formula, Q ａｄｓ Q is the amount of heat generated when the adsorbent adsorbs the refrigerant in the first heat recovery unit, and ｌｇ＿ｍａｘ r is the amount of thermal energy recovered from the refrigerant and the adsorbent in the heat exchange section, the reduced pressure section, and the second heat recovery section, and r ｌｇ Q is the amount of heat recovered from the refrigerant and the adsorbent in the heat exchange section. ｌｇ＿ｍａｘ This is the value obtained by dividing by , where W is the input to the transport mechanism.

2. The refrigeration apparatus according to claim 1, further comprising a confluence section (151) for confluence with the refrigerant discharged from the compressor and the adsorbent that has undergone heat exchange in the heat exchange section.

3. The refrigeration apparatus according to claim 1, wherein the transport mechanism further includes a delivery section (152) that sends the adsorbent, which has undergone heat exchange in the heat exchange section, to the discharge side of the compressor.

4. The refrigeration apparatus according to any one of claims 1 to 3, wherein the heat exchange unit performs heat exchange between the refrigerant and the adsorbent between the first heat recovery unit and the reduced pressure unit, and between the refrigerant and the adsorbent between the second heat recovery unit and the suction side of the transport mechanism.

5. The refrigeration apparatus according to claim 4, further comprising a separation unit (142) for separating the refrigerant and the adsorbent that have passed through the second heat recovery unit, wherein the heat exchange unit performs heat exchange between the refrigerant and the adsorbent between the first heat recovery unit and the reduced pressure unit, and the refrigerant and the adsorbent separated in the separation unit.

6. The refrigeration apparatus according to any one of claims 1 to 3, further comprising: a first flow path (111j, 111m) that branches off from the refrigerant flow path between the first heat recovery unit and the depressurization unit, passes through the heat exchange unit, and is connected to the suction side of the transport mechanism; and a second depressurization unit (140) provided in the first flow path, wherein the heat exchange unit performs heat exchange between the refrigerant and the adsorbent between the first heat recovery unit and the depressurization unit, and the refrigerant and the adsorbent that flows into the first flow path and is depressurized by the second depressurization unit.

7. The refrigeration apparatus according to claim 6, further comprising a separation unit (143) between the first heat recovery unit and the pressure reduction unit for separating the refrigerant and the adsorbent, wherein the separation unit is connected to the first flow path, and the second pressure reduction unit reduces the pressure of the refrigerant flowing out from the separation unit.

8. A refrigeration apparatus according to any one of claims 1 to 7, wherein the COP is 1.67 or higher.

9. The refrigeration apparatus according to any one of claims 1 to 8, wherein the adsorbent comprises a metal-organic structure containing a metal ion and an organic ligand.

10. The refrigeration apparatus according to any one of claims 1 to 9, wherein the refrigerant comprises at least one of carbon dioxide, hydrocarbons, ammonia, water, HFCs, and HFOs.

11. A refrigeration device in which a refrigerant and an adsorbent that adsorbs and desorbs the refrigerant in response to a change in the pressure of the refrigerant circulate, the refrigeration device including: a transport mechanism including a compressor (131); a first heat recovery unit (133, 134) that recovers the heat generated when the adsorbent adsorbs the refrigerant; a second heat recovery unit (133, 134) that recovers the cold heat generated when the adsorbent desorbs the refrigerant; a decompression unit (132) that decompresses the refrigerant; a first heat exchange unit (181) that recovers the heat of the refrigerant discharged from the compressor and the adsorbent; and a second heat exchange unit (182) that passes through the first heat exchange unit and recovers the cold heat of the decompressed refrigerant and the adsorbent, the refrigeration device (900) having a COP calculated by the following formula (I) of 1 or more. Formula (I): COP = (Q ａｄｓ - Q ｌｇ＿ｍａｘ × (1 - r ｌｇ )) / W (where Q ａｄｓ is the amount of heat of the heat generated when the adsorbent adsorbs the refrigerant in the first heat recovery unit, Q ｌｇ＿ｍａｘ is the amount of heat of the heat recovered from the refrigerant and the adsorbent in the first heat exchange unit, the decompression unit, and the second heat recovery unit, r ｌｇ is the value obtained by dividing the amount of heat of the heat recovered from the refrigerant and the adsorbent in the first heat exchange unit by Q ｌｇ＿ｍａｘ , and W is the input of the transport mechanism.)

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