WO2005103577A1 - 調湿装置 - Google Patents
調湿装置 Download PDFInfo
- Publication number
- WO2005103577A1 WO2005103577A1 PCT/JP2005/007895 JP2005007895W WO2005103577A1 WO 2005103577 A1 WO2005103577 A1 WO 2005103577A1 JP 2005007895 W JP2005007895 W JP 2005007895W WO 2005103577 A1 WO2005103577 A1 WO 2005103577A1
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- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- air
- heat exchanger
- adsorbent
- compressor
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/1411—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
- B01D53/26—Drying gases or vapours
- B01D53/265—Drying gases or vapours by refrigeration (condensation)
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/1411—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
- F24F3/1429—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant alternatively operating a heat exchanger in an absorbing/adsorbing mode and a heat exchanger in a regeneration mode
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
Definitions
- the present invention relates to a humidity control device having a heat exchanger having a surface on which an adsorbent is supported, and more particularly to a measure for improving the dehumidifying ability and the humidifying ability.
- the humidity control device includes two adsorption elements having an adsorbent and a refrigerant circuit that performs a refrigeration cycle. This humidity control device performs a first operation of dehumidifying the first air with the first adsorption element and regenerating the second adsorption element with the second air heated by the condenser in the refrigerant circuit, and a second adsorption operation. A second operation of dehumidifying the first air with the arrival element and regenerating the first adsorption element with the second air heated by the condenser. These two operations are alternately repeated, and the dehumidified first air or the humidified second air is supplied to the room.
- the adsorption heat exchange is configured as a V and so-called fin “and” tube type heat exchange having a large number of plate-like fins and a copper tube penetrating the fins.
- An adsorbent is supported on the surfaces of the fins and the copper tube.
- moisture is adsorbed and desorbed by the adsorbent to dehumidify and circulate the flowing air, and the refrigerant flowing in the copper tube heats and cools the adsorbent.
- the present invention has been made in view of the above points, and an object of the present invention is to increase the discharge temperature of a compressor to increase the sensible heat amount of a discharged refrigerant, thereby absorbing moisture in an adsorbent. This is to increase the amount of desorption.
- a first solution is that a compressor (63), a first heat exchange (61), an expansion mechanism (65), and a second heat exchanger (62) are connected by piping and a refrigerant
- the circulation is configured to be reversible, and a refrigerant circuit (60) that performs a vapor compression refrigeration cycle, and absorbs moisture carried on the surfaces of the first heat exchanger (61) and the second heat exchanger (62).
- the compressor (63) further includes superheat control means (71) for increasing the superheat of the suction gas refrigerant of the compressor (63).
- the adsorbent in the first heat exchanger (61) or the second heat exchanger (62) functioning as an evaporator, the adsorbent is cooled by the circulating refrigerant and moisture in the air is adsorbed. Adsorbed on the agent.
- the second heat exchanger (62) or the first heat exchanger m ⁇ (61) functioning as a condenser the adsorbent is heated by the flowing refrigerant and the adsorbent is released into the air. Is done.
- the degree of superheat of the suction gas refrigerant of the compressor (63) since the degree of superheat of the suction gas refrigerant of the compressor (63) is increased, the temperature of the superheated gas refrigerant discharged from the compressor (63) is also increased.
- the heat exchange (61, 62) serving as a condenser since the higher temperature superheated gas refrigerant flows to the heat exchange (61, 62) serving as a condenser, the amount of sensible heat increases, the adsorbent in the condenser is further heated by the refrigerant, and the water content is reduced. The amount of desorption increases. Also, if the amount of desorbed water in the adsorbent increases, the amount of water adsorbed in the adsorbent converted from the condenser to the evaporator increases. As described above, the amount of adsorbed and desorbed water is increased, and the dehumidifying ability and the humidifying ability are improved.
- the superheat degree control means (71) makes an opening of an expansion valve (65) as an expansion mechanism smaller than a normal opening.
- a third solution is the first invention, wherein the superheat degree control means (71) is the first heat exchanger (61) or the second heat exchanger (62) serving as an evaporator. Increase the air volume.
- the fourth solution is the invention according to any one of the first to third aspects, wherein the superheat degree control means (71) controls the superheat degree of the suction gas refrigerant of the compressor (63) for a predetermined time.
- a switching means (72) for switching the circulation direction of the refrigerant after being raised for a while is provided.
- the suction gas refrigerant of the compressor (63) is operated at a normal degree of superheat for a while after the refrigerant circulation is switched, and thereafter, at a superheat degree increased for a predetermined time. Operate and switch the refrigerant circulation again. In this way, after the water is desorbed to some extent from the adsorbent at the time of normal superheat, the remaining water that cannot be completely desorbed is desorbed at the elevated superheat. Therefore, moisture is more efficiently and effectively desorbed than when the degree of superheat is increased throughout the entire operation.
- each of the heat exchangers (61, 62) is an upstream side through which a refrigerant flows when functioning as a condenser. It is configured as a parallel flow type in which air flows toward the downstream side where the refrigerant flows out from the air.
- the superheat degree control means (71) for increasing the superheat degree of the suction gas refrigerant of the compressor (63) is provided. Since the temperature of the superheated gas refrigerant increases and the amount of sensible heat of the refrigerant increases, the adsorbent for heat exchange (61, 62) serving as a condenser can be further heated. Thereby, the amount of desorbed water in the adsorbent can be increased. Accordingly, the amount of moisture adsorbed by the adsorbent of the heat exchange (61, 62) switched from the condenser to the evaporator can be increased. As a result, the humidifying ability and the dehumidifying ability can be improved.
- the expansion valve is used as a means for increasing the degree of superheat.
- the degree of opening of (65) is reduced or the amount of air blown by the heat exchange (61, 62) serving as an evaporator is increased, the degree of superheat can be easily and reliably increased.
- the circulation direction of the refrigerant is switched after the superheat degree of the suction gas refrigerant of the compressor (63) is increased by the superheat degree control means (71) for a predetermined time. Since the switching means (72) is provided, the water can be desorbed to some extent from the adsorbent at the time of normal superheat, and then the remaining water can be desorbed at the time of the superheat with the increased moisture. Thereby, the regeneration of the adsorbent in the condenser without increasing the input of the compressor (63) so much can be performed effectively as compared with the case where the degree of superheat is increased throughout the entire operation.
- the heat exchangers (61, 62) function as condensers, the refrigerant flow and the air flow are made to flow in parallel. Air having a low relative humidity can flow through the portion where the gas refrigerant flows. As a result, it is possible to ensure that the water desorbed by the high-temperature gas refrigerant in a larger amount than the other parts is given to the air. Therefore, compared with the case of the counterflow type, the amount of desorbed water can be increased by effectively using the high-temperature superheated gas refrigerant.
- FIG. 1 is a schematic configuration diagram showing a humidity control apparatus according to an embodiment.
- FIG. 2 is a perspective view showing an adsorption heat exchanger according to the embodiment.
- FIG. 3 is a circuit diagram showing a refrigerant circuit of the humidity control apparatus according to the embodiment.
- FIG. 4 is a diagram schematically showing a condenser when a flow of a refrigerant and a flow of air are parallel flows.
- FIG. 5 is a diagram schematically showing a condenser in a case where the flow of the refrigerant and the flow of air are countercurrent.
- FIG. 6 is an adsorption isotherm showing the adsorption characteristics of zeolite and silica gel.
- FIG. 7 is a schematic configuration diagram of a humidity control apparatus showing a flow of air in a first operation during a dehumidifying operation according to the first embodiment.
- FIG. 8 is a schematic configuration diagram of a humidity control apparatus showing a flow of air in a second operation during a dehumidifying operation according to the first embodiment.
- FIG. 9 is a schematic configuration diagram of a humidity control apparatus showing a flow of air in a first operation during a humidification operation according to Embodiment 1.
- FIG. 10 is a schematic configuration diagram of a humidity control apparatus showing a flow of air in a second operation during a humidification operation according to Embodiment 1.
- FIG. 11 is a Mollier diagram showing behavior of a refrigerant in a refrigerant circuit.
- the humidity control apparatus (10) of the present embodiment performs dehumidification and humidification of room air, and includes a hollow rectangular parallelepiped box-shaped casing (11).
- the casing (11) houses a refrigerant circuit (60) and the like.
- the refrigerant circuit (60) includes a compressor (63), a four-way switching valve (64) as a flow path switching means,
- This is a closed circuit in which the adsorption heat exchange (61), the expansion valve (65) as an expansion mechanism, and the second adsorption heat exchange (62) are connected in order, and are filled with a refrigerant.
- the refrigerant circuit (60) is configured so that the charged refrigerant circulates to perform a vapor compression refrigeration cycle. The details of the refrigerant circuit (60) will be described later.
- the lower side is the front side of the casing (11), and the upper side is the casing (11).
- the casing (11) is formed in a flat box shape having a substantially square shape in plan view.
- the left side plate (12) and the right side plate (13), and the front plate (14) and the rear plate (15) are located in the thickness direction of the casing (11), and are mutually separated. It comprises two opposing end faces.
- the left side plate (12) has an outdoor air intake (21) formed near the rear plate (15), and an indoor air intake (22) formed near the front plate (14).
- an exhaust air outlet (23) is formed near the back plate (15), and an air supply air outlet (24) is formed near the front plate (14).
- the outdoor air inlet (21) and the indoor air inlet (22) constitute an air inlet, and the exhaust outlet (23) and the supply air outlet (24) constitute an air outlet. ing.
- a first partition plate (31) is provided upright toward the right side plate (13) from the center in the left-right direction.
- the internal space (16) of the casing (11) is partitioned left and right by a first partition plate (31).
- the right side of the first partition plate (31) becomes the first space (17), and the left side of the first partition plate (31) becomes the second space (18).
- the first space (17) of the casing (11) is divided into a front space and a back space by a seventh partition plate (37).
- the compressor (63) and the exhaust fan (26) of the refrigerant circuit (60) are arranged in a space on the back side of the first space (17).
- an expansion valve (65) and a four-way switching valve (64) of the refrigerant circuit (60) are also arranged in the space on the rear side (not shown).
- an air supply fan (25) is arranged in a space on the front side in the first space (17).
- the exhaust fan (26) is connected to an exhaust outlet (23), and the air supply fan (25) is connected to an air outlet (24).
- a second partition (32), a third partition (33), and a sixth partition (36) are provided in the second space (18) of the casing (11).
- the second partition plate (32) is set up near the front plate (14), and the third partition plate (33) is set up near the back plate (15).
- the second space (18) is partitioned into three spaces by a second partition plate (32) and a third partition plate (33) with a frontal force and a backward force.
- the sixth partition plate (36) is provided in a space between the second partition plate (32) and the third partition plate (33).
- the sixth partition (36) is provided upright at the center in the left-right direction of the second space (18).
- the space between the second partition plate (32) and the third partition plate (33) is formed by a sixth partition plate (36). Is divided into right and left. Of these, the space on the right side constitutes a first heat exchange chamber (41), in which the first adsorption heat exchanger (61) is arranged. On the other hand, the space on the left side constitutes a second heat exchange chamber (42), in which the second adsorption heat exchange (62) is arranged. That is, the first heat exchange chamber (41) and the second heat exchange chamber (42) are arranged adjacent to each other.
- a fifth partition plate (35) is provided in a space between the third partition plate (33) and the rear plate (15) of the casing (11) in the second space (18). .
- the fifth partition plate (35) is provided so as to cross the center in the height direction of the space, and partitions the space up and down (see FIG. 1 (A)).
- the space above the fifth partition plate (35) forms a first inflow channel (43), and the space below the fifth partition plate (35) forms a first outflow channel (44).
- the first inflow path (43) communicates with the outdoor air suction port (21), and the first outflow path (44) communicates with the exhaust air outlet (23) via the exhaust fan (26).
- a fourth partition plate (34) is provided in the space between the second partition plate (32) and the front plate (14) of the casing (11) in the second space (18). ing.
- the fourth partition plate (34) is provided so as to cross the center in the height direction of the space, and partitions the space up and down (see FIG. 1 (C)).
- the space above the fourth partition plate (34) forms a second inflow channel (45), and the space below the fourth partition plate (34) forms a second outflow channel (46).
- the second inflow path (45) communicates with the indoor air suction port (22), and the second outflow path (46) communicates with the air supply outlet (24) via the air supply fan (25). I have.
- openings (51 to 54) are formed in the third partition plate (33) (see Fig. 1 (A)). These four openings (51 to 54) are located close to each other in the row and column direction, that is, are arranged in a grid pattern at the top, bottom, left and right.
- the first opening (51) connects the first inflow path (43) to the first heat exchange chamber (41), and the second opening (52) connects the first inflow path (43) to the first inflow path (43). 2 It communicates with the heat exchange chamber (42).
- the third opening (53) connects the first outflow passage (44) to the first heat exchange chamber (41), and the fourth opening (54) connects the first outflow passage (44) to the first outflow passage (44). 2 Communicates with the heat exchange chamber (42).
- openings (55 to 58) are formed in the second partition plate (32) (see Fig. 1 (C)). These four openings (55 to 58) are located close to each other in the row and column direction, that is, are arranged in two grids at the top, bottom, left and right.
- the fifth opening (55) is connected to the second inflow path (45) and the first inflow path (45).
- the sixth opening (56) communicates the second inflow path (45) and the second heat exchange chamber (42) with the heat exchange chamber (41).
- the seventh opening (57) connects the second outflow passage (46) with the first heat exchange chamber (41), and the eighth opening (58) connects the second outflow passage (46) with the second outflow passage (46). 2 Communicates with the heat exchange chamber (42).
- Each of the openings (51 to 58) of the third partition plate (33) and the second partition plate (32) is provided with a damper as an opening / closing means, though not shown. These dampers are configured to switch each opening (51-58) between an open state and a closed state by opening and closing, and to switch a flow path of the first air and the second air.
- each of the first adsorption heat exchanger (61) and the second adsorption heat exchanger (62) is a cross-fin type fin-and-tube heat exchanger. It is composed of Specifically, the first adsorption heat exchanger (61) and the second adsorption heat exchanger (62) include a large number of aluminum fins (6a) formed in a rectangular plate shape, and the fins (6a). And a copper heat transfer tube (6b) penetrating therethrough.
- an adsorbent capable of absorbing and desorbing moisture is carried by dip molding (immersion molding).
- the first adsorption heat exchanger (61) constitutes the first heat exchange
- the second adsorption heat exchange (62) constitutes the second heat exchange.
- the adsorbent is carried on the outer surfaces of the fins (13) and the heat transfer tubes (15) by dip molding.
- the present invention is not limited to this, as long as the performance as the adsorbent is not impaired.
- the adsorbent may be supported on the outer surface by any method.
- the four-way switching valve (64) of the refrigerant circuit (60) has a first port connected to the discharge side of the compressor (63), and a second port connected to the suction side of the compressor (63). It is connected.
- the third port of the four-way switching valve (64) is connected to the first adsorption heat exchanger (61), and the fourth port is connected to the second adsorption heat exchange (62).
- the refrigerant circuit (60) is configured such that the circulation direction of the refrigerant is switched by switching the four-way switching valve (64). That is, the four-way switching valve (64) is in a state where the first port and the third port are in communication with each other and at the same time the second port and the fourth port are in communication (the state shown in FIG. 3 (A)). And the first port and the fourth port communicate with each other while the second port and the third port The state switches to the state where the port communicates (the state shown in Fig. 3 (B)). When the four-way switching valve (64) switches to the state shown in FIG.
- the refrigerant circuit (60) passes the refrigerant discharged from the compressor (63) to the first adsorption heat exchanger (61). After the condensation, a first refrigeration cycle operation is performed in which the refrigerant circulates so as to evaporate in the second adsorption heat exchanger (62). Also, when the four-way switching valve (64) switches to the state shown in FIG. 3 (B), the refrigerant circuit (60) operates the compressor (63) with the refrigerant discharged by the second adsorption heat exchanger (62). ), A second refrigeration cycle operation in which the refrigerant circulates so as to evaporate in the first adsorption heat exchanger (61).
- the humidity control device (10) is configured to switch between a dehumidifying operation and a humidifying operation.
- the humidity control device (10) removes the moisture of the air flowing through the second adsorption heat exchanger (62) or the first adsorption heat exchanger (61) in which the refrigerant evaporates.
- the adsorbent is adsorbed and the refrigerant is condensed.
- the air flowing through the first adsorption heat exchanger (61) or the second adsorption heat exchanger (62) releases moisture to regenerate the adsorbent, and the air dehumidified by the adsorbent
- the refrigerant circulation of the refrigerant circuit (60) and the air circulation path are switched so as to supply the air into the room.
- the humidity control device (10) adsorbs moisture of air flowing through the first adsorption heat exchanger (61) or the second adsorption heat exchanger (62) in which the refrigerant evaporates.
- the adsorbent is adsorbed and the refrigerant is condensed.
- the air flowing through the second adsorption heat exchanger (62) or the first adsorption heat exchanger (61) releases moisture to regenerate the adsorbent and is humidified by the adsorbent.
- the circulation of the refrigerant in the refrigerant circuit (60) and the flow path of the air are switched so as to supply the air to the room.
- the humidity control apparatus (10) switches the refrigerant circulation of the refrigerant circuit (60) in any operation, and switches the first adsorption heat exchanger (61) and the second adsorption heat exchanger (62). ), The dehumidifying operation and the humidifying operation are performed continuously by alternately absorbing and desorbing water.
- the refrigerant circuit (60) includes a controller (90).
- the controller (90) is provided with a superheat control section (71) and a circulation switching section (72) as features of the present invention.
- the superheat degree control section (71) is configured as superheat degree control means for increasing the superheat degree of the suction gas refrigerant of the compressor (63) by making the opening of the expansion valve (65) smaller than the normal opening. Have been. Specifically, in the present embodiment, the opening degree of the expansion valve (65) is set so that the degree of superheat of the suction gas refrigerant is normally less than 2 ° C. Then, the superheat degree control section (71) The opening of the expansion valve (65) is controlled so that the degree of superheat is 2 ° C to 20 ° C (optimal range is 5 ° C to 10 ° C).
- the circulation switching section (72) serves as switching means for switching the circulation direction of the refrigerant after the superheat degree of the suction gas refrigerant of the compressor (63) is increased by the superheat degree control section (71) for a predetermined time. It is configured. In other words, for a while after switching the refrigerant circulation, the suction gas refrigerant of the compressor (63) is set to the normal degree of superheat (less than 2 ° C), and water is desorbed to some extent from the adsorbent in the condenser. Increases the degree of superheat and desorbs the water remaining during the predetermined time. This predetermined time is set to a time necessary for the remaining water to be desorbed. This makes it possible to effectively regenerate the adsorbent in the condenser without significantly increasing the input of the compressor (63), as compared with the case where the degree of superheat is increased throughout the entire operation.
- each of the adsorption heat exchangers (61, 62) acts on the upstream side where the refrigerant flows in when functioning as a condenser, and the air on the downstream side where the refrigerant flows out. It is configured in a parallel flow system in which is distributed.
- the refrigerant temperature goes from a high temperature region (that is, the sensible heat region S1) to a low refrigerant temperature region (the S2 (+ S3) portion). Air is flowing.
- the S1 portion represents a portion through which the high-temperature superheated gas refrigerant discharged from the compressor (63) flows
- the S2 portion represents a portion through which the refrigerant in the two-phase state flows
- the S3 portion represents a portion through which the refrigerant in the supercooled liquid state flows.
- the relative humidity of the flowing air (the surface humidity of the adsorbent significantly increases in the S1 portion, and gradually increases in the S2 (+ S3) portion.
- the temperature of the adsorbent rapidly decreases in the part S1, and hardly decreases thereafter.
- the amount of water desorbed by the flow of the high-temperature superheated gas refrigerant is greater than in the other parts. This desorbed water is reliably applied to the air with low relative humidity due to the flow of the dewatered water. The relative humidity will rise extremely.
- the counter-flow adsorption heat exchanger is configured such that air flows from the downstream side where the refrigerant flows out to the upstream side where the refrigerant flows in. That is, in the adsorption heat exchanger, air flows from the low temperature region (S2 (+ S3) portion) of the refrigerant temperature to the high temperature region (S1 portion). In this case, the relative humidity of the inflowing air gradually increases in the S2 (+ S3) portion, but decreases in the S1 portion. This is because the air humidified to some extent in S2 (+ S3) flows through the S1 part and cannot capture much moisture, and is also heated by the high-temperature superheated gas refrigerant, which lowers the relative humidity of the air. Will do.
- the adsorption heat exchange (61, 62) serving as a condenser is of a parallel flow type, and air having a low relative humidity is caused to flow through a portion (S1) through which a high-temperature superheated gas coolant flows.
- the amount of water desorbed in the adsorbent can be increased by effectively utilizing the high-temperature gas refrigerant. That is, the regeneration capacity of the adsorbent is improved.
- zeolite and silica gel are used as adsorbents, and the zeolite is supported, and the silica gel is supported and the silica gel is supported.
- zeolite is supported on the part where the refrigerant flows in when adsorption heat exchange (61, 62) functions as a condenser (S1 part in Fig. 4), and silica gel is used on the side where the refrigerant flows out. (S2 in Fig. 4). That is, the zeolite is supported on the portion of the adsorption heat exchanger (61, 62) on the air inflow side, and the silica gel is supported on the portion on the air outflow side.
- the adsorption characteristics of zeolite and silica gel will be described with reference to FIG.
- the slope of the adsorption isotherm is larger for zeolite than for silica gel.
- the slope of the adsorption isotherm is larger for silica gel than for zeolite.
- zeolite is supported on the inflow side where low relative humidity air flows, and silica gel is supported on the outflow side where high relative humidity air flows, so that zeolite or silica gel is It is possible to increase the amount of desorbed water as compared with the case in which is carried.
- a combination of zeolite and silica gel is used as the adsorbent.
- adsorbents with so-called type I (Langmuir type) adsorption characteristics such as alumina and ion-exchange resin-based materials, may be combined.
- This type I sorbent is one of six types classified by the International Union of Pure and Applied Chemistry (IUPAC).
- the amount of adsorption does not increase.
- the humidity control operation of the humidity control device (10) will be described.
- this humidity control device (10) switching between dehumidification operation and humidification operation is possible.
- the superheat degree of the intake gas refrigerant of the compressor (63) is increased by the superheat degree control unit (71). The operation when this is done will be described.
- the air supply fan (25) and the exhaust fan (26) are operated in the humidity control device (10).
- the humidity control device (10) takes in the outdoor air (OA) as the first air and supplies it to the room, while taking in the room air (RA) as the second air and discharges it to the outside.
- the first refrigeration cycle operation during the dehumidifying operation will be described with reference to FIGS. 3 and 7.
- the adsorbent is regenerated in the first adsorption heat exchange (61), and the outdoor air (OA) as the first air is dehumidified in the second adsorption heat exchanger (62). .
- the four-way switching valve (64) is switched to the state shown in Fig. 3 (A).
- the compressor (63) When the compressor (63) is operated in this state, the refrigerant circulates in the refrigerant circuit (60), the first adsorption heat exchanger (61) becomes a condenser, and the second adsorption heat exchange (62) becomes an evaporator.
- the first refrigeration cycle operation is performed.
- the refrigerant discharged from the compressor (63) radiates heat in the first adsorption heat exchanger (61) to condense, and is then sent to the expansion valve (65) to be decompressed. .
- the decompressed refrigerant absorbs heat in the second adsorption heat exchanger (62), evaporates, and is then sucked into the compressor (63) to be compressed. Then, the compressed refrigerant is discharged again from the compressor (63).
- the second air flowing from the indoor air suction port (22) flows from the second inflow path (45) to the first heat exchange chamber (41) through the fifth opening (55). Sent in. In the first heat exchange chamber (41), the second air passes through the first adsorption heat exchange (61) downward from above. In the first adsorption heat exchanger (61), the adsorbent carried on the outer surface is heated by the refrigerant, and moisture is desorbed from the adsorbent. The desorbed moisture is released to the second air passing through the first adsorption heat exchange (61). The second air to which water has been given by the first adsorption heat exchange (61) flows out of the first heat exchange chamber (41) through the third opening (53) to the first outflow path (44). Thereafter, the second air is sucked into the exhaust fan (26), and is exhausted from the exhaust air outlet (23) to the outside as exhaust air (EA).
- exhaust air exhaust air
- the first air that has flowed in from the outdoor air suction port (21) is sent from the first inflow path (43) to the second heat exchange chamber (42) through the second opening (52).
- the first air passes upward through the second adsorption heat exchanger (62).
- the second adsorption heat exchange (62) moisture in the first air is adsorbed on the adsorbent carried on the outer surface. The heat of adsorption generated at that time is absorbed by the refrigerant.
- the first air dehumidified by the second adsorption heat exchanger (62) flows out of the second heat exchange chamber (42) through the eighth opening (58) to the second outflow path (46). Thereafter, the first air is sucked into the air supply fan (25), and is supplied from the air supply outlet (24) to the room as supply air (SA).
- the second refrigeration cycle operation during the dehumidifying operation will be described with reference to FIGS. 3 and 8. I will explain it.
- the adsorbent is regenerated in the second adsorption heat exchanger (62), and the dehumidification of the outdoor air (OA), which is the first air, in the first adsorption heat exchanger (61). Done.
- the four-way switching valve (64) is switched to the state shown in FIG. 3 (B).
- the compressor (63) is operated in this state, the refrigerant circulates in the refrigerant circuit (60), the first adsorption heat exchanger (61) functions as an evaporator, and the second adsorption heat exchange (62) functions as a condenser.
- a second refrigeration cycle operation is performed.
- the refrigerant discharged from the compressor (63) dissipates heat by the second adsorption heat exchange (62) and condenses, and then is sent to the expansion valve (65) to be decompressed.
- the decompressed refrigerant absorbs heat in the first adsorption heat exchanger (61), evaporates, and is then sucked into the compressor (63) to be compressed. Then, the compressed refrigerant is discharged again from the compressor (63).
- the dampers of the respective openings (51 to 58) are switched to form the first opening (51), the fourth opening (54), and the sixth opening (56).
- the seventh opening (57) is in an open state, and the second opening (52), the third opening (53), the fifth opening (55), and the eighth opening (58) are in a closed state.
- outdoor air (OA) as first air is supplied to the first adsorption heat exchanger (61), and indoor air (OA) as second air is supplied to the second adsorption heat exchanger (62).
- RA is supplied.
- the second air flowing from the indoor air suction port (22) passes through the sixth opening (56) from the second inflow path (45) to the second heat exchange chamber (42). Sent in.
- the second air passes through the second adsorption heat exchange (62) downward from above.
- the second adsorption heat exchanger (62) the adsorbent carried on the outer surface is heated by the refrigerant, and moisture is desorbed from the adsorbent. The desorbed water is released to the second air passing through the second adsorption heat exchange (62).
- the second air to which water has been imparted by the second adsorption heat exchanger (62) flows out to the first outflow path (44) through the second heat exchange chamber (42) and the fourth opening (54). Thereafter, the second air is sucked into the exhaust fan (26), and is exhausted from the exhaust air outlet (23) to the outside as exhaust air (EA).
- the first air flowing from the outdoor air suction port (21) is sent from the first inflow path (43) to the first heat exchange chamber (41) through the first opening (51).
- the first air passes upward through the first adsorption heat exchanger (61).
- moisture in the first air is adsorbed on the adsorbent carried on the outer surface.
- the heat of adsorption generated at that time is absorbed by the refrigerant.
- the first air dehumidified by the first adsorption heat exchanger (61) flows out of the first heat exchange chamber (41) through the seventh opening (57) to the second outflow passage (46). Thereafter, the first air is sucked into the air supply fan (25), and is supplied from the air supply outlet (24) to the room as supply air (SA).
- the humidity control device (10) operates the air supply fan (25) and the exhaust fan (26).
- the humidity control device (10) takes in the room air (RA) as the first air and discharges it outside the room, while taking in the outdoor air (OA) as the second air and supplies it to the room.
- the first refrigeration cycle operation during the humidification operation will be described with reference to FIG. 3 and FIG.
- the outdoor air (OA) as the second air is humidified in the first adsorption heat exchange (61), and the indoor air as the first air in the second adsorption heat exchanger (62).
- Moisture recovery is performed from air (RA).
- the four-way switching valve (64) is switched to the state shown in FIG. 3A, and the first refrigeration cycle operation is performed.
- the dampers of the respective openings (51 to 58) are switched to form the first opening (51), the fourth opening (54), and the sixth opening (56).
- the seventh opening (57) is in an open state, and the second opening (52), the third opening (53), the fifth opening (55), and the eighth opening (58) are in a closed state.
- outdoor air (OA) as the second air is supplied to the first adsorption heat exchanger (61), and the second adsorption heat exchanger (62) is supplied as the first air.
- Indoor air (RA) is supplied.
- the first air flowing from the indoor air suction port (22) flows from the second inflow path (45) to the second heat exchange chamber (42) through the sixth opening (56). Sent in.
- the first air passes through the second adsorption heat exchange (62) downward from above.
- the second adsorption heat exchange (62) the moisture in the first air is adsorbed by the adsorbent carried on the outer surface. The heat of adsorption generated at that time is absorbed by the refrigerant.
- the dehydrated first air passes through the fourth opening (54), the first outflow passage (44), and the exhaust fan (26) in this order, and is discharged as exhaust air (EA). The air is discharged outside from the air outlet (23).
- the second air that has flowed in from the outdoor air suction port (21) is sent from the first inflow path (43) to the first heat exchange chamber (41) through the first opening (51).
- the second air passes upward through the first adsorption heat exchanger (61).
- the adsorbent carried on the outer surface is heated by the refrigerant, and moisture is desorbed from the adsorbent.
- the desorbed water is released to the second air passing through the first adsorption heat exchange (61).
- the humidified second air passes through the seventh opening (57), the second outflow channel (46), and the air supply fan (25) in this order, and is supplied from the air supply outlet (24) as supply air (SA). It is supplied to the room.
- the second refrigeration cycle operation during the humidification operation will be described with reference to FIG. 3 and FIG.
- the outdoor air (OA) as the second air is humidified in the second adsorption heat exchanger (62), and the indoor air as the first air in the first adsorption heat exchanger (61).
- Air (RA) power Moisture recovery is performed.
- the four-way switching valve (64) is switched to the state shown in FIG. 3B, and the second refrigeration cycle operation is performed.
- the dampers of the openings (51 to 58) are switched so that the second opening (52), the third opening (53), and the fifth opening (55) are switched.
- the eighth opening (58) is in an open state, and the first opening (51), the fourth opening (54), the sixth opening (56), and the seventh opening (57) are in a closed state.
- room air (RA) as first air is supplied to the first adsorption heat exchange (61), and second air as the second air is supplied to the second adsorption heat exchanger (62).
- Outdoor air (OA) is supplied.
- the first air flowing from the indoor air suction port (22) passes through the fifth opening (55) from the second inflow path (45) to the first heat exchange chamber (41). Sent in.
- the first air passes through the first adsorption heat exchanger (61) from top to bottom.
- the first adsorption heat exchange (61) moisture in the first air is adsorbed by the adsorbent carried on the outer surface. The heat of adsorption generated at that time is absorbed by the refrigerant.
- the deprived first air passes through the third opening (53), the first outflow passage (44), and the exhaust fan (26) in that order, and as exhaust air (EA), the exhaust air outlet (23). From the room.
- the second air that has flowed in from the outdoor air suction port (21) is sent from the first inflow path (43) to the second heat exchange chamber (42) through the second opening (52).
- the second air passes upward through the second adsorption heat exchanger (62).
- the adsorbent carried on the outer surface is heated by the refrigerant, and moisture is desorbed from the adsorbent.
- the desorbed water is given to the second air passing through the second adsorption heat exchange (62).
- the humidified second air passes through the eighth opening (58), the second outflow passage (46), and the air supply fan (25) in this order, and is supplied from the air supply outlet (24) as supply air (SA). It is supplied to the room.
- the superheat degree of the suction gas refrigerant of the compressor (63) is increased by the superheat degree control unit (71). Then, after operating for the predetermined time at the increased degree of superheat, the first refrigeration cycle operation and the second refrigeration cycle operation are switched by switching the refrigerant circulation by the circulation switching unit (72).
- the opening of the expansion valve (65) is set to the normal opening, and the compressor (63) is driven.
- the superheat degree of the suction gas refrigerant of the compressor (63) is the normal superheat degree (less than 2 ° C).
- the degree of opening of the expansion valve (65) is reduced by the superheat degree control section (71) to increase the degree of superheat of the suction gas refrigerant to, for example, 10 ° C.
- the refrigeration cycle operation is switched again by the circulation switching unit (72).
- the refrigeration cycle (a ⁇ b ⁇ c ⁇ d) indicated by the broken line in the figure represents the case of normal superheat (less than 2 ° C), and the refrigeration cycle (A ⁇ B ⁇ C ⁇ D) indicated by the solid line. ) Indicates the case of an increased degree of superheat (10 ° C).
- the compressor (63) compresses and discharges to the refrigerant point (eg, 65 ° C.).
- the refrigerant at the point a is radiated and condensed to the adsorbent by the adsorption heat exchange (61, 62) as a condenser, and becomes the refrigerant at the point b.
- the refrigerant at point b is decompressed by the expansion valve (65), and becomes refrigerant at point c (for example, 0 ° C.).
- the refrigerant at the point c absorbs the heat of adsorption of the adsorbent in the adsorption heat exchange (61, 62) serving as an evaporator and evaporates to become the refrigerant at the point d (below 2 ° C). And is again sucked into the compressor (63) and compressed.
- the compressor (63) compresses and discharges the refrigerant to point A (eg, 100 ° C.).
- the refrigerant at the point A is radiated and condensed to the adsorbent by adsorption heat exchange (61, 62) serving as a condenser, and becomes the refrigerant at the point B.
- the refrigerant at point B is decompressed by the expansion valve (65), and becomes refrigerant at point C (for example, 0 ° C).
- the refrigerant at point C absorbs the heat of adsorption of the adsorbent in the adsorption heat exchange (61, 62), which becomes an evaporator, and evaporates, and becomes refrigerant at point D (for example, 10 ° C). It is sucked into (63) and compressed.
- the adsorption heat exchange (61, 62) is made to be a parallel flow type when functioning as a condenser, the high temperature of the superheated gas refrigerant (S1 part) is used for water desorption in the adsorbent. It can be used effectively. Thereby, the amount of desorbed water can be increased.
- the portion (S1 portion) where the superheated gas refrigerant flows which is the sensible heat region, carries zeolite, and the other portion (S2 (+ S3) portion) Since silica gel is supported on the substrate, the amount of desorbed water can be effectively obtained in each part of those characteristic forces.
- the discharge from the compressor (63) is performed.
- the amount of sensible heat can be increased by raising the temperature of Heat exchange ⁇ (61,62) adsorbent can be heated more.
- the amount of desorbed water in the adsorbent can be increased.
- the amount of water adsorbed by the adsorbent of the adsorption heat exchange (61, 62) switched from the condenser to the evaporator increases.
- the humidifying ability and the dehumidifying ability can be improved.
- the degree of opening of the expansion valve (65) is reduced, so that the degree of superheat can be easily and reliably increased.
- a circulation switching unit (72) for switching the circulation direction of the refrigerant after increasing the superheat degree of the suction gas refrigerant of the compressor (63) by the superheat degree control unit (71) for a predetermined time is provided.
- the water can be desorbed from the adsorbent to some extent during the normal superheat, and the remaining water can be desorbed at the elevated superheat. This makes it possible to effectively regenerate the adsorbent in the condenser without increasing the input of the compressor (63) so much as compared with a case where the degree of superheat is increased throughout the entire operation.
- the adsorption heat exchangers (61, 62) function as condensers, the refrigerant flow and the air flow are made to flow in parallel. Low-flow air. As a result, it is possible to surely give the air more water desorbed than the other parts by the high-temperature gas refrigerant. Therefore, compared with the case of the counter-flow type, the high-temperature superheated gas refrigerant can be effectively used, and the amount of desorbed water can be increased.
- each adsorption heat exchange (61, 62)
- zeolite as an adsorbent is carried on the air inlet side (the side where low humidity air flows when functioning as a condenser), and the air Since silica gel as an adsorbent is supported on the outflow side (the side on which air with a high relative humidity flows), zeolite or silica gel is supported over the entire body.
- the desorption amount can be earned effectively.
- the humidity control apparatus (10) of the second embodiment is a modification of the configuration of the superheat control section (71) of the controller (90) in the first embodiment. That is, in the present embodiment, the superheat degree control unit (71) is configured to increase the amount of air blown by the first adsorption heat exchanger (61) or the second adsorption heat exchanger (62) serving as an evaporator. did. [0095] Specifically, in the case of the dehumidification operation, the superheat degree control section (71) performs the operation during each refrigeration cycle operation.
- the present invention is useful as a humidity control device provided with a heat exchanger having an adsorbent supported on the surface.
Abstract
Description
Claims
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JP2004131662A JP3807409B2 (ja) | 2004-04-27 | 2004-04-27 | 調湿装置 |
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CN111278532A (zh) * | 2017-10-24 | 2020-06-12 | 都灵理工学院 | 基于低温热量从空气中生产水的方法以及用于该方法的机器和系统 |
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JP3891207B2 (ja) * | 2005-06-17 | 2007-03-14 | ダイキン工業株式会社 | 調湿装置 |
JP5109593B2 (ja) * | 2007-10-31 | 2012-12-26 | ダイキン工業株式会社 | 調湿装置 |
JP5396799B2 (ja) * | 2008-09-30 | 2014-01-22 | ダイキン工業株式会社 | 調湿システム |
JP5332466B2 (ja) * | 2008-09-30 | 2013-11-06 | ダイキン工業株式会社 | 調湿システム |
JP5332465B2 (ja) * | 2008-09-30 | 2013-11-06 | ダイキン工業株式会社 | 調湿システム |
JP5003697B2 (ja) * | 2009-02-09 | 2012-08-15 | 三菱電機株式会社 | 加湿装置、加湿装置の制御方法、及び加湿装置を有する空気調和機 |
JP5799670B2 (ja) * | 2011-08-26 | 2015-10-28 | ダイキン工業株式会社 | 調湿装置 |
CN108472578B (zh) * | 2015-12-28 | 2020-12-08 | 三菱电机株式会社 | 除湿装置 |
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JPH09310886A (ja) * | 1996-05-23 | 1997-12-02 | Matsushita Electric Ind Co Ltd | 吸着材の脱着装置および吸脱着装置 |
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JP2004012127A (ja) * | 2003-10-02 | 2004-01-15 | Mitsubishi Electric Corp | 可燃性冷媒を用いた冷蔵庫 |
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JPH09310886A (ja) * | 1996-05-23 | 1997-12-02 | Matsushita Electric Ind Co Ltd | 吸着材の脱着装置および吸脱着装置 |
JPH11344239A (ja) * | 1998-06-01 | 1999-12-14 | Denso Corp | 除湿装置および車両用空調装置 |
JP2003161465A (ja) * | 2001-11-26 | 2003-06-06 | Daikin Ind Ltd | 調湿装置 |
JP2002213797A (ja) * | 2001-12-10 | 2002-07-31 | Sharp Corp | 空気調和機 |
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CN111278532A (zh) * | 2017-10-24 | 2020-06-12 | 都灵理工学院 | 基于低温热量从空气中生产水的方法以及用于该方法的机器和系统 |
US11674699B2 (en) | 2017-10-24 | 2023-06-13 | Politecnico Di Torino | Method for production of water from air based on low-temperature heat, and machine and system thereof |
CN111278532B (zh) * | 2017-10-24 | 2023-10-20 | 都灵理工学院 | 基于低温热量从空气中生产水的方法以及用于该方法的机器和系统 |
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