JP2005283041A - Humidity controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To avoid a problem of noise occurring when changing a circulating direction of refrigerant. <P>SOLUTION: In a refrigerant circuit 60, a compressor 63, a four way selector valve 64, a first adsorption heat exchanger 61, an expansion valve 65, and a second adsorption heat exchanger 62 are connected, it is composed such that refrigerant circulation can be reversed, and it carries out a vapor compression type refrigerating cycle. An adsorbent carrying out adsorption and desorption of moisture is carried on surfaces of the first adsorption heat exchanger 61 and the second adsorption heat exchanger 62. To alternately carry out adsorption and desorption of moisture in the first adsorption heat exchanger 61 and the second adsorption heat exchanger 62, a selector mechanism 64 is changed to change a circulating direction of the refrigerant of the refrigerant circuit 60. Moreover, before changing the refrigerant circulation, the compressor 63 is stopped for reducing a differential pressure between a high pressure side and a low pressure side of the refrigerant circuit 60. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

    The present invention relates to a humidity control apparatus that adjusts humidity using an adsorbent, and particularly relates to a humidity control apparatus including a refrigerant circuit of a vapor compression refrigeration cycle.

    Conventionally, a humidity control apparatus using an adsorbent is configured to perform dehumidification or humidification of air using an adsorption action and a desorption action of moisture by the adsorbent. When the moisture adsorption amount of the adsorbent reaches the saturation region, the humidity control apparatus needs to desorb moisture and regenerate it. However, if adsorption and regeneration are simply performed alternately at that time, dehumidification and regeneration can be performed only intermittently.

    Therefore, in this type of humidity control apparatus, two adsorbing members containing an adsorbent are used, and the one used on the adsorption side and the one used on the regeneration side are switched alternately, so that only the air on the adsorption side or the regeneration side is always used. A method of supplying only air into the room is known (see, for example, Patent Document 1). In this method, the dehumidifying operation or the humidifying operation is continued by switching between the adsorption side and the regeneration side every time a predetermined time elapses while performing the regeneration operation on the other side while performing the adsorption operation on one of the adsorption members. (For example, refer to Patent Document 1).

The regeneration operation is performed between the adsorption operation and the next adsorption operation. Therefore, in order to perform the adsorption operation in a short time, it is necessary to heat the adsorption member. For this reason, in the said humidity control apparatus, the adsorption member is heated with the heat of a refrigerant | coolant using the refrigerant circuit of a vapor compression refrigeration cycle.
JP 2003-028458 A

    In the humidity control apparatus, in order to efficiently heat the adsorbent during regeneration, it is conceivable to integrate the condenser of the refrigerant circuit and the adsorbing member. Specifically, the adsorbent is supported on the fins of the condenser. In this case, in order to perform the same operation as alternately switching between the adsorption side and the regeneration side using two adsorption members, both of the two heat exchangers of the refrigerant circuit use those carrying an adsorbent. Good. In this way, while switching the refrigerant circulation direction in the refrigerant circuit, an efficient operation is possible by using the heat exchanger as an evaporator on the adsorption side and the heat exchanger as a condenser on the regeneration side.

    Incidentally, a four-way switching valve is generally used to switch the refrigerant circulation direction in the refrigerant circuit. However, when operating the humidity control device, the switching frequency of the four-way switching valve is much higher than when switching between cooling and heating with an air conditioning device or performing reverse cycle defrost operation with a refrigeration device (for example, It may be necessary to switch every few minutes). At the time of switching the four-way switching valve, a relatively loud sound is generated in the four-way switching valve or pipe as the refrigerant flows from the high pressure side to the low pressure side. In particular, when the frequency of switching increases, the frequency of sound generation increases, and driving noise becomes a major problem.

    The present invention has been made in view of such a point, and an object thereof is to avoid the problem of noise when the refrigerant circulation direction is switched.

    Specifically, as shown in FIG. 1, the first invention provides a compressor (63), a switching mechanism (64), a first heat exchanger (61), an expansion mechanism (65), and a second heat exchanger ( 62) and a refrigerant circuit (60) configured to perform reversible refrigerant circulation and performing a vapor compression refrigeration cycle, the surfaces of the first heat exchanger (61) and the second heat exchanger (62) In addition, the present invention is intended for a humidity control apparatus in which an adsorbent that adsorbs and desorbs moisture is supported. In order to alternately perform the adsorption and desorption of moisture in the first heat exchanger (61) and the second heat exchanger (62), the switching mechanism (64) is switched to change the refrigerant circuit (60). Circulation switching means (71) for switching the refrigerant circulation direction is provided. In addition, differential pressure reducing means (80) for reducing the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is provided before the circulation switching of the circulation switching means (71).

    The second invention is configured such that, in the first invention, the differential pressure reducing means (80) stops the compressor (63).

    Further, in a third aspect of the present invention based on the first aspect, the compressor (63) is configured to have a variable capacity, and the differential pressure reducing means (80) reduces the operating capacity of the compressor (63). It is configured.

    According to a fourth aspect of the present invention, in the first aspect, the expansion mechanism (65) is configured by an expansion valve having a variable opening, and the differential pressure reducing means (80) opens the opening of the expansion valve. It is configured.

    According to a fifth invention, in the first invention, the differential pressure reducing means (80) is provided in the bypass passage (81) bypassing the expansion mechanism (65) and the bypass passage (81). A normally closed bypass valve (82), and is configured to open the bypass valve (82) before the circulation switching of the circulation switching means (71).

    According to a sixth invention, in the first invention, the differential pressure reducing means (80) includes a bypass passage (81) connecting the discharge side and the suction side of the compressor (63), and the bypass passage ( 81) and a normally closed bypass valve (82), and is configured to open the bypass valve (82) before the circulation switching means (71) switches the circulation.

    According to a seventh aspect, in the fifth or sixth aspect, the differential pressure reducing means (80) includes a flow rate adjusting mechanism (83) provided in the bypass passage (81).

    In an eighth aspect based on the first aspect, the differential pressure reducing means (80) is provided in the gas pipe (6b, 6c) connected to the compressor (63) and through which the gas refrigerant always flows. The normally open on-off valve (85) is provided so that the on-off valve (85) is closed before the circulation switching of the circulation switching means (71).

<Action>
That is, in the first aspect of the invention, moisture is adsorbed by the adsorbent of the heat exchanger serving as an evaporator, out of the first heat exchanger (61) and the second heat exchanger (62) of the refrigerant circuit (60). In the heat exchanger as a condenser, moisture is desorbed and the adsorbent is regenerated. For this reason, for example, the dehumidifying operation is performed when the adsorption-side air is supplied into the room, and the humidifying operation is performed when the regeneration-side air is supplied into the room. In both cases of the dehumidifying operation and the humidifying operation, the refrigerant circulation direction is switched by the switching mechanism (64), and the dehumidifying and humidifying continuous operation is performed.

    In this switching, the differential pressure reducing means (80) reduces the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) before the switching mechanism (64) of the circulation switching means (71) is switched. Is suppressed from instantaneously flowing from the high pressure side to the low pressure side.

    Specifically, in the second invention, before the differential pressure reducing means (80) switches the switching mechanism (64) of the circulation switching means (71), the compressor (63) is stopped for a predetermined time, and the switching mechanism ( 64) Restart the compressor (63) after switching. By stopping the compressor (63) by the differential pressure reducing means (80), the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is reduced.

    Further, in the third invention, before the differential pressure reducing means (80) switches the switching mechanism (64) of the circulation switching means (71), the capacity of the compressor (63) is reduced, and the switching mechanism (64) Return the capacity of the compressor (63) after switching. The differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is reduced by the capacity reduction of the compressor (63) by the differential pressure reducing means (80).

    Further, in the fourth invention, before the differential pressure reducing means (80) switches the switching mechanism (64) of the circulation switching means (71), the opening degree of the expansion valve (65) is increased so that the switching mechanism (64) Return the opening of the expansion valve (65) after switching. By increasing the opening of the expansion valve (65) by the differential pressure reducing means (80), the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is reduced.

    In the fifth and sixth inventions, before the differential pressure reducing means (80) switches the switching mechanism (64) of the circulation switching means (71), the bypass valve (82) is opened, and the switching mechanism (64 ) Close the bypass valve (82) after switching. By opening the bypass valve (82) by the differential pressure reducing means (80), the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is reduced.

    In the seventh invention, the amount of refrigerant flowing through the bypass passage (81) is adjusted by the flow rate adjusting mechanism (83), and the refrigerant generation sound at the time of switching of the bypass valve (82) is suppressed.

    In the eighth aspect of the invention, the differential pressure reducing means (80) closes the on-off valve (85) before switching of the switching mechanism (64) of the circulation switching means (71), and opens and closes after switching of the switching mechanism (64). Open valve (85). By closing the on-off valve (85) by the differential pressure reducing means (80), the refrigerant circulation amount is reduced, and the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is reduced.

    Therefore, according to the present invention, since the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is reduced before switching the refrigerant circulation, the refrigerant instantaneously flows from the high pressure side to the low pressure side. The operation does not occur, and it is possible to prevent the generated sound of the refrigerant. In particular, even when the switching frequency is high, the sound of the refrigerant does not become a problem.

    According to the second aspect of the invention, since the compressor (63) is stopped before the switching mechanism (64) is switched, the pressure difference between the high pressure side and the low pressure side of the refrigerant circuit (60) is reliably ensured. Since it can be reduced, it is possible to reliably prevent refrigerant generation noise at the time of switching.

    Moreover, according to the 3rd-6th and 8th invention, since the driving | operation of a compressor (63) is continued, the fall of humidity control ability can be suppressed.

    Further, according to the seventh aspect, since the flow rate adjusting mechanism (83) is provided in the bypass passage (81), the refrigerant flows from the high pressure side through the bypass valve (82) when the bypass valve (82) is opened. The operation that instantaneously flows to the side can be suppressed. Refrigerant generation noise due to the opening of the bypass valve (82) is suppressed.

    Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

<Embodiment 1>
As shown in FIGS. 1-3, the humidity control apparatus (10) of this embodiment performs dehumidification and humidification of indoor air, and is provided with the flat hollow rectangular parallelepiped casing (11). The casing (11) contains a refrigerant circuit (60) and the like. The refrigerant circuit (60) includes the first adsorption heat exchanger (61) and the second adsorption heat exchanger (62), It has a compressor (63).

    As shown in FIG. 3, the first adsorption heat exchanger (61) and the second adsorption heat exchanger (62) are each a first heat exchanger and a cross fin type fin-and-tube heat exchanger. The 2nd heat exchanger is comprised. The first adsorptive heat exchanger (61) and the second adsorptive heat exchanger (62) are made of a large number of aluminum fins (6a) formed in a rectangular plate shape and made of copper penetrating the fins (6a). And a heat transfer tube (6b). For example, an adsorbent such as zeolite is supported on the outer surface of the fin (6a). The first adsorption heat exchanger (61) constitutes a first adsorption member, and the second adsorption heat exchanger (62) constitutes a second adsorption member.

    Next, the internal structure of the casing (11) will be described with reference to FIG. In FIG. 2B, the lower side is the front side of the casing (11) and the upper side is the back side of the casing (11). In the following description, “right”, “left”, “upper”, and “lower” all refer to those in the referenced drawings.

    The casing (11) is formed in a flat box shape with a substantially square shape in plan view. In this casing (11), the left side plate (12) and the right side plate (13), and the front plate (14) and the back plate (15) are positioned in the thickness direction of the casing (11) and are mutually connected. Two opposing end faces are formed. The left side plate (12) has an outdoor air inlet (21) near the back plate (15), and an indoor air inlet (22) near the front plate (14). On the other hand, the right side plate (13) of the casing (11) is formed with an exhaust outlet (23) closer to the rear plate (15) and an air supply outlet (24) closer to the front plate (14). ing. The outdoor air inlet (21) and the indoor air inlet (22) constitute an air inlet, and the exhaust outlet (23) and the air supply outlet (24) constitute an air outlet. Yes.

    A first partition plate (31) is erected in the casing (11) closer to the right side plate (13) than the central portion in the left-right direction. The internal space (16) of the casing (11) is partitioned left and right by the first partition plate (31). The right side of the first partition (31) is the first space (17), and the left side of the first partition (31) is the second space (18).

    The first space (17) of the casing (11) is partitioned into a front-side space and a back-side space by a seventh partition plate (37). A compressor (63) and an exhaust fan (26) of the refrigerant circuit (60) are disposed in the space on the back side in the first space (17). Although not shown, an expansion valve (65) and a four-way switching valve (64) of the refrigerant circuit (60) are also arranged in the space on the back side. On the other hand, an air supply fan (25) is arranged in the space on the front side in the first space (17). The exhaust fan (26) is connected to the exhaust outlet (23), and the air supply fan (25) is connected to the air supply outlet (24).

    A second partition plate (32), a third partition plate (33), and a sixth partition plate (36) are provided in the second space (18) of the casing (11). The second partition plate (32) is erected closer to the front plate (14), and the third partition plate (33) is erected closer to the rear plate (15). The second space (18) is partitioned into three spaces from the front side to the back side by the second partition plate (32) and the third partition plate (33). 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 plate (36) is erected at the center in the left-right direction of the second space (18).

    The space sandwiched between the second partition plate (32) and the third partition plate (33) is partitioned left and right by the sixth partition plate (36). Among these, the space on the right side constitutes the first heat exchange chamber (41), and the first adsorption heat exchanger (61) is disposed therein. On the other hand, the left space constitutes the second heat exchange chamber (42), and the second adsorption heat exchanger (62) is disposed therein. That is, the first heat exchange chamber (41) and the second heat exchange chamber (42) are disposed adjacent to each other. The first heat exchange chamber (41) constitutes a first processing space, and the second heat exchange chamber (42) constitutes a second processing space.

    A fifth partition plate (35) is provided in a space between the third partition plate (33) and the back plate (15) of the casing (11) in the second space (18). The fifth partition plate (35) is provided so as to cross the central portion in the height direction of the space, and partitions the space up and down (see FIG. 2A). The upper space of the fifth partition plate (35) constitutes the first inflow passage (43), and the lower space constitutes the first outflow passage (44). The first inflow passage (43) communicates with the outdoor air inlet (21), and the first outflow passage (44) communicates with the exhaust outlet (23) via the exhaust fan (26).

    On the other hand, a fourth partition plate (34) is provided in a space between the second partition plate (32) and the front plate (14) of the casing (11) in the second space (18). This 4th partition plate (34) is provided so that the center part of the height direction of a space may be crossed, and the space is partitioned up and down (refer FIG.2 (C)). The upper space of the fourth partition plate (34) constitutes the second inflow passage (45), and the lower space constitutes the second outflow passage (46). The second inflow passage (45) communicates with the indoor air inlet (22), and the second outflow passage (46) communicates with the air supply outlet (24) via the air supply fan (25). Yes.

    Thus, the first inflow passage (43) and the first outflow passage (44) serve as a first side surface in which the first heat exchange chamber (41) and the second heat exchange chamber (42) are continuous. It arrange | positions so that it may overlap along a 3rd partition plate (33). On the other hand, the second inflow passage (45) and the second outflow passage (46) face the third partition plate (33) of the first heat exchange chamber (41) and the second heat exchange chamber (42). It arrange | positions so that it may overlap along the 2nd partition plate (32) as a 2nd side surface. The first inflow passage (43) and the second inflow passage (45) constitute an inflow passage, and the first outflow passage (44) and the second outflow passage (46) constitute an outflow passage.

    Four openings (51 to 54) are formed in the third partition plate (33) (see FIG. 2A). The four openings (51 to 54) are located close to each other in the matrix direction, that is, two openings are arranged in a grid pattern on the top, bottom, left, and right. The first opening (51) communicates the first inflow passage (43) and the first heat exchange chamber (41), and the second opening (52) communicates with the first inflow passage (43) and the first heat exchange chamber (41). 2 The heat exchange chamber (42) is in communication. The third opening (53) communicates the first outflow passage (44) and the first heat exchange chamber (41), and the fourth opening (54) communicates with the first outflow passage (44) and the first heat exchange chamber (41). 2 The heat exchange chamber (42) is in communication.

    Four openings (55 to 58) are formed in the second partition plate (32) (see FIG. 2C). These four openings (55 to 58) are located close to each other in the matrix direction, that is, two openings are arranged in a grid pattern on the top, bottom, left, and right. The fifth opening (55) communicates the second inflow channel (45) and the first heat exchange chamber (41), and the sixth opening (56) communicates with the second inflow channel (45) and the first heat exchange chamber (41). 2 The heat exchange chamber (42) is in communication. The seventh opening (57) communicates the second outflow passage (46) with the first heat exchange chamber (41), and the eighth opening (58) communicates with the second outflow passage (46). 2 The heat exchange chamber (42) is in communication.

    As shown in FIGS. 4 to 7, the eight openings (51 to 58) are provided with dampers (71 to 78) each configured as an opening / closing means that opens and closes and switches between air flow and blockage. Yes. That is, these dampers (71 to 78) are provided with a second partition plate (partition between the inflow passages (43, 45) and the outflow passages (44, 46) and the heat exchange chambers (41, 42)). 32) and the third partition plate (33).

    Specifically, the first opening (51) and the second opening (52) are provided with a first damper (71) and a second damper (72), and the first damper (71) and the second damper (72). Are arranged next to each other. The third opening (53) and the fourth opening (54) are provided with a third damper (73) and a fourth damper (74), and the third damper (73) and the fourth damper (74) are mutually connected. They are placed next to each other. The fifth opening (55) and the sixth opening (56) are provided with a fifth damper (75) and a sixth damper (76), and the fifth damper (75) and the sixth damper (76) are mutually connected. They are placed next to each other. A seventh damper (77) and an eighth damper (78) are provided in the seventh opening (57) and the eighth opening (58), and the seventh damper (77) and the eighth damper (78) are mutually connected. They are placed next to each other.

    Next, the refrigerant circuit (60) will be described with reference to FIG.

    The refrigerant circuit (60) includes a compressor (63), a four-way switching valve (64), a first adsorption heat exchanger (61), an expansion valve (65), and a second adsorption heat exchanger (62) in this order. It is connected to the refrigerant pipe (6c) to form a closed circuit. The refrigerant circuit (60) is configured to perform a vapor compression refrigeration cycle by circulating the filled refrigerant.

    The four-way selector valve (64) constitutes a switching mechanism for switching the refrigerant circulation direction in the refrigerant circuit (60). Specifically, the discharge port (6d) of the compressor (63) is connected to the first port of the four-way selector valve (64), and the suction pipe of the compressor (63) is connected to the second port. (6e) is connected. One end of the first adsorption heat exchanger (61) is connected to the third port of the four-way switching valve (64), and the fourth port of the second adsorption heat exchanger (62). One end is connected. The refrigerant circuit (60) is configured such that the refrigerant circulation is reversible by the four-way switching valve (64).

    The expansion valve (65) constitutes an expansion mechanism for expanding the refrigerant.

    In the second adsorption heat exchanger (62) or the first adsorption heat exchanger (61) serving as an evaporator, the refrigerant circuit (60) generates adsorption heat generated when moisture in the air is adsorbed by the adsorbent. The refrigerant absorbs heat. In the first adsorption heat exchanger (61) or the second adsorption heat exchanger (62) serving as a condenser, the refrigerant circuit (60) heats the adsorbent and removes moisture from the adsorbent. Let go.

    The refrigerant circuit (60) performs the adsorption and desorption of moisture in the first adsorption heat exchanger (61) or the second adsorption heat exchanger (62) with the first adsorption heat exchanger (61) and the second adsorption heat. It is configured to alternately perform dehumidification or humidification of air by alternately performing with the exchanger (62).

    Furthermore, the refrigerant circuit (60) is controlled by a controller (70). The controller (70) is provided with a circulation switching means (71) and a differential pressure reducing means (80).

    The circulation switching means (71) includes the four-way switching valve (64) in order to alternately adsorb and desorb moisture in the first adsorption heat exchanger (61) and the second adsorption heat exchanger (62). ) To switch the circulation direction of the refrigerant in the refrigerant circuit (60). The circulation switching means (71) is configured to switch the four-way switching valve (64) every 3 minutes, for example.

    The differential pressure reducing means (80) is connected between the high pressure side and the low pressure side of the refrigerant circuit (60) before switching the circulation of the circulation switching means (71), that is, before switching the four-way switching valve (64). It is configured to reduce the differential pressure. Specifically, the differential pressure reducing means (80) is configured to stop the compressor (63), and before the switching of the four-way switching valve (64) of the circulation switching means (71), the compressor (63) Is stopped for a predetermined time, and after the four-way switching valve (64) is switched, the operation of the compressor (63) is resumed.

    The differential pressure reducing means (80) reduces the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) by stopping the compressor (63), and suppresses refrigerant generation noise during switching. ing.

-Driving action-
Next, the humidity control operation of the humidity control apparatus (10) will be described. In the humidity control apparatus (10), the dehumidifying operation and the humidifying operation can be switched.

《Dehumidification operation》
During the dehumidifying operation, the air supply fan (25) and the exhaust fan (26) are operated in the humidity control apparatus (10). The humidity control apparatus (10) takes outdoor air (OA) as the first air and supplies it to the room, while taking in the indoor air (RA) as the second air and discharges it to the outside.

    First, the first operation during the dehumidifying operation will be described with reference to FIGS. 1 and 4. In this first operation, the adsorbent is regenerated in the first adsorption heat exchanger (61), and the outdoor air (OA), which is the first air, is dehumidified in the second adsorption heat exchanger (62).

    During the first operation, in the refrigerant circuit (60), the four-way selector valve (64) is switched to the state shown by the solid line in FIG. 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 exchanger (62) becomes an evaporator. The first refrigeration cycle operation is performed.

    Specifically, the refrigerant discharged from the compressor (63) dissipates heat in the first adsorption heat exchanger (61) and condenses, and then is sent to the expansion valve (65) to be depressurized. The decompressed refrigerant absorbs heat and evaporates in the second adsorption heat exchanger (62), and is then sucked into the compressor (63) and compressed. Then, the compressed refrigerant is discharged again from the compressor (63).

    In the first operation, the second opening (52), the third opening (53), the fifth opening (55), and the second opening (51) are switched by switching the dampers (71 to 78) of the openings (51 to 58). The eight openings (58) are in the open state, and the first opening (51), the fourth opening (54), the sixth opening (56), and the seventh opening (57) are in the closed state. Then, as shown in FIG. 4, indoor air (RA) as second air is supplied to the first adsorption heat exchanger (61), and outdoor air as the first air is supplied to the second adsorption heat exchanger (62). (OA) is supplied.

    Specifically, the 2nd air which flowed in from the said indoor air suction inlet (22) is sent into a 1st heat exchange chamber (41) through a 5th opening (55) from a 2nd inflow path (45). In the first heat exchange chamber (41), the second air passes through the first adsorption heat exchanger (61) from top to bottom. In the first adsorption heat exchanger (61), the adsorbent supported on the outer surface is heated by the refrigerant, and moisture is desorbed from the adsorbent. The moisture desorbed from the adsorbent is released to the second air passing through the first adsorption heat exchanger (61). The second air given moisture in the first adsorption heat exchanger (61) flows out from the first heat exchange chamber (41) through the third opening (53) to the first outflow passage (44). Thereafter, the second air is sucked into the exhaust fan (26), and discharged from the exhaust outlet (23) to the outside as exhaust air (EA).

    On the other hand, the 1st air which flowed in from the said outdoor air suction inlet (21) is sent into a 2nd heat exchange chamber (42) through a 2nd opening (52) from a 1st inflow path (43). In the second heat exchange chamber (42), the first air passes from the top to the bottom through the second adsorption heat exchanger (62). In the second adsorption heat exchanger (62), 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 first air dehumidified in the second adsorption heat exchanger (62) flows out from the second heat exchange chamber (42) through the eighth opening (58) to the second outflow passage (46). Thereafter, the first air is sucked into the air supply fan (25) and is supplied into the room as supply air (SA) from the air supply outlet (24).

    Next, the second operation during the dehumidifying operation will be described with reference to FIGS. In the second operation, the adsorbent is regenerated in the second adsorption heat exchanger (62), and the outdoor air (OA) that is the first air is dehumidified in the first adsorption heat exchanger (61).

    During this second operation, in the refrigerant circuit (60), the four-way selector valve (64) is switched to the state shown by the broken line in FIG. When the compressor (63) is operated in this state, the refrigerant circulates in the refrigerant circuit (60), the first adsorption heat exchanger (61) becomes an evaporator, and the second adsorption heat exchanger (62) becomes a condenser. The second refrigeration cycle operation is performed.

    Specifically, the refrigerant discharged from the compressor (63) dissipates heat and condenses in the second adsorption heat exchanger (62), and then is sent to the expansion valve (65) to be depressurized. The decompressed refrigerant absorbs heat and evaporates in the first adsorption heat exchanger (61), and is then sucked into the compressor (63) and compressed. Then, the compressed refrigerant is discharged again from the compressor (63).

    In the second operation, the first opening (51), the fourth opening (54), the sixth opening (56), and the first opening (51) are switched by switching the dampers (71 to 78) of the openings (51 to 58). 7 opening (57) is made into an open state, and 2nd opening (52), 3rd opening (53), 5th opening (55), and 8th opening (58) are made into a closed state. Then, as shown in FIG. 5, outdoor air (OA) as first air is supplied to the first adsorption heat exchanger (61), and indoor air as second air is supplied to the second adsorption heat exchanger (62). (RA) is supplied.

    Specifically, the 2nd air which flowed in from the above-mentioned indoor air suction opening (22) is sent into the 2nd heat exchange room (42) through the 6th opening (56) from the 2nd inflow passage (45). In the second heat exchange chamber (42), the second air passes through the second adsorption heat exchanger (62) from top to bottom. In the second adsorption heat exchanger (62), the adsorbent supported on the outer surface is heated by the refrigerant, and moisture is desorbed from the adsorbent. The moisture desorbed from the adsorbent is released to the second air passing through the second adsorption heat exchanger (62). The second air given moisture in the second adsorption heat exchanger (62) flows out from the second heat exchange chamber (42) through the fourth opening (54) to the first outflow passage (44). Thereafter, the second air is sucked into the exhaust fan (26), and discharged from the exhaust outlet (23) to the outside as exhaust air (EA).

    On the other hand, the 1st air which flowed in from the said outdoor air inlet (21) is sent into a 1st heat exchange chamber (41) through a 1st inlet (51) through a 1st opening (51). In the first heat exchange chamber (41), the first air passes through the first adsorption heat exchanger (61) from top to bottom. In the first adsorption heat exchanger (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 first air dehumidified by the first adsorption heat exchanger (61) flows out from 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 into the room as supply air (SA) from the air supply outlet (24).

《Humidification operation》
During the humidification operation, the air supply fan (25) and the exhaust fan (26) are operated in the humidity control apparatus (10). And this humidity control apparatus (10) takes in indoor air (RA) as 1st air, and discharges it outside, while taking in outdoor air (OA) as 2nd air and supplies it indoors.

    First, the first operation during the humidifying operation will be described with reference to FIGS. 1 and 6. In this first operation, the outdoor air (OA) that is the second air is humidified in the first adsorption heat exchanger (61), and the indoor air that is the first air in the second adsorption heat exchanger (62) ( The water is recovered from (RA). During the first operation, the four-way switching valve (64) of the refrigerant circuit (60) is switched to the state shown by the solid line in FIG. 1, and the first refrigeration cycle operation is performed.

    In the first operation, the first opening (51), the fourth opening (54), the sixth opening (56), and the first opening are switched by switching the dampers (71 to 78) of the openings (51 to 58). 7 opening (57) is made into an open state, and 2nd opening (52), 3rd opening (53), 5th opening (55), and 8th opening (58) are made into a closed state. Then, as shown in FIG. 6, outdoor air (OA) as second air is supplied to the first adsorption heat exchanger (61), and first air is supplied to the second adsorption heat exchanger (62). Room air (RA) is supplied.

    Specifically, the 1st air which flowed in from the said indoor air suction inlet (22) is sent into a 2nd heat exchange chamber (42) through a 6th opening (56) from a 2nd inflow path (45). In the second heat exchange chamber (42), the first air passes from the top to the bottom through the second adsorption heat exchanger (62). In the second adsorption heat exchanger (62), 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. Thereafter, the first air deprived of moisture passes through the fourth opening (54), the first outflow passage (44), and the exhaust fan (26) in this order, and from the exhaust outlet (23) as exhaust air (EA). It is discharged outside the room.

    On the other hand, the 2nd air which flowed in from the said outdoor air suction inlet (21) is sent into a 1st heat exchange chamber (41) through a 1st inflow path (43) through a 1st opening (51). In the first heat exchange chamber (41), the second air passes through the first adsorption heat exchanger (61) from top to bottom. In the first adsorption heat exchanger (61), the adsorbent supported on the outer surface is heated by the refrigerant, and moisture is desorbed from the adsorbent. The moisture desorbed from the adsorbent is released to the second air passing through the first adsorption heat exchanger (61). Thereafter, the humidified second air sequentially passes through the seventh opening (57), the second outflow passage (46), and the air supply fan (25), and is supplied as supply air (SA) from the air supply outlet (24). Supplied indoors.

    Next, the second operation during the humidification operation will be described with reference to FIGS. In the second operation, the outdoor air (OA), which is the second air, is humidified in the second adsorption heat exchanger (62), and the indoor air (the first air, in the first adsorption heat exchanger (61)). The water is recovered from (RA). During the second operation, the four-way selector valve (64) of the refrigerant circuit (60) is switched to the state shown by the broken line in FIG. 1, and the second refrigeration cycle operation is performed.

    In the second operation, the second opening (52), the third opening (53), the fifth opening (55), and the second opening (51) are switched by switching the dampers (71 to 78) of the openings (51 to 58). The eight openings (58) are in the open state, and the first opening (51), the fourth opening (54), the sixth opening (56), and the seventh opening (57) are in the closed state. Then, as shown in FIG. 7, the first adsorption heat exchanger (61) is supplied with indoor air (RA) as the first air, and the second adsorption heat exchanger (62) as the second air. Outdoor air (OA) is supplied.

    Specifically, the 1st air which flowed in from the said indoor air suction inlet (22) is sent into a 1st heat exchange chamber (41) through a 5th opening (55) from a 2nd inflow path (45). In the first heat exchange chamber (41), the first air passes from the top to the bottom through the first adsorption heat exchanger (61). In the first adsorption heat exchanger (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. Thereafter, the first air deprived of moisture passes through the third opening (53), the first outflow passage (44), and the exhaust fan (26) in this order, and is discharged from the exhaust outlet (23) as exhaust air (EA). It is discharged outside the room.

    On the other hand, the 2nd air which flowed in from the said outdoor air suction inlet (21) is sent into a 2nd heat exchange chamber (42) through a 2nd opening (52) from a 1st inflow path (43). In the second heat exchange chamber (42), the second air passes through the second adsorption heat exchanger (62) from top to bottom. In the second adsorption heat exchanger (62), the adsorbent supported on the outer surface is heated by the refrigerant, and moisture is desorbed from the adsorbent. The moisture desorbed from the adsorbent is given to the second air passing through the second adsorption heat exchanger (62). Thereafter, the humidified second air sequentially passes through the eighth opening (58), the second outflow passage (46), and the air supply fan (25), and serves as supply air (SA) from the air supply outlet (24). Supplied indoors.

<Switching control of four-way switching valve (64)>
Next, specific switching control of the four-way switching valve (64) will be described.

    As described above, the first operation and the second operation are alternately switched during the dehumidifying operation, while the first operation and the second operation are alternately switched during the humidifying operation. This switching is performed by the circulation switching means (71), for example, by switching the four-way switching valve (64) every 3 minutes.

    At the time of switching, before the differential pressure reducing means (80) switches the four-way switching valve (64) of the circulation switching means (71), the compressor (63) is stopped for a predetermined time, and the four-way switching valve (64) Restart the compressor (63) after switching. By stopping the compressor (63) by the differential pressure reducing means (80), the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is reduced, and the refrigerant flows instantaneously from the high pressure side to the low pressure side. Can be suppressed. As a result, the refrigerant generation noise at the time of switching is suppressed.

-Effect of Embodiment 1-
As described above, according to the present embodiment, the refrigerant is changed from the high pressure side to the low pressure side because the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is reduced before switching the refrigerant circulation. The operation that flows instantaneously does not occur, and it is possible to prevent the noise generated by the refrigerant. In particular, even when the switching frequency is high, the sound of the refrigerant does not become a problem.

    In addition, since the compressor (63) is stopped before the four-way switching valve (64) is switched, the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) can be reliably reduced. Thus, it is possible to reliably prevent refrigerant generation noise at the time of switching.

<Embodiment 2 of the invention>
Next, Embodiment 2 of the present invention will be described in detail.

    In this embodiment, instead of the differential pressure reducing means (80) of Embodiment 1 stopping the compressor (63), the capacity of the compressor (63) is reduced. .

    That is, in the present embodiment, the compressor (63) is configured such that the operating capacity is variable, and for example, the operating frequency is switched to a plurality of stages by an inverter. The differential pressure reducing means (80) reduces the operating frequency of the compressor (63) before switching the four-way switching valve (64), and after switching the four-way switching valve (64), the compressor (63) The operation frequency is returned.

    Therefore, according to the present embodiment, since the operating frequency of the compressor (63) is reduced before the switching of the four-way switching valve (64), the difference between the high pressure side and the low pressure side of the refrigerant circuit (60). Since the pressure can be reduced, it is possible to prevent refrigerant generation noise at the time of switching. Moreover, since the operation of the compressor (63) is continued, it is possible to suppress a decrease in humidity control capability. Other configurations, operations, and effects are the same as those in the first embodiment.

Embodiment 3 of the Invention
Next, Embodiment 3 of the present invention will be described in detail.

    In this embodiment, instead of the differential pressure reducing means (80) of Embodiment 1 stopping the compressor (63), the opening of the expansion valve (65) is opened. .

    That is, in the present embodiment, the expansion valve (65) is configured to have a variable opening, and for example, the opening is configured to change in multiple stages by an electric valve. The differential pressure reducing means (80) increases the opening of the expansion valve (65) before switching the four-way switching valve (64), for example, fully opens the expansion valve (65), and opens the four-way switching valve. The opening of the expansion valve (65) is returned after switching (64).

    Therefore, according to this embodiment, since the opening degree of the expansion valve (65) is increased before the switching of the four-way switching valve (64), the difference between the high pressure side and the low pressure side of the refrigerant circuit (60). Since the pressure can be reduced, it is possible to prevent refrigerant generation noise at the time of switching. Moreover, since the operation of the compressor (63) is continued, it is possible to suppress a decrease in humidity control capability. Other configurations, operations, and effects are the same as those in the first embodiment.

<Embodiment 4 of the Invention>
Next, a fourth embodiment of the present invention will be described in detail based on the drawings.

    In this embodiment, as shown in FIG. 8, instead of the differential pressure reducing means (80) of the first embodiment stopping the compressor (63), the refrigerant bypasses the expansion valve (65). It is what you do.

    That is, the differential pressure reducing means (80) of the present embodiment includes a bypass passage (81), a bypass valve (82), and a flow rate regulator (83), and valve control means ( 84).

    The bypass path (81) is connected at both ends to both sides of the expansion valve (65), and the refrigerant bypasses the expansion valve (65) so as to bypass the first adsorption heat exchanger (61) and the second adsorption heat exchanger (62). ) Between each other.

    The bypass valve (82) is configured by a valve that switches between a fully open position and a fully closed position, and bypasses the refrigerant, and is configured by a normally closed valve that is fully closed during normal operation.

    The flow rate regulator (83) constitutes a flow rate regulation mechanism such as a capillary tube, and is provided in series with the bypass valve (82). The flow rate regulator (83) is configured to regulate the refrigerant flowing through the bypass passage (81).

    The valve control means (84) is configured to open the bypass valve (82) before switching the four-way switching valve (64) and close the bypass valve (82) after switching the four-way switching valve (64). ing.

    Accordingly, when the first operation and the second operation are alternately switched during the dehumidifying operation and the humidifying operation, before the four-way switching valve (64) of the circulation switching means (71) is switched, the valve control means (84) Opens the bypass valve (82) and closes the bypass valve (82) after switching the four-way switching valve (64). The opening of the bypass valve (82) by the valve control means (84) reduces the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60), and suppresses the instantaneous flow of refrigerant from the high pressure side to the low pressure side. can do. As a result, the refrigerant generation noise at the time of switching is suppressed.

    According to the present embodiment, since the flow rate regulator (83) is provided in the bypass passage (81), the refrigerant flows from the high pressure side to the low pressure side via the bypass valve (82) when the bypass valve (82) is opened. It is possible to suppress the movement that flows instantaneously. As a result, refrigerant generation noise due to the opening of the bypass valve (82) is suppressed. Other configurations, operations, and effects are the same as those in the first embodiment.

    In the present embodiment, the capillary tube is applied to the flow rate regulator (83), but an electric valve with adjustable opening may be applied as the flow rate adjustment mechanism. At this time, the bypass valve (82) may be configured as a valve whose opening degree is adjustable, and the bypass valve (82) may have a flow rate adjusting function as the flow rate regulator (83).

    In the present embodiment, the flow rate regulator (83) is provided in the bypass passage (81). However, the flow rate may be adjusted by the diameter of the bypass passage (81). 83) may be omitted.

<Embodiment 5 of the Invention>
Next, a fifth embodiment of the present invention will be described in detail based on the drawings.

    In the present embodiment, as shown in FIG. 9, the refrigerant in the fourth embodiment is bypassed from the expansion valve (65) so that the refrigerant bypasses from the discharge side to the suction side of the compressor (63). It is a thing.

    That is, the differential pressure reducing means (80) of the present embodiment includes the bypass passage (81), the bypass valve (82), and the flow rate regulator (83), as in the fourth embodiment, and the controller (70). Provided valve control means (84).

    The bypass path (81) is connected at both ends to the discharge pipe (6d) and suction pipe (6e) of the compressor (63) to connect the discharge side and suction side of the compressor (63), and the refrigerant is compressed. The machine (63) is configured to flow from the discharge side to the suction side. The bypass valve (82), the flow rate regulator (83), and the valve control means (84) are the same as those in the fourth embodiment.

    Accordingly, when the first operation and the second operation are alternately switched during the dehumidifying operation and the humidifying operation, before the four-way switching valve (64) of the circulation switching means (71) is switched, the valve control means (84) Opens the bypass valve (82) and closes the bypass valve (82) after switching the four-way switching valve (64). Since the refrigerant flows from the discharge side to the suction side of the compressor (63) by the opening of the bypass valve (82) by the valve control means (84), the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is small. Thus, the operation of the refrigerant flowing instantaneously from the high pressure side to the low pressure side can be suppressed. As a result, the refrigerant generation noise at the time of switching is suppressed.

    In addition, according to the present embodiment, the flow regulator (83) suppresses an operation in which the refrigerant instantaneously flows from the high pressure side to the low pressure side via the bypass valve (82) when the bypass valve (82) is opened. Can do. Refrigerant generation noise due to the opening of the bypass valve (82) is suppressed.

    In the present embodiment, as in the fourth embodiment, an electric valve or the like whose opening degree can be adjusted may be applied as the flow rate adjusting mechanism (83), and the bypass valve (82) has a flow rate adjusting function. Also good. Further, the flow rate may be adjusted by the diameter of the bypass passage (81). Other configurations, operations, and effects are the same as those in the fourth embodiment.

<Sixth Embodiment of the Invention>
Next, a sixth embodiment of the present invention will be described in detail based on the drawings.

    In the present embodiment, as shown in FIG. 10, the differential pressure reducing means (80) is replaced with a refrigerant instead of the differential pressure reducing means (80) of the first embodiment stopping the compressor (63). The amount of circulation is reduced.

    That is, the differential pressure reducing means (80) of the present embodiment includes an on-off valve (85) provided in the suction pipe (6e) of the compressor (63), which is a gas pipe through which gas refrigerant always flows, and a controller ( 70) provided with a valve control means (84).

    The on-off valve (85) is composed of a valve that switches between a fully open position and a fully closed position, and is provided between the second port of the four-way selector valve (64) and the suction port of the compressor (63), It consists of a normally open valve that is fully open during normal operation.

    The valve control means (84) is configured to close the opening / closing valve (85) before switching the four-way switching valve (64) and to open the opening / closing valve (85) after switching the four-way switching valve (64). ing.

    Accordingly, when the first operation and the second operation are alternately switched during the dehumidifying operation and the humidifying operation, before the four-way switching valve (64) of the circulation switching means (71) is switched, the valve control means (84) Closes the on-off valve (85) and opens the on-off valve (85) after switching the four-way selector valve (64). By closing the on-off valve (85) by the valve control means (84), the upstream side of the on-off valve (85) is maintained in a high pressure state.

    That is, the on-off valve (4) from the discharge side of the compressor (63) through the four-way switching valve (64), the first adsorption heat exchanger (61), the expansion valve (65) and the second adsorption heat exchanger (62). Up to 85) is maintained at high pressure. Therefore, the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) is reduced, and when the four-way selector valve (64) is switched, the operation of the instantaneous flow of refrigerant from the high pressure side to the low pressure side is suppressed. Can do. As a result, the refrigerant generation noise at the time of switching is suppressed.

    Further, in the present embodiment, since the refrigerant sucked into the compressor (63) is suppressed, liquid back in which the liquid refrigerant returns to the compressor (63) can be reliably prevented. Other configurations, operations, and effects are the same as those in the first embodiment.

    In the present embodiment, the on-off valve (85) is provided in the suction pipe (6e) of the compressor (63). However, instead of the on-off valve (85) of the suction pipe (6e), FIG. As shown, the on-off valve (85) may be provided in the discharge pipe (6d) of the compressor (63), which is a gas pipe through which gas refrigerant always flows.

    That is, the on-off valve (85) is provided between the compressor (63) and the first port of the four-way switching valve (64). In this case, when the on-off valve (85) is closed, the on-off valve (85) to the four-way switching valve (64), the first adsorption heat exchanger (61), the expansion valve (65), and the second adsorption heat exchanger (62 ) Through the suction side of the compressor (63) is maintained in a low pressure state.

    The on-off valve (85) is not limited to being fully closed, and the opening degree may be reduced to reduce the refrigerant circulation amount.

    In the present embodiment, the differential pressure reducing means (80) such as the second embodiment may be used in combination.

<Other embodiments>
The present invention may be configured as follows for each of the above embodiments.

    Although the switching mechanism (64) in each of the above embodiments is the four-way switching valve (64), the refrigerant circulation direction may be switched by a bridge circuit and four valves provided in the bridge circuit. Even in this case, it is possible to reduce the refrigerant generation sound when the refrigerant circulation direction is switched by opening and closing the valve.

    The differential pressure reducing means (80) is such that the compressor (63) and the like are restored after the switching mechanism (64) is switched, but the compressor (63) and the bypass valve (82) are restored. May be immediately before the switching of the switching mechanism (64), in short, as long as the refrigerant pressure state can suppress the generation of refrigerant at the time of switching.

    As described above, the present invention is useful for a humidity control apparatus that performs adsorption and desorption of moisture by switching the refrigerant circulation direction, and particularly for a humidity control apparatus having a heat exchanger carrying an adsorbent. Are suitable.

It is a circuit diagram which shows the refrigerant circuit of the humidity control apparatus of Embodiment 1. It is a schematic block diagram which shows the humidity control apparatus of Embodiment 1. It is a perspective view which shows the adsorption heat exchanger of Embodiment 1. FIG. It is a schematic block diagram of the humidity control apparatus which shows the flow of the air in the 1st operation | movement of the dehumidification driving | operation of Embodiment 1. It is a schematic block diagram of the humidity control apparatus which shows the flow of the air in 2nd operation | movement of the dehumidification driving | operation of Embodiment 1. It is a schematic block diagram of the humidity control apparatus which shows the flow of the air in the 1st operation | movement of the humidification driving | operation of Embodiment 1. It is a schematic block diagram of the humidity control apparatus which shows the flow of the air in 2nd operation | movement of the humidification driving | operation of Embodiment 1. It is a circuit diagram which shows the refrigerant circuit of the humidity control apparatus of Embodiment 4. It is a circuit diagram which shows the refrigerant circuit of the humidity control apparatus of Embodiment 5. It is a circuit diagram which shows the refrigerant circuit of the humidity control apparatus of Embodiment 6.

Explanation of symbols

10 Humidity control device
60 Refrigerant circuit
61 First adsorption heat exchanger (first heat exchanger)
62 Second adsorption heat exchanger (second heat exchanger)
63 Compressor
64 Four-way selector valve (switching mechanism)
65 Expansion valve (expansion mechanism)
70 controller
71 Circulation switching means
80 Means to reduce differential pressure
81 Bypass
82 Bypass valve
83 Flow controller (Flow control mechanism)
84 Valve control means
85 On-off valve

Claims (8)

The compressor (63), the switching mechanism (64), the first heat exchanger (61), the expansion mechanism (65), and the second heat exchanger (62) are connected so that the refrigerant circulation is reversible, and the vapor compression Equipped with a refrigerant circuit (60) that performs a refrigerating cycle,
A humidity control apparatus in which an adsorbent that adsorbs and desorbs moisture is supported on the surfaces of the first heat exchanger (61) and the second heat exchanger (62),
In order to alternately perform the adsorption and desorption of moisture in the first heat exchanger (61) and the second heat exchanger (62), the switching mechanism (64) is switched to change the refrigerant in the refrigerant circuit (60). Circulation switching means (71) for switching the circulation direction;
Humidity adjustment characterized by comprising differential pressure reducing means (80) for reducing the differential pressure between the high pressure side and the low pressure side of the refrigerant circuit (60) before the circulation switching of the circulation switching means (71). apparatus. In claim 1,
The humidity control apparatus, wherein the differential pressure reducing means (80) is configured to stop the compressor (63). In claim 1,
The compressor (63) has a variable capacity,
The humidity control apparatus, wherein the differential pressure reducing means (80) is configured to reduce an operating capacity of the compressor (63). In claim 1,
The expansion mechanism (65) is composed of an expansion valve with variable opening,
The humidity control apparatus, wherein the differential pressure reducing means (80) is configured to open an opening of the expansion valve. In claim 1,
The differential pressure reducing means (80) includes a bypass passage (81) that bypasses the expansion mechanism (65) and a normally closed bypass valve (82) provided in the bypass passage (81), and a circulation switching means. A humidity control apparatus configured to open the bypass valve (82) before switching the circulation of (71). In claim 1,
The differential pressure reducing means (80) includes a bypass passage (81) connecting the discharge side and the suction side of the compressor (63), and a normally closed bypass valve (82) provided in the bypass passage (81). The humidity control apparatus is characterized in that the bypass valve (82) is opened before the circulation switching of the circulation switching means (71). In claim 5 or 6,
The said pressure difference reducing means (80) is equipped with the flow volume adjustment mechanism (83) provided in the bypass (81), The humidity control apparatus characterized by the above-mentioned. In claim 1,
The differential pressure reducing means (80) includes a normally open on-off valve (85) provided in a gas pipe (6b, 6c) connected to the compressor (63) and through which a gas refrigerant always flows. 71) A humidity control device configured to close the on-off valve (85) before switching to circulation.

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