JP2010243003A - Dehumidification system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a dehumidification system excellent in energy saving performance capable of reducing a necessary cooling or heating capacity more than before. <P>SOLUTION: The dehumidification system includes a first air heat exchanger (63) connected to a circulation circuit (60) for circulating a prescribed heat medium and arranged at the upstream side of air cooling parts (61, 115) in an air passage (52), and a second air heat exchanger (64) connected to the circulation circuit (60) in series with the first air heat exchanger (63) and arranged at the downstream side of the air cooling parts (61, 115) in the air passage (52). <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a dehumidification system that cools and dehumidifies air and supplies the dehumidified air to a room.

  Conventionally, a dehumidification system that supplies dehumidified air into a room is known.

  For example, Patent Document 1 discloses this type of dehumidification system. In this dehumidification system, a cooling heat exchanger as an air cooling unit is provided in an air passage in the casing. The cooling heat exchanger is connected to a heat medium circuit in which a heat medium such as water circulates. The heat medium circuit is provided with a pump for circulating the heat medium and a heat medium cooling unit for cooling the circulating heat medium.

  During operation of this dehumidification system, the pump is operated and water circulates in the heat medium circuit. This water flows through the cooling heat exchanger after being cooled by the heat medium cooling section. Air flows through the air passage when the fan is operated. For this reason, in the cooling heat exchanger, water and air exchange heat, and the air is cooled to a dew point temperature or lower. As a result, moisture in the air condenses, thereby dehumidifying the air. As described above, the cooled and dehumidified air is supplied into the room.

JP 2006-112780 A

  As described above, in this type of dehumidifying system, air must be cooled to a dew point temperature or lower by a cooling heat exchanger (air cooling unit) in order to dehumidify the air. Therefore, the required cooling capacity in the air cooling section becomes relatively large, and there is a problem that energy saving performance is impaired.

  This invention is made | formed in view of this point, The objective is to provide the dehumidification system excellent in energy-saving property.

  The first invention includes a casing (51) that forms an air passage (52) through which air flows, and an air cooling section (61, 115) provided in the air passage (52), wherein the air cooling section (61, 115) The target is a dehumidification system that cools and dehumidifies air and supplies the dehumidified air to the room. The dehumidification system is connected to a circulation circuit (60, 130) through which a predetermined heat medium circulates, and is arranged on the upstream side of the air cooling section (61, 115) in the air passage (52). (63) and a first air heat exchanger (63) connected in series to the circulation circuit (60, 130) and disposed downstream of the air cooling section (61, 115) in the air passage (52). And a two-air heat exchanger (64).

  In the first invention, in the air passage (52) in the casing (51), the first air heat exchanger (63) is provided on the upstream side of the air cooling part (61, 115), and downstream of the air cooling part (61, 115). A second air heat exchanger (64) is provided on the side. The first air heat exchanger (63) and the second air heat exchanger (64) are connected to a circulation circuit (60, 130), and a predetermined heat medium is circulated in the circulation circuit (60, 130). The air flowing through the air passage (52) first passes through the first air heat exchanger (63). In the first air heat exchanger (63), the air and the heat medium exchange heat. As a result, in the first air heat exchanger (63), air can be cooled by the heat medium. The air cooled by the first air heat exchanger (63) is cooled to the dew point temperature or lower by the air cooling section (61, 115) and dehumidified. The air dehumidified by the air cooling unit (61, 115) flows through the second air heat exchanger (64).

  In the second air heat exchanger (64), a heat medium having a relatively high temperature after absorbing heat from the air in the first air heat exchanger (63) described above flows. For this reason, in the second air heat exchanger (64), air is heated by the heat medium by exchanging heat between the air and the heat medium. As a result, the relative humidity of the air decreases as the temperature of the air increases. On the other hand, the heat medium radiated to the air by the second air heat exchanger (64) is sent again to the first air heat exchanger (63) and used for cooling the air. The air dehumidified as described above flows out of the air passage (52) and is supplied to the room.

  According to a second aspect of the present invention, in the first aspect of the present invention, the air passage (52) further includes an air heating section (55) arranged on the downstream side of the second air heat exchanger (64) to heat the air. It is characterized by being.

  In the second invention, the air heating section (55) is provided on the downstream side of the second air heat exchanger (64). For this reason, the air after passing through the second air heat exchanger (64) can be heated by the air heating section (55). Thereby, the relative humidity of the air after passing through the air heating section (55) can be further reduced. Here, since the air before flowing in the air heating unit (55) is already heated by the second air heat exchanger (64) as described above, the air is heated by the air heating unit (55). The heating capacity required to do this can be reduced.

  According to a third invention, in the first or second invention, the first air heat exchanger (63) is located on the downstream side of the air passage (52) and the inflow portion (73a) into which the heat medium flows. ), An outflow part (73b) located upstream of the air passage (52) from which the heat medium flows out, and an intermediate formed between the inflow part (73a) and the outflow part (73b) And a flow path part (63c).

  In the first air heat exchanger (63) of the third invention, a heat medium inflow portion (73a) is provided on the downstream side of the air passage (52), and a heat medium outflow portion (73b) is provided in the air passage ( 52), an intermediate flow path portion (63c) through which the heat medium flows is provided between the inflow portion (73a) and the outflow portion (73b). Thereby, in the 1st air heat exchanger (63), it can be made to exchange heat by flowing air and a heat carrier so that it may counter substantially. That is, in the present invention, the first air heat exchanger (63) can function as a so-called counter flow heat exchanger. If it does in this way, since the temperature of the air which flowed out the 1st air heat exchanger (63) approaches the temperature of the heat carrier which flows into an inflow part (73a), compared with a parallel flow type, for example, the 1st air heat exchange The cooling effect in the vessel (63) can be improved.

  On the other hand, the temperature of the heat medium flowing through the outflow part (73b) of the first air heat exchanger (63) approaches the temperature of the air flowing into the first air heat exchanger (63). Thus, the temperature of the heat medium sent from the first air heat exchanger (63) to the second air heat exchanger (64) can be increased. Thereby, in the 2nd air heat exchanger (64), since the temperature difference of air and a heat medium becomes large, the heating capability of the air in a 2nd air heat exchanger (64) improves. As a result, in the second air heat exchanger (64), the relative humidity of the air can be further reduced.

  In a fourth aspect based on any one of the first to third aspects, the second air heat exchanger (64) is located downstream of the air passage (52) and the heat medium flows into the second air heat exchanger (64). Between the inflow part (74a), the outflow part (74b) located on the upstream side of the air passage (52) from which the heat medium flows out, and between the inflow part (74a) and the outflow part (74b) And an intermediate flow path portion (64c) to be formed.

  In the second air heat exchanger (64) of the fourth invention, the heat medium inflow portion (74a) is provided downstream of the air passage (52), and the heat medium outflow portion (74b) is provided in the air passage ( 52), an intermediate flow path portion (64c) through which the heat medium flows is provided between the inflow portion (74a) and the outflow portion (74b). Thereby, in the second air heat exchanger (64), heat can be exchanged by flowing the air and the heat medium so as to substantially face each other. In other words, in the present invention, the second air heat exchanger (64) can function as a so-called counter-flow heat exchanger. If it does in this way, since the temperature of the air which flowed out the 2nd air heat exchanger (64) approaches the temperature of the heat carrier which flows through an inflow part (74a), compared with a parallel flow type, for example, the 1st air heat exchange The heating capacity in the vessel (63) can be improved. As a result, in the second air heat exchanger (64), the relative humidity of the air can be further reduced.

  On the other hand, the temperature of the heat medium flowing through the outflow part (74b) of the second air heat exchanger (64) approaches the temperature of the air flowing into the second air heat exchanger (64). Thus, the cooling effect of the heat medium in the second air heat exchanger (64) can be improved. Therefore, the temperature of the heat medium sent from the second air heat exchanger (64) to the first air heat exchanger (63) can be further lowered, and the cooling effect in the first air heat exchanger (63). Can be further improved.

  In a fifth aspect based on any one of the first to fourth aspects, the air cooling section (61, 115) includes a heat medium cooling section (25) for cooling a predetermined heat medium, and the heat medium is It is characterized by comprising a cooling heat exchanger (61) connected to a circulating heat medium circuit (41).

  The air cooling section (61, 115) according to the fifth aspect of the invention includes a cooling heat exchanger (61) connected to a heat medium circuit (41) through which a predetermined heat medium circulates. In the heat medium circuit (41), the heat medium cooled by the heat medium cooling section (25) flows through the cooling heat exchanger (61). Thereby, in the cooling heat exchanger (61), the air flowing through the air passage (52) and the heat medium exchange heat, and the air is cooled to the dew point temperature or lower and dehumidified. In the present invention, as described above, since the air is cooled in advance by the first air heat exchanger (63), the necessary cooling capacity in the cooling heat exchanger (61) can be reduced.

  In a sixth aspect based on the fifth aspect, the cooling heat exchanger (61) is located on the downstream side of the air passage (52) and the inflow portion (71a) into which the heat medium flows, and the air An outflow part (71b) located on the upstream side of the passage (52) from which the heat medium flows out, and an intermediate flow path part (61c) formed between the inflow part (71a) and the outflow part (71b) ).

  In the sixth invention, the cooling heat exchanger (61) functions as a so-called counter flow heat exchanger. Therefore, the air cooling effect in the cooling heat exchanger (61) is improved, and the dehumidifying capacity is also improved.

  According to a seventh invention, in any one of the first to sixth inventions, the heat medium circulating in the circulation circuit (60, 130) is branched and the branched heat medium is joined to the circulation circuit (60, 130). A flow path (66), an auxiliary cooling section (95) for cooling the heat medium flowing through the branch flow path (66), and a partial flow rate adjusting mechanism (97) for adjusting the flow rate of the heat medium flowing through the branch flow path (66) And further comprising.

  In the seventh invention, the cooling capacity of the air in the first air heat exchanger (63) can be changed by adjusting the flow rate of the heat medium flowing through the branch flow path (66) by the split flow rate adjusting mechanism (97). . Specifically, for example, when the flow rate of the heat medium flowing through the branch flow path (66) is increased by the partial flow rate adjusting mechanism (97), the amount of the heat medium cooled by the auxiliary cooling unit (95) is increased. As a result, since the temperature of the heat medium returned to the circulation circuit (60, 130) is lowered, the cooling capacity of the first air heat exchanger (63) is increased.

  On the other hand, for example, when the flow rate of the heat medium flowing through the branch flow path (66) is reduced by the partial flow rate adjusting mechanism (97), the amount of the heat medium cooled by the auxiliary cooling unit (95) is also reduced. As a result, the temperature of the heat medium returned to the circulation circuit (60, 130) increases, and the cooling capacity of the first air heat exchanger (63) decreases.

  According to an eighth invention, in any one of the first to seventh inventions, the flow rate of the heat medium flowing through the first air heat exchanger (63) and the heat medium flowing through the second air heat exchanger (64). And a flow rate adjusting mechanism (35 to 37, 65) for individually adjusting the flow rate.

  In the eighth invention, each flow rate of the heat medium flowing through the first air heat exchanger (63) and the second air heat exchanger (64) can be adjusted by the flow rate adjusting mechanism (35 to 37, 65). ing. Thereby, the cooling / dehumidification capability of the air by the first air heat exchanger (63) can be changed by changing the flow rate of the heat medium of the first air heat exchanger (63), for example. Moreover, the heating capability of the air by a 2nd air heat exchanger (64) can be changed by changing the flow volume of the heat medium of a 2nd air heat exchanger (64).

  According to a ninth invention, in any one of the first to eighth inventions, an exhaust passage (59) for exhausting indoor air to the outside, a heat medium flowing in the circulation circuit (60, 130), and an exhaust flow A sensible heat exchanger (68) for exchanging heat with the air flowing through the passage (59) is further provided.

  In the ninth aspect of the invention, the indoor air is discharged to the outside through the exhaust passage (59). At this time, in the sensible heat exchanger (68) provided in the exhaust passage (59), the heat medium and the indoor air after being used for cooling the air in the first air heat exchanger (63) are heated. Exchange. Thereby, for example, under the condition where the temperature of the indoor air flowing through the exhaust passage (59) is relatively low, the cold air of the indoor air can be applied to the heat medium. Thereby, the cooling effect of the air in a 1st air heat exchanger (63) can be improved.

  Further, for example, under conditions where the temperature of the indoor air flowing through the exhaust passage (59) is relatively high, the heat of the indoor air can be applied to the heat medium. Thereby, the heating capability of the air in a 2nd air heat exchanger (64) can be improved.

  According to a tenth aspect of the present invention, in any one of the first to ninth aspects, the air on the upstream side of the first air heat exchanger (63) in the air passage (52) is transferred to the air cooling unit (61, 115). A bypass channel (140) for bypassing downstream and a bypass amount adjusting mechanism (141) for adjusting the flow rate of air flowing through the bypass channel (140) are further provided.

  In the tenth invention, the bypass passage (140) is provided in the air passage (52), and the flow rate of the air flowing through the bypass passage (140) can be adjusted by the bypass amount adjusting mechanism (141). For example, when the flow rate of air flowing through the bypass flow path (140) is increased, the flow rate of air cooled / dehumidified by the first air heat exchanger (63) and the air cooling unit (61, 115) decreases. Accordingly, the amount of latent heat processed by the dehumidification system is reduced. For example, when the flow rate of air flowing through the bypass flow path (140) is decreased, the flow rate of air cooled / dehumidified by the first air heat exchanger (63) and the air cooling unit (61, 115) increases. As described above, in the present invention, the operation according to the latent heat load can be performed by changing the flow rate of the air flowing through the bypass flow path (140).

  In the present invention, after the air is cooled in advance by the heat medium flowing through the first air heat exchanger (63), the air is cooled / dehumidified by the air cooling section (61, 115). Thereby, the required cooling capacity in an air cooling part (61,115) can be reduced. The second air heat exchanger (64) uses the heat of the air recovered by the first air heat exchanger (63) to heat the air after being cooled by the air cooling unit (61, 115). I have to. Thereby, the relative humidity of air can be reduced and dehumidification capability can be raised, and the cold energy collect | recovered from this air can be utilized again for the air cooling in a 1st air heat exchanger (63). As described above, in the present invention, the dehumidifying ability can be enhanced while improving the energy saving performance of the dehumidifying system.

  Moreover, in the second invention, since the air can be heated by the second air heat exchanger (64), the heating capacity necessary for heating the air by the air heating section (55) can be reduced. Thereby, the energy-saving property of a dehumidification system can further be improved.

  In the third aspect of the invention, the first air heat exchanger (63) performs heat exchange while facing air and the heat medium. For this reason, the first air heat exchanger (63) can cool the air to a lower temperature, and can heat the heat medium to a higher temperature. Therefore, since the required cooling capacity in the air cooling section (61, 115) and the required heating capacity in the air heating section (55) can be further reduced, the energy saving performance of the dehumidification system can be further improved.

  In the fourth aspect of the invention, the second air heat exchanger (64) exchanges heat while facing air and the heat medium. For this reason, the heating capability of the air in the second air heat exchanger (64) is further improved, and the amount of cold heat recovered from the air in the second air heat exchanger (64) is increased. Thereby, the air cooling effect in the first air heat exchanger (63) is further improved.

  In the fifth invention, air can be cooled by the cooling heat exchanger (61) as the air cooling section (61, 115). In the present invention, since the air is cooled in advance by the first air heat exchanger (63), the cooling required for cooling the air by the cooling heat exchanger (61) can be reduced. Thereby, the circulation amount of the heat medium which flows through a circulation circuit (60,130) can be decreased, and the cooling load of a heat medium cooling part (25) can be reduced. Particularly in the sixth aspect of the invention, since the heat exchange is performed while the air and the heat medium are opposed to each other in the cooling heat exchanger (61), the air cooling effect in the cooling heat exchanger (61) is further improved.

  7th invention can adjust the cooling capacity of a 1st air heat exchanger (63) suitably by adjusting the flow volume of the heat carrier sent to a branch flow path (66). Therefore, operation according to the humidity and temperature of the air to be processed can be performed. Moreover, air can be cooled / dehumidified also in the second air heat exchanger (64) by lowering the temperature of the heat medium by the auxiliary cooling section (95).

  In the eighth invention, since the flow rate of the heat medium flowing through the first air heat exchanger (63) and the second air heat exchanger (64) can be adjusted, the air in the first air heat exchanger (63) The cooling capacity and the air heating capacity in the second air heat exchanger (64) can be individually changed. Therefore, it is possible to perform an optimal operation according to the operating conditions.

  In the ninth invention, heat is exchanged between the air exhausted from the room and the heat medium flowing through the heat medium circuit (41) by the sensible heat exchanger (68). For this reason, when the room is cooled, the cooling capacity of the first air heat exchanger (63) can be improved by applying air cooling to the heat medium flowing through the heat medium circuit (41). For example, when the room is heated, the heating capacity of the second air heat exchanger (64) can be improved by applying air heat to the heat medium flowing through the heat medium circuit (41).

  In the tenth invention, the flow rate of air passing through the first air heat exchanger (63) and the air cooling section (61, 115) can be adjusted by adjusting the flow rate of air flowing through the bypass flow path (140). Therefore, since the dehumidification capacity and cooling capacity of the air by the dehumidification system can be individually adjusted, it is possible to perform the optimal cooling / dehumidification operation in accordance with the operation conditions and the operation needs.

FIG. 1 is a schematic configuration diagram illustrating the entire dehumidification system according to the first embodiment. FIG. 2 is a schematic configuration diagram of a heat exchanger in the air conditioning unit. FIG. 3 is a schematic configuration diagram of the heat exchanger in the air conditioning unit, and schematically shows the flow of the heat medium. FIG. 4 is a schematic configuration diagram illustrating the entire dehumidification system according to the first modification. FIG. 5 is a schematic configuration diagram of a heat exchanger in an air conditioning unit according to Modification 1, and schematically shows the flow of the heat medium when the three-way valve is in the first state. FIG. 6 is a schematic configuration diagram of a heat exchanger in the air conditioning unit according to Modification 1, and schematically shows the flow of the heat medium when the three-way valve is in the second state. FIG. 7 is a schematic configuration diagram illustrating the entire dehumidification system according to the second modification. FIG. 8 is a schematic configuration diagram illustrating the entire dehumidification system according to the third modification. FIG. 9 is a schematic configuration diagram illustrating an entire dehumidification system according to Modification 4. FIG. 10 is a schematic configuration diagram illustrating an entire dehumidification system according to the fifth modification. FIG. 11 is a schematic configuration diagram illustrating the entire dehumidification system according to Modification 6. FIG. 12 is a schematic configuration diagram illustrating an entire dehumidification system according to Modification 7. FIG. 13 is a schematic configuration diagram illustrating an entire air conditioning unit of a dehumidifying system according to Modification 8. FIG. 14 is a schematic configuration diagram illustrating an entire air conditioning unit of another example of the dehumidifying system according to the modification 8.

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

Embodiment 1
The dehumidifying system according to Embodiment 1 adjusts indoor humidity and temperature, and constitutes an air conditioning system (10) applied to, for example, a semiconductor manufacturing factory. As shown in FIG. 1, the air conditioning system (10) according to the first embodiment is configured to take outdoor air (OA) and send the air after adjusting the humidity and temperature to the room as supply air (SA). ing. The air conditioning system (10) includes a chiller unit (20) and an air conditioning unit (50). The air conditioning system (10) includes a refrigerant circuit (21), a heat dissipation circuit (31), and a heat medium circuit (41).

<Configuration of refrigerant circuit>
The refrigerant circuit (21) is included in the chiller unit (20). The refrigerant circuit (21) constitutes a closed circuit filled with the refrigerant. A compressor (22), a radiator (23), an expansion valve (24), and an evaporator (25) are connected to the refrigerant circuit (21). In the refrigerant circuit (21), a refrigerant is circulated to perform a vapor compression refrigeration cycle.

  The radiator (23) includes a first heat transfer tube (23a) connected to the refrigerant circuit (11) and a second heat transfer tube (23b) connected to the heat dissipation circuit (31). That is, the refrigerant circuit (21) is connected to the heat dissipation circuit (31) via the heat radiator (23). In the radiator (23), the refrigerant flowing through the first heat transfer tube (23a) and the heat medium flowing through the second heat transfer tube (23b) exchange heat. The evaporator (25) has a first heat transfer tube (25a) connected to the refrigerant circuit (11) and a second heat transfer tube (25b) connected to the heat medium circuit (41). That is, the refrigerant circuit (11) is connected to the heat medium circuit (41) via the evaporator (25). In the evaporator (25), the refrigerant flowing through the first heat transfer tube (25a) and the heat medium flowing through the second heat transfer tube (25b) exchange heat.

<Configuration of heat dissipation circuit>
The heat dissipation circuit (31) forms a closed circuit filled with water as a heat medium. The heat radiator (23), the water pump (32), and the cooling tower (33) are connected to the heat dissipation circuit (31). The water pump (32) conveys and circulates water in the heat dissipation circuit (31). The cooling tower (33) constitutes a cooling means for cooling the water circulating in the heat dissipation circuit (31). In the drawing, the arrow attached to the water pump (32) means the direction of circulation of the water flowing through the heat dissipation circuit (31).

<Configuration of circulation circuit>
The heat medium circuit (41) constitutes a closed circuit filled with water as a heat medium. The evaporator (25), the chiller side pump (42), and the cooling heat exchanger (61) are connected to the heat medium circuit (41). The evaporator (25) constitutes a heat medium cooling unit that cools the heat medium circulating in the heat medium circuit (41). The chiller side pump (42) constitutes a heat medium transport mechanism for transporting and circulating the water in the heat medium circuit (41). Details of the cooling heat exchanger (61) will be described later. In the drawing, the arrow attached to the chiller side pump (42) means the direction of circulation of the water flowing through the heat medium circuit (41).

  A water bypass pipe (43) is connected to the heat medium circuit (41). One end of the water bypass pipe (43) is connected between the chiller side pump (42) and the cooling heat exchanger (61). The other end of the water bypass pipe (43) is connected between the cooling heat exchanger (61) and the evaporator (25). The water bypass pipe (43) is provided with a bypass motor operated valve (44). The bypass motor operated valve (44) constitutes a flow rate control valve capable of adjusting the opening degree of the water bypass pipe (43).

<Configuration of air conditioning unit>
The air conditioning unit (50) has a rectangular parallelepiped casing (51) that is flat in the vertical direction. An air passage (52) through which air flows is formed in the casing (51). One end of the suction duct (53) is connected to the inflow end of the air passage (52). The other end of the suction duct (53) faces the outdoors. One end of an air supply duct (54) is connected to the outflow end of the air passage (52). The other end of the air supply duct (54) faces the indoor space (5).

  In the air passage (52), in order from the upstream side to the downstream side, the first air heat exchanger (63), the cooling heat exchanger (61), the second air heat exchanger (64), the electric heater ( 55), a sprinkler (56), and a blower (57) are provided. The electric heater (55) is provided on the downstream side of the second air heat exchanger (64) and constitutes an air heating unit that heats the air. The water sprinkler (56) constitutes a humidifying unit that sprays water in a tank (not shown) from the nozzle into the air. The blower (57) constitutes an air transport mechanism that transports air in the air passage (52).

  The cooling heat exchanger (61) described above constitutes an air cooling unit for cooling the air to the dew point temperature or lower. As shown in FIGS. 2 and 3, the cooling heat exchanger (61) has a plurality of fins (61a) and a heat transfer tube (61b) that penetrates the plurality of fins (61a). A heat exchanger of the type is configured. In the cooling heat exchanger (61), five rows of fin groups are arranged in the air flow direction.

  The cooling heat exchanger (61) includes an inflow portion (71a) that is located downstream of the air passage (52) and into which water flows and an outflow portion that is located upstream of the air passage (52) and from which water flows out. (71b). The cooling heat exchanger (61) has a first inflow pipe (71) connected to the inflow part (71a) and a first outflow pipe (72) connected to the outflow part (71b). The first inflow pipe (71) is provided with an on-off valve (81) capable of adjusting the opening degree of the first inflow pipe (71).

  In the cooling heat exchanger (61), the inflow part (71a) and the outflow part (71b) are each branched into a plurality by the flow dividers. Each branch portion of the inflow portion (71a) is connected to the inflow side of the plurality of path groups (61c, 61c,...) In the cooling heat exchanger (61), and the branch portion of the outflow portion (71b) is cooled by the cooling heat. It connects with the outflow side of a plurality of path groups (61c, 61c,...) In the exchanger (61). These path groups (61c, 61c,...) Are arranged vertically so as to be parallel to each other, and extend across the inflow portion (71a) and the outflow portion (71b). These path groups (61c, 61c,...) Constitute an intermediate flow path portion formed between the inflow portion (71a) and the outflow portion (71b).

  The air conditioning system (10) has a circulation circuit (60) through which water as a heat medium circulates. The first air heat exchanger (63) and the second air heat exchanger (64) described above are connected in series to the circulation circuit (60).

  The first air heat exchanger (63) is provided on the upstream side of the cooling heat exchanger (61) in the air passage (52). The first air heat exchanger (63) has a plurality of fins (63a) and a heat transfer tube (63b) that penetrates the plurality of fins (63a), and constitutes a so-called fin-and-tube heat exchanger. ing. In the first air heat exchanger (63), two rows of fin groups are arranged in the air flow direction. That is, the number of rows of fin groups of the first air heat exchanger (63) is smaller than the number of rows of fin groups of the cooling heat exchanger (61).

  The first air heat exchanger (63) is located on the downstream side of the air passage (52) and has an inflow portion (73a) into which water flows, and on the upstream side of the air passage (52), water flows out. And an outflow part (73b). The first air heat exchanger (63) has one end of the first relay pipe (73) connected to the outflow part (73b) and one end of the second relay pipe (74) connected to the inflow part (73a). is doing.

  In the first air heat exchanger (63), the inflow part (73a) and the outflow part (73b) are each branched into a plurality by the flow dividers. And each branch part of an inflow part (73a) connects with the inflow side of a plurality of path groups (63c, 63c, ...) in the 1st air heat exchanger (63), and each branch part of an outflow part (73b) Are connected to the outflow sides of the plurality of path groups (63c, 63c,...) In the first air heat exchanger (63). These path groups (63c, 63c,...) Are arranged vertically so as to be parallel to each other, and extend across the inflow portion (73a) and the outflow portion (73b). These path groups (63c, 63c,...) Constitute an intermediate flow path portion formed between the inflow portion (73a) and the outflow portion (73b).

  The second air heat exchanger (64) is provided on the downstream side of the cooling heat exchanger (61) in the air passage (52). The second air heat exchanger (64) includes a plurality of fins (64a) and a heat transfer tube (64b) penetrating the plurality of fins (64a), and constitutes a so-called fin-and-tube heat exchanger. ing. In the second air heat exchanger (64), three rows of fin groups are arranged in the air flow direction. That is, the number of fin groups in the second air heat exchanger (64) is smaller than the number of fin groups in the cooling heat exchanger (61), and the number of fin groups in the first air heat exchanger (63). More than the number.

  The second air heat exchanger (64) is located on the downstream side of the air passage (52) and has an inflow portion (74a) into which water flows in, and located on the upstream side of the air passage (52) and out of water. And an outflow portion (74b). The second air heat exchanger (64) has the other end of the first relay pipe (73) connected to the inflow part (74a) and the other end of the second relay pipe (74) to the outflow part (74b). Is connected.

  In the second air heat exchanger (64), the inflow part (74a) and the outflow part (74b) are each branched into a plurality by the flow dividers. And each branch part of an inflow part (74a) connects with the inflow side of a plurality of path groups (64c, 64c, ...) in the 2nd air heat exchanger (64), and each branch part of an outflow part (73b) Are connected to the outflow sides of the plurality of path groups (64c, 64c,...) In the second air heat exchanger (64). These path groups (64c, 64c,...) Are arranged vertically so as to be parallel to each other, and extend across the inflow portion (74a) and the outflow portion (74b). These path groups (64c, 64c,...) Constitute an intermediate flow path portion formed between the inflow portion (74a) and the outflow portion (74b).

  As described above, the first air heat exchanger (63), the first relay pipe (73), the second air heat exchanger (64), and the second relay pipe (74) are connected in this order, thereby closing. The circulation circuit (60) serving as a circuit is configured. The first relay pipe (73) is provided with a circulation pump (65) for transporting water in the circulation circuit (60).

<Configuration of controller>
The air conditioning system (10) includes a controller (100) as a control unit. The controller (100) receives a signal related to the operation status of the air conditioning system (10). The controller (100) then determines the cooling capacity of the chiller unit (20), the amount of circulating water in the water pump (32), the chiller side pump (42), and the circulation pump (65), the electric power according to this type of input signal. The heating capacity of the heater (55), the amount of water sprayed by the water sprinkler (56), the opening degree of the bypass electric valve (44) and the on-off valve (81), and the like are controlled.

-Driving action-
Next, the operation of the air conditioning system (10) will be described with reference to FIGS. The air conditioning system (10) is configured to perform a dehumidifying operation for dehumidifying the room.

  In the dehumidifying operation, the compressor (22), the water pump (32), the chiller side pump (42), the circulation pump (65), and the blower (57) of the chiller unit (20) are driven. Further, in the dehumidifying operation, basically, the electric heater (55) is energized and the sprinkler of the sprinkler (56) is stopped. Further, the controller (100) opens the on-off valve (81).

  In the refrigerant circuit (21), a refrigeration cycle is performed. Specifically, the refrigerant compressed by the compressor (22) flows through the radiator (23). In the radiator (23), the refrigerant flowing through the first heat transfer tube (23a) dissipates heat into the water flowing through the second heat transfer tube (23b) and condenses. The water heated by the second heat transfer tube (23b) of the radiator (23) radiates heat to the outdoor air in the cooling tower (33). The refrigerant condensed in the radiator (23) is depressurized by the expansion valve (24) as a depressurization mechanism, and then flows through the evaporator (25). In the evaporator (25), the refrigerant flowing through the first heat transfer tube (25a) absorbs heat from the water flowing through the second heat transfer tube (25b) and evaporates. The refrigerant evaporated in the evaporator (25) is sucked into the compressor (22) and compressed.

  The water cooled by the second heat transfer tube (25b) of the evaporator (25) passes through the chiller side pump (42) and is conveyed into the casing (51) of the air conditioning unit (50). This water flows through the first inflow pipe (71) and flows into the cooling heat exchanger (61). This water is divided into a plurality of path groups (61c, 61c,...), And flows through each path group (61c, 61c,...) Toward the upstream side of the air flow. The water that has passed through each path group (61c, 61c,...) Of the cooling heat exchanger (61) flows out to the first outflow pipe (72) and is sent to the evaporator (25).

  On the other hand, in the circulation circuit (60), the water conveyed by the circulation pump (65) flows through the first relay pipe (73) and flows into the second air heat exchanger (64). This water is divided into a plurality of path groups (64c, 64c,...), And flows through each path group (64c, 64c,...) Toward the upstream side of the air flow. The water that has passed through each path group (64c, 64c,...) Of the second air heat exchanger (64) is sent to the second relay pipe (74) and flows into the first air heat exchanger (63). This water is divided into a plurality of path groups (63c, 63c,...), And flows through each path group (63c, 63c,...) Toward the upstream side of the air flow. The water that has passed through each path group (63c, 63c,...) Of the first air heat exchanger (63) is sent to the first relay pipe (73).

  In the air conditioning unit (50), outdoor air (OA) taken into the suction duct (53) from the outside flows through the air passage (52) in the casing (51). This air first passes through the first air heat exchanger (63). In the first air heat exchanger (63), water and air flow so as to be substantially opposed to exchange heat. Specifically, in the first air heat exchanger (63), for example, air at about 30 ° C. and water at about 17 ° C. exchange heat, and the air at 30 ° C. is cooled to about 25 ° C. Further, the water flowing out of the first air heat exchanger (63) is heated to about 20 °, for example.

  The air cooled by the first air heat exchanger (63) passes through the cooling heat exchanger (61). In the cooling heat exchanger (61), water and air flow so as to substantially face each other to exchange heat. As a result, the air is cooled to a dew point temperature or lower (for example, about 10 ° C.) and dehumidified.

  The air cooled / dehumidified by the first air heat exchanger (63) flows through the second air heat exchanger (64). In the second air heat exchanger (64), the refrigerant and air flow so as to substantially face each other to exchange heat. Specifically, in the second air heat exchanger (64), for example, about 10 ° C. air and about 20 ° C. water exchange heat, and about 10 ° C. air is heated to about 13 ° C. The water flowing out of the second air heat exchanger (64) is cooled to about 17 ° C., for example.

  The air heated by the second air heat exchanger (64) is further heated by the electric heater (55). In addition, when the temperature of the air heated with the 2nd air heat exchanger (64) has already exceeded the indoor target temperature, you may perform control which stops electricity supply of an electric heater (55).

  The air dehumidified as described above is supplied to the indoor space (5) as supply air (SA) via the air supply duct (54).

-Effect of Embodiment 1-
In the above embodiment, the air before being cooled / dehumidified by the cooling heat exchanger (61) is cooled in advance by the first air heat exchanger (63). Thereby, since the required cooling capacity in the cooling heat exchanger (61) can be reduced, for example, the circulation amount of water flowing through the heat medium circuit (41) is reduced, or the cooling capacity of the evaporator (25) (that is, Compressor power) can be reduced. As a result, the energy saving performance of the air conditioning system (10) can be improved.

  In the second air heat exchanger (64), the air is heated using the heat recovered from the air in the first air heat exchanger (63). Thereby, since the input of the electric heater (55) for reheating air can also be reduced, the energy-saving property of an air conditioning system (10) can further be improved.

  Moreover, the cooling effect of air can be heightened by making a 1st air heat exchanger (63) into what is called a counterflow type. Moreover, since the temperature of the water flowing out of the first air heat exchanger (63) also becomes relatively high, the heating effect of air in the second air heat exchanger (64) can be enhanced. Furthermore, the 2nd air heat exchanger (64) can also be made into a counterflow type, and can improve the heating effect of air. Moreover, since the temperature of the water flowing out of the second air heat exchanger (64) becomes relatively low, the air cooling effect in the first air heat exchanger (63) can also be enhanced. In addition, the cooling heat exchanger (61) is also of a counterflow type, so that the air cooling effect in the cooling heat exchanger (61) can be enhanced and the dehumidifying performance of the dehumidifying system (10) is improved. be able to.

<< Modification of Embodiment 1 >>
In the first embodiment described above, the configurations of the following modifications may be employed. In the following description, the same points as those of the first embodiment described above are omitted.

<Modification 1>
The air conditioning system (10) according to the first modification shown in FIGS. 4 to 6 includes a branch channel (66) in which a part of the water circulating in the circulation circuit (60) branches and a branch channel (66). An auxiliary cooling unit (90) for cooling the flowing water is provided.

  The auxiliary cooling unit (90) has a refrigerant circuit (91) in which a refrigerant is filled and a vapor compression refrigeration cycle is performed. A compressor (92), a radiator (93), an expansion valve (94), and an evaporator (95) are sequentially connected to the refrigerant circuit (91) of the auxiliary cooling unit (90). The refrigerant circuit (91) is connected to the branch channel (66) via the evaporator (95). And the evaporator (95) comprises the auxiliary | assistant cooling part which cools the heat medium which flows through a branch flow path (66) with a refrigerant | coolant.

  The branch channel (66) has a first branch pipe (66a) on the inflow side of the evaporator (95) and a second branch pipe (66b) on the outflow side of the evaporator (95). The inflow end of the first branch pipe (66a) is connected to the upstream side of the first relay pipe (73). Further, a three-way valve (97) is provided at a connection portion between the first branch pipe (66a) and the first relay pipe (73). The three-way valve (97) can adjust the distribution amount of the heat medium sent from the outflow part (73b) of the first air heat exchanger (63) to the first relay pipe (73) and the first branch pipe (66a). It is configured. Specifically, the three-way valve (97) sends all the heat medium flowing out of the outflow part (73b) of the first air heat exchanger (63) to the first relay pipe (73) (the state shown in FIG. 5). ) Or a state in which the heat medium flowing out from the outflow part (73b) of the first air heat exchanger (63) is divided into the first relay pipe (73) and the first branch pipe (66a) (the state shown in FIG. 6) ). The three-way valve (97) can be switched to a state in which all the heat medium that has flowed out of the outflow portion (73b) of the first air heat exchanger (63) is sent to the first branch pipe (66a). As described above, the three-way valve (97) constitutes a partial flow rate adjusting mechanism that adjusts the flow rate of the heat medium flowing through the branch flow path (66).

  In the dehumidifying operation of the air conditioning system (10) of Modification 1, the controller (100) has a three-way valve according to the temperature and humidity of the air to be processed, the indoor set temperature (target temperature) and the indoor set humidity (target humidity). The opening degree of (97) is controlled.

  Specifically, for example, during a normal dehumidifying operation, the controller (100) sets the three-way valve (97) as shown in FIG. As a result, the heat medium that has flowed out of the outflow portion (73b) of the first air heat exchanger (63) is not sent to the branch flow path (66), and all flows through the first relay pipe (73). Therefore, in this case, the same dehumidifying operation as that of the first embodiment described above is performed.

  On the other hand, for example, when the humidity or temperature of the air to be processed is extremely high or when the dehumidifying operation is performed under conditions where the indoor set temperature or set humidity is extremely low, the controller (100) sets the three-way valve (97) in FIG. The state shown in Thereby, a part of heat medium which flowed out the outflow part (73b) of a 1st air heat exchanger (63) is sent to a branch flow path (66). The heat medium flowing through the branch channel (66) is cooled by the evaporator (95) of the auxiliary cooling unit (90) and then sent to the second air heat exchanger (64). As a result, in this operation, air can be cooled / dehumidified also in the second air heat exchanger (64). Therefore, the desired dehumidifying performance can be obtained even under conditions where the so-called latent heat load is high.

<Modification 2>
The air conditioning system (10) according to the second modification shown in FIG. 7 is different from the first embodiment in the configuration of the air cooling unit. Specifically, in Modification 2, a refrigeration cycle unit (110) is provided in place of the chiller unit (20).

  The refrigeration cycle unit (110) has a refrigerant circuit (111) in which a refrigerant is filled to perform a vapor compression refrigeration cycle. In the refrigerant circuit (111), a compressor (112), a radiator (113), an expansion valve (114), and an evaporator (115) are connected. And in the modification 2, the evaporator (115) as an air cooling part is provided between the 1st air heat exchanger (63) and the 2nd air heat exchanger (64) in an air path (52). ing. That is, in Modification 2, the air flowing through the air passage (52) is cooled to the dew point temperature or lower by the refrigerant as the heat medium flowing through the evaporator (115) and dehumidified.

  Also in the modified example 2, since the air is pre-cooled by the first air heat exchanger (63), the necessary cooling capacity in the evaporator (115) can be reduced, and hence the power of the compressor (112) can be reduced. . Therefore, the energy saving performance of the air conditioning system (10) can be improved.

<Modification 3>
In the air conditioning system (10) according to Modification 3 shown in FIG. 8, a refrigerant circuit (130) as a circulation circuit is used instead of the first embodiment and the circulation circuit (60). The refrigerant circuit (130) is configured to perform a vapor compression refrigeration cycle by circulating a refrigerant as a heat medium.

  A compressor (131), a second air heat exchanger (64), an expansion valve (132), and a first air heat exchanger (63) are sequentially connected to the refrigerant circuit (130). And in the modification 3, a 2nd air heat exchanger (64) functions as a radiator (condenser), and a 1st air heat exchanger (63) functions as an evaporator.

  That is, when the air flowing through the air passage (52) passes through the first air heat exchanger (63), the refrigerant absorbs heat from the air and evaporates, thereby precooling the air. Moreover, when the air cooled / dehumidified by the cooling heat exchanger (61) passes through the second air heat exchanger (64), the refrigerant releases heat to the air, thereby heating the air. Also in the modification 3, the heat | fever collect | recovered from the air to the refrigerant | coolant in the 1st air heat exchanger (63) is utilized for the heating of the air in a 2nd air heat exchanger (64). Therefore, the energy saving performance of the air conditioning system (10) can be improved.

<Modification 4>
The circulation circuit (41) of the fourth modification shown in FIG. 9 is provided with a first water tank (35), a second water tank (36), and an auxiliary pump (37).

  The first water tank (35) and the second water tank (36) constitute a heat medium storage unit for temporarily storing water as a heat medium. The first water tank (35) is provided on the suction side of the circulation pump (65) in the first relay pipe (73). The auxiliary pump (37) is provided in the second relay pipe (74). The second water tank (36) is provided on the suction side of the auxiliary pump (37) in the second relay pipe (74). The circulation pump (65) and the auxiliary pump (37) are, for example, centrifugal pumps, and are configured such that the conveyance flow rate of the heat medium is variable by changing the number of rotations of the motor.

  The first water tank (35), the second water tank (36), the auxiliary pump (37), and the circulation pump (65) are used for the flow rate of water flowing through the first air heat exchanger (63) and the second air heat exchange. The flow rate adjustment mechanism for individually adjusting the flow rate of the water flowing through the vessel (64) is configured.

  The controller (100) of the fourth modification is provided with a pump control unit. The pump control unit is configured to control the motor rotation speeds of the circulation pump (65) and the auxiliary pump (37) (that is, the conveyance flow rate of the heat medium).

  Specifically, the pump control unit adjusts the conveyance flow rates of the circulation pump (65) and the auxiliary pump (37) during the daytime and nighttime periods.

  In the daytime period, an operation (first pump control operation) is performed in which the water conveyance flow rate of the auxiliary pump (37) is larger than the water conveyance flow rate of the circulation pump (65). That is, during the first pump control operation, the flow rate of water flowing through the first air heat exchanger (63) is greater than the flow rate of water flowing through the second air heat exchanger (64). Here, during the daytime period, the temperature of the outdoor air (OA) is higher than that of the nighttime, but the flow rate of water flowing through the first air heat exchanger (63) is relatively large, so that the outdoor air is sufficient. To dehumidify. Further, if the flow rate of the water flowing through the second air heat exchanger (64) is made smaller than the flow rate of the water flowing through the first air heat exchanger (63) in this way, the first water tank (35) The amount of water heated by the 1 air heat exchanger (63) increases.

  In the nighttime period, an operation (second pump control operation) is performed in which the water conveyance flow rate of the circulation pump (65) is larger than the water conveyance flow rate of the auxiliary pump (37). That is, during the second pump control operation, the flow rate of water flowing through the second air heat exchanger (64) is greater than the flow rate of water flowing through the first air heat exchanger (63). Here, during the nighttime period, the temperature of the outdoor air (OA) is lower than that of the daytime, but the flow of water flowing through the second air heat exchanger (64) becomes relatively small, so that the outdoor air is excessive. It is avoided that it cools down. At night, a relatively large amount of relatively hot water stored in the first water tank (35) during the daytime flows through the second air heat exchanger (64). For this reason, in the second air heat exchanger (64), heat exchange between water and air is promoted, and air heating and water cooling are promoted.

  Further, when the flow rate of water flowing through the first air heat exchanger (63) is made smaller than the flow rate of water flowing through the second air heat exchanger (64) in this way, the second water tank (36) The amount of water cooled by the two air heat exchanger (64) increases.

  Thereafter, when the first pump control operation is performed again in the daytime period, as described above, the water conveyance flow rate of the auxiliary pump (37) becomes larger than the water conveyance flow rate of the circulation pump (65). As a result, a relatively low temperature water stored in the second water tank (36) during the nighttime period flows in a large amount through the first air heat exchanger (63). For this reason, in the first air heat exchanger (63), heat exchange between water and air is promoted, and air cooling and water heating are promoted.

  As described above, in the fourth modification, water is accumulated in each water tank (35, 36) while changing the water transfer flow rate of the circulation pump (65) and the auxiliary pump (37) between night and daytime. By going, the cold energy collected at night can be used for cooling the air during the daytime, and the heat collected during the daytime can be used for heating the air at night. As a result, the energy saving performance during the heat recovery operation of the air conditioning system (10) can be further improved.

  In the modified example 4, as the method of switching between the daytime operation and the nighttime operation described above, for example, a method using a timer or the like, a method of switching the operation according to the outdoor temperature (for example, the outdoor temperature detected by the sensor is For example, the first pump control operation is performed when the temperature exceeds a predetermined value, and the second pump control operation is performed when the outdoor temperature detected by the sensor becomes lower than the predetermined value.

<Modification 5>
The air conditioning system (10) according to the modified example 5 shown in FIG. 10 is provided with an internal heat exchanger (28) for exchanging heat between the water in the heat dissipation circuit (31) and the water in the circulation circuit (60). Yes. Specifically, a shunt pipe (26) for shunting a part of the water in the heat dissipation circuit (31) is connected to the heat dissipation circuit (31). The shunt pipe (26) is provided with a flow rate control valve (27) whose opening degree can be adjusted. The internal heat exchanger (28) exchanges heat between the water circulating in the circulation circuit (60) and the water divided into the distribution pipe (26), so that the water in the circulation circuit (60) can be used by the water in the circulation circuit (26). It is configured to cool the water.

  Specifically, in the above-described dehumidifying operation, when the flow control valve (27) opens the shunt pipe (26) at a predetermined opening, water in the heat dissipation circuit (31) is shunted to the shunt pipe (26). This water is cooled by exchanging heat with relatively cool water flowing through the circulation circuit (60) in the internal heat exchanger (28). As described above, in the fifth modification, for example, under the condition that the outdoor temperature is low, the cooling water of the circulation circuit (60) can be used for cooling the water of the heat dissipation circuit (31).

<Modification 6>
The air conditioning system (10) according to the modified example 6 shown in FIG. 11 is provided with an exhaust duct (59) and a duct side heat exchanger (68). The exhaust duct (59) has one end connected to the indoor space (5) and the other end facing the outside air. That is, the exhaust duct (59) forms an exhaust passage for discharging the air in the indoor space (5) to be air-conditioned by the air conditioning system (10) to the outside as exhaust air (EA). The duct side heat exchanger (68) is arrange | positioned so that the inside of an exhaust duct (59) may be straddled. The duct side heat exchanger (68) is connected to a pipe (first relay pipe (73)) between the first air heat exchanger (63) and the second air heat exchanger (64). . In other words, the duct-side heat exchanger (68) uses water sent from the first air heat exchanger (63) to the second air heat exchanger (64) and air sent from the indoor space (5) to the outside. A sensible heat exchanger for heat exchange is formed.

  Thereby, in the modification 6, the cold of indoor air can be provided to the water of a circulation circuit (60), for example in summer. Therefore, in the air conditioning unit (50), the cold heat collected in this way on the circulation circuit (60) side can be used for cooling the air in the first air heat exchanger (63). Further, for example, in winter, the heat of room air can be applied to the water in the circulation circuit (60). Therefore, in the air conditioning unit (50), the heat recovered in this way to the circulation circuit (60) side can be used for heating the air in the second air heat exchanger (64).

<Modification 7>
The air conditioning unit (50) of the air conditioning system (10) according to the modified example 7 shown in FIG. 12 has three indoor spaces (first indoor space (5a), second indoor space (5b), and third indoor space (5c )) To supply supply air (SA). That is, the outflow side of the air supply duct (54) of the air conditioning unit (50) has three air supply parts (first air supply part (54a), second air supply part (54b), and third air supply part ( Branch to 54c)). Then, the outflow end of the first air supply section (54a) faces the first indoor space (5a), the outflow end of the second air supply section (54b) faces the second indoor space (5b), and the third air supply The outflow end of the section (54c) faces the third indoor space (5c). An exhaust duct (59a) is connected to the first indoor space (5a).

  Moreover, the air conditioning system (10) of the modification 7 has the 1st and 2nd auxiliary | assistant air conditioning unit (120,130). The first auxiliary air conditioning unit (120) targets the second indoor space (5b) for air conditioning, and the second auxiliary air conditioning unit (130) targets the third indoor space (5c) for air conditioning.

  Each auxiliary air conditioning unit (120, 130) includes a casing (121, 131) that forms an air passage (122, 132), a suction duct (123, 133) that connects the inflow side of the air passage (122, 132) and the indoor space (5b, 5c), and air Air supply ducts (124, 134) connecting the outflow side of the passages (122, 132) and the indoor spaces (5b, 5c) are provided.

  In addition, in the air passages (122,132) of the auxiliary air conditioning units (122,132), the air heat exchanger (125,135), the electric heater (126,136), the water sprayer (127,137), and the blower are sequentially arranged from the upstream side to the downstream side. (128,138) are respectively arranged. A heat medium such as water is supplied to the heat transfer tube of each air heat exchanger (125, 135).

  In the air conditioning system (10), the air conditioning unit (50) and the auxiliary air conditioning units (122, 132) are operated in conjunction with each other. The air cooled / dehumidified by the air conditioning unit (50) is distributed from the air supply duct (54) to the three air supply parts (54a, 54b, 54c) and supplied to the indoor spaces (54a, 54b, 54c). The

  In each auxiliary air conditioning unit (120, 130), room air (RA) in each indoor space (5b, 5c) is taken into the air passage (122, 132) via the suction duct (123, 133). The air is cooled / dehumidified by the heat medium flowing through the air heat exchanger (125, 135), and then heated by the electric heater (126, 136). The air dehumidified as described above is supplied to each indoor space (5b, 5c) as supply air (SA).

<Modification 8>
The air conditioning system (10) according to the modified example 8 shown in FIG. 13 is provided with a branch duct (140) and an air flow rate control valve (141). The inflow end of the branch duct (140) is connected to the suction duct (53). The outflow end of the branch duct (140) faces the second air heat exchanger (64) and the electric heater (55) in the air passage (52). That is, the branch duct (140) bypasses the air upstream of the first air heat exchanger (63) in the air passage (52) to the downstream side of the second air heat exchanger (64). Is configured. The air flow rate adjustment valve (141) constitutes a bypass amount adjustment mechanism that adjusts the flow rate of the air flowing through the branch duct (140). Note that another mechanism such as a damper may be employed as the bypass amount adjusting mechanism.

  In the modification 8, the controller (100) controls the air flow rate control valve (141) according to the operation condition, so that the operation according to the latent heat load or the sensible heat load to be processed is possible.

  Specifically, for example, when the latent heat load to be processed is high, the opening degree of the air flow rate control valve (141) is reduced, and the flow rate of air flowing through the branch duct (140) is reduced. Thereby, since the flow rate of the air passing through the first air heat exchanger (63) and the cooling heat exchanger (61) becomes relatively large, the latent heat load can be sufficiently processed by cooling / dehumidifying the air. .

  In addition, for example, when the latent heat load to be processed is not so high, but the sensible heat load to be processed is relatively high, the opening of the air flow control valve (141) becomes large, and the air flowing through the branch duct (140) The flow rate increases. Thereby, the flow rate of the air passing through the first air heat exchanger (63) and the cooling heat exchanger (61) becomes relatively small. Therefore, since the cooling load of the evaporator (25) of the heat medium circuit (41) is reduced, the cooling capacity of the evaporator (25) can be reduced.

  As described above, in the modified example 8, since the operation according to the latent heat load or the sensible heat load can be performed, the latent heat load or the sensible heat load can be reliably processed while ensuring energy saving. The latent heat load to be processed by the air conditioning system (10) can be obtained from the difference between the indoor target humidity set in the controller (100) and the outdoor air humidity detected by a sensor or the like. The sensible heat load to be processed by the air conditioning system (10) can be obtained from the difference between the indoor target temperature set in the controller (100) and the outdoor air humidity detected by a sensor or the like.

  Moreover, in the modification 8, the heating / humidification operation which heats outdoor air with an electric heater (55) and further humidifies with a water sprayer (56) at the time of the heating operation which heats outdoor air with an electric heater (55) in winter etc. At that time, the air flow control valve (141) is fully opened. That is, at the time of heating operation or heating / humidifying operation, the first air heat exchanger (63), the cooling heat exchanger (61), and the second air heat exchanger (64) are in a dormant state. The flow rate of air flowing through the branch duct (140) is maximized. For this reason, the flow rate of air flowing through each heat exchanger (61, 63, 64) can be minimized, and the pressure loss in these heat exchangers (61, 63, 64) should be minimized. Can do. As a result, the power of the blower (57) can be reduced during heating operation or heating / humidifying operation.

  In addition, you may arrange | position so that the outflow end of the branch duct (140) of the modification 8 may face another location. Specifically, as shown in FIG. 14, for example, the outlet end of the branch duct (140) may be disposed so as to face the downstream side of the electric heater (55).

<< Other Embodiments >>
About the said embodiment, it is good also as the following structures.

  The air conditioning system (10) according to the above-described embodiment (including the above-described modifications) takes outdoor air (OA) into the air passage (52) and cools / dehumidifies the air. (RA) may be taken in and this air may be cooled / dehumidified.

  Moreover, in the said embodiment, although the electric heater (55) is used as a heating part which is provided in an air path (52) and heats air, the condenser of the refrigerant circuit in which a refrigerating cycle is performed, and other systems The heating part may be used.

  In addition, you may make it comprise an air-conditioning system (10) combining any two or more of the modifications 1-8 mentioned above mutually. Moreover, the above embodiment is an essentially preferable example, and is not intended to limit the scope of the present invention, its application, or its use.

  As described above, the present invention is useful for a dehumidification system that cools and dehumidifies air and supplies the dehumidified air to the room.

10 Air conditioning system (dehumidification system)
25 Evaporator (heat medium cooling part)
35 1st water tank (flow rate adjustment mechanism)
36 Second water tank (flow rate adjustment mechanism)
37 Auxiliary pump (flow control mechanism)
41 Heat transfer medium circuit
51 Casing
52 Air passage
55 Electric heater (air heating part)
59 Exhaust flow path (exhaust duct)
61 Cooling heat exchanger (air cooling part)
61c path group (intermediate flow path)
63 1st air heat exchanger
63c path group (intermediate flow path)
64 2nd air heat exchanger
64c path group (intermediate flow path)
65 Circulation pump (flow rate adjustment mechanism)
66 Branch flow path
68 Duct side heat exchanger (sensible heat exchanger)
71a Inflow part
71b Outflow section
73a Inflow part
73b Outflow part
74a Inflow part
74b Outflow part
95 Evaporator (auxiliary cooling section)
97 Three-way valve (split flow control mechanism)
130 Circulation circuit (refrigerant circuit)
140 Branch duct (bypass pipe)
141 Air flow control valve (Bypass adjustment mechanism)

Claims (10)

A casing (51) that forms an air passage (52) through which air flows and an air cooling section (61, 115) provided in the air passage (52) are used to cool and dehumidify the air by the air cooling section (61, 115). And a dehumidifying system for supplying dehumidified air to the room,
A first air heat exchanger (63) connected to a circulation circuit (60, 130) through which a predetermined heat medium circulates and disposed upstream of the air cooling section (61, 115) in the air passage (52);
A second air heat exchanger connected to the circulation circuit (60, 130) in series with the first air heat exchanger (63) and disposed downstream of the air cooling section (61, 115) in the air passage (52). (64) and the dehumidification system further characterized by the above-mentioned. In claim 1,
The dehumidification system further comprising an air heating section (55) that is disposed downstream of the second air heat exchanger (64) in the air passage (52) and heats the air. In claim 1 or 2,
The first air heat exchanger (63) is located on the downstream side of the air passage (52) and is located on the upstream side of the air passage (52) and an inflow portion (73a) into which the heat medium flows. And an outflow part (73b) through which the heat medium flows out, and an intermediate flow path part (63c) formed between the inflow part (73a) and the outflow part (73b). And dehumidification system. In any one of Claims 1 thru | or 3,
The second air heat exchanger (64) is located on the downstream side of the air passage (52) and is located on the upstream side of the air passage (52) and an inflow portion (74a) into which the heat medium flows. And an outflow portion (74b) through which the heat medium flows out, and an intermediate flow path portion (64c) formed between the inflow portion (74a) and the outflow portion (74b). And dehumidification system. In any one of Claims 1 thru | or 4,
The air cooling section (61, 115) has a heat medium cooling section (25) for cooling a predetermined heat medium, and is connected to a heat medium circuit (41) through which the heat medium circulates. A dehumidification system comprising: In claim 5,
The cooling heat exchanger (61) is located on the downstream side of the air passage (52) and has an inflow portion (71a) into which the heat medium flows, and on the upstream side of the air passage (52). It has an outflow part (71b) through which the medium flows out, and an intermediate flow path part (61c) formed between the inflow part (71a) and the outflow part (71b). Dehumidification system. In any one of Claims 1 thru | or 6,
A branch flow path (66) for diverting the heat medium circulating in the circulation circuit (60, 130) and joining the diverted heat medium to the circulation circuit (60, 130);
An auxiliary cooling part (95) for cooling the heat medium flowing through the branch channel (66),
A dehumidification system further comprising: a partial flow rate adjusting mechanism (97) for adjusting a flow rate of the heat medium flowing through the branch flow path (66). In any one of Claims 1 thru | or 7,
A flow rate adjusting mechanism (35 to 37,65) for individually adjusting the flow rate of the heat medium flowing through the first air heat exchanger (63) and the flow rate of the heat medium flowing through the second air heat exchanger (64). And a dehumidifying system. In any one of claims 1 to 8,
An exhaust passage (59) for exhausting the indoor air to the outside;
The dehumidification system further comprising a sensible heat exchanger (68) for exchanging heat between the heat medium flowing through the circulation circuit (60, 130) and the air flowing through the exhaust passage (59). In any one of Claims 1 thru | or 9,
A bypass passage (140) for bypassing the air upstream of the first air heat exchanger (63) in the air passage (52) to the downstream of the air cooling section (61, 115);
The dehumidification system further comprising a bypass amount adjustment mechanism (141) for adjusting a flow rate of air flowing through the bypass flow path (140).

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