WO2007080979A1

WO2007080979A1 - Dehumidifying air conditioning system

Info

Publication number: WO2007080979A1
Application number: PCT/JP2007/050342
Authority: WO
Inventors: Tatsuo Fujii; Masao Imanari; Minoru Takahashi; Takumi Sugiura; Yasuhiro Kashirajima; Itsushi Fukui
Original assignee: Hitachi Plant Technologies, Ltd.
Priority date: 2006-01-13
Filing date: 2007-01-12
Publication date: 2007-07-19
Also published as: CN101713573A; CN101713573B

Abstract

In a dehumidifying system using a desiccant dehumidifier, regeneration air at the desiccant dehumidifier is heated by the condenser of a heat pump or a gas cooler, indoor return air re-circulated from an air-conditioned indoor to a dehumidifying rotor is cooled by an evaporator. Since the cooling load of indoor return air is almost stable during operations, the size of a heat pump unit is made small as compared with outdoor air cooling by setting the capacity of the heat pump to match this cooling load to thereby reduce initial costs. Furthermore, the heat pump can be operated at an almost maximum capacity throughout operating periods to provide a stabilized energy saving effect.

Description

Specification

Dehumidification air conditioning system

Technical field

TECHNICAL FIELD [0001] The present invention relates to a dehumidifying air conditioning system based on a desiccant air conditioner and provided with a heat pump as its air heating / cooling means.

Background art

[0002] As a dehumidifying air-conditioning system according to the present invention, for example, a technique described in JP-A-2005-34838 can be cited. In this publication, a refrigerant circuit, that is, a heat pump and a desiccant rotor as a moisture absorption and desorption means are provided, the air to be dehumidified is heated by a heat radiator of the heat pump, and the air is humidified in the moisture release area of the desiccant rotor. The air is cooled by the heat pump heat sink and dehumidified in the moisture absorption region of the desiccant rotor. In this publicly known example, the heat pump refrigerant dissipates heat at a supercritical pressure in a radiator, and carbon dioxide is used as the refrigerant.

[0003] In addition, as background technology related to the heat pump cycle used in the present invention, Japanese Examined Patent Publication No. 7-18602 and NEDO 2001 Survey Report 51401011-0-1 Survey on applied equipment using carbon dioxide refrigerant, etc. P 105. In these documents, there is an additional heat exchanger in which the low-pressure refrigerant is evaporated and heated by the heat of the high-pressure refrigerant, that is, a supercritical vapor compression cycle in which an internal heat exchanger is installed to increase the capacity. It is disclosed.

[0004] Further, there is a dehumidifying air conditioning system disclosed in Japanese Patent Laid-Open No. 2005-201624.

In this publication, the dehumidifier is composed of an air supply path and an exhaust path, an adsorbent holding mechanism and a heat pump, and the low temperature heat source and the high temperature heat source of the heat pump are respectively connected to the adsorbent holding mechanism in the air supply path and the exhaust path. It is arranged on the upstream side. Energy is saved by effectively using the low and high temperature heat sources of this heat pump.

[0005] As another conventional technique according to the present invention, a publicly known technique is shown in Fig. 1 of 2005 Air Conditioning 'Sanitary Engineering Society Conference Proceedings PP. 1233-1236. In this known example, energy is saved by introducing a heat pump, and at the same time, the regeneration air for the dehumidifying rotor is used. Then, an auxiliary heater is provided so that the regeneration air is heated by the high-temperature heat source of the heat pump and then further heated by the auxiliary heater to be led to the regeneration zone of the dehumidifying rotor.

[0006] In the prior art disclosed in Japanese Patent Laid-Open No. 2005-34838, since a dehumidifying device used for general air conditioning is targeted, outside air is used as regeneration air heated by a heat pump. However, when a low humidity and low dew point environment is required, a purge zone is provided in the desiccant rotor! /, A so-called purge type desiccant dehumidifier is used. Power used to purge or cool the rotor This air has a higher temperature than the outside air, so heat pump power is not sufficiently dissipated, resulting in lower cooling COP and increased power consumption. .

[0007] Further, in the prior art disclosed in the above Japanese Patent Laid-Open No. 2005-34838, consideration is given to fluctuations in the external air condition in which the air taken from outside is heated using the heat radiating part of the heat pump to regenerate the desiccant rotor. Therefore, the regeneration temperature and the humidity of the supplied air vary greatly depending on the season, and the distribution of heating and cooling heat is determined by the heat pump site, making it difficult to respond to fluctuations in the outside air. There were challenges. In addition, since the regeneration air is heated only by the heat radiating part of the heat pump, there is a problem that the dehumidifying ability with which the upper limit of the regeneration air temperature is low is limited to this.

[0008] Further, according to the prior art disclosed in the above Japanese Patent Application Laid-Open No. 2005-34838, the global warming potential is small as the refrigerant of the heat pump, carbon dioxide is used, and the regeneration air is heated at supercritical pressure. When high-temperature heating of regeneration air is performed using carbon dioxide as a heat pump refrigerant, it is necessary to compress the refrigerant to a high pressure in the compressor in order to obtain a high temperature. However, the above-mentioned prior art does not give consideration to this point when there is a decrease in the energy consumption and the capacity of the heat pump device increases.

[0009] The NEDO 2001 survey report 51401011-0-1 described above improves the heat insulation efficiency of the compressor and reduces the energy consumption caused by the reduction of the compression ratio. It does not mention that the installation of the exchanger plays a major role.

[0010] Further, in the prior art disclosed in JP 2005-201624, the same refrigeration cycle is used. Cooling of supply air taken into the air supply path from outside, such as outdoors, and heating to use exhaust air (regeneration air) taken into the exhaust path from indoors for regeneration of the adsorbent. On the other hand, the cooling heat quantity of the supply air changes greatly depending on the time fluctuation and seasonal fluctuation of the outside air temperature. For this reason, if the heat pump cycle is operated in accordance with this change, the amount of heating of the exhaust air also fluctuates, and the regeneration state of the adsorbent and further the dehumidification performance of the supply air performed by this adsorbent fluctuate. was there. Furthermore, as described above, the operating state of the heat pump largely fluctuates depending on the cooling load with respect to the outside air condition, and the conditions under which the heat pump equipment operates effectively are limited to the state where the cooling load is large. There was a problem.

[0011] In addition, in order to compensate for fluctuations in the heating amount of the exhaust air, when an auxiliary heater using electricity is provided to reheat the exhaust air, the load on the auxiliary heater increases due to fluctuations in the operating state of the heat pump. As a result, the problem of increased energy consumption arises.

In response to these issues, in the 2005 Air Conditioning Sanitation Engineering Society Conference Proceedings, the regeneration air heated by the high-temperature heat source of the heat pump and then further heated by the auxiliary heater, the regeneration supplied to the regeneration zone Stabilize the air temperature to stabilize the adsorbent regeneration and dehumidification performance of the supply air! / Speak.

[0012] For fluctuations in the cooling load, a sensible heat rotor is provided to exchange heat between the air exhausted from the room and the supply air dehumidified by the dehumidifying rotor and having a temperature increased to about 65 ° C. The structure of cooling the supply air heat-exchanged with indoor air using a heat rotor with a low-temperature heat source of the heat pump suppresses the influence of fluctuations in the outside air, enabling the heat pump equipment to be effective regardless of time fluctuations and seasonal fluctuations in the outside air conditions. Is in operation. However, this conventional technology requires a sensible heat rotor, which increases the size of the dehumidification system.

Disclosure of the invention

[0013] An object of the present invention is to supply a stable low-humidity air to a desiccant dehumidification system using a heat pump, regardless of fluctuations in the outside air conditions, and at the same time to operate the heat pump stably to save energy and dehumidify. This is to suppress the increase in size of the system device. Another object of the present invention is to provide a heat pump in which the refrigerant of the heat radiating section using superoxide pressure such as carbon dioxide and carbon dioxide as a refrigerant is used for heating and cooling the air. The purpose is to improve the heat insulation efficiency of the compressor by reducing the refrigerant pressure and compression ratio, and to reduce the power consumption of the dehumidifying air conditioning system.

[0014] In order to achieve the above object, the dehumidifying air conditioning system according to the present invention uses a heat pump for heating the regenerative air and cooling the supply air, and in addition to a heat radiator for heating the regenerative air in this heat pump cycle. Thus, a heat dissipating means for cooling the high-pressure side refrigerant by an external cooling medium is provided.

[0015] In addition, the indoor air that is recirculated through the outside air introduced from the outside and the air-conditioned room that is treated with the treated air is used as the mixed air of the indoor return air, and the air cooler that uses the heat absorption part of the heat pump as the cooling source is recirculated. It is provided in the return air flow path.

[0016] According to the dehumidifying air conditioning system described above, the regeneration air is heated using the heat pump. Therefore, the power consumption is reduced as compared with the case where heating is performed using only the electric heater. As efficiency increases, power consumption can be further reduced. In addition, since the indoor return air is cooled by the heat pump's heat absorption part, when performing dehumidification air conditioning in offices, factory production sites, clean rooms, etc. that generate cooling loads throughout the year, a nearly stable cooling load can be obtained throughout the year. As a result, it is possible to operate the heat pump equipment effectively and to obtain an energy saving effect according to its capacity.

Brief Description of Drawings

FIG. 1 is an overall system diagram of a dehumidifying air conditioning system according to one embodiment of the present invention.

2 is a Th diagram of the heat pump cycle in the embodiment of FIG.

FIG. 3 is a graph showing energy consumption of the dehumidifying air conditioning system in the embodiment of FIG.

FIG. 4 is an overall system diagram of a dehumidifying air conditioning system according to another embodiment of the present invention.

FIG. 5 is a Th diagram of the heat pump cycle in the embodiment of FIG.

[Figure 6] The power consumption of the dehumidifying air conditioning system and the compression ratio of the compressor in the embodiment of FIG.

It is the graph shown by the relationship with the temperature efficiency of an internal heat exchanger.

FIG. 7 is a graph showing energy consumption of the dehumidifying air conditioning system in the embodiment of FIG. 4. FIG. 8 is an overall system diagram of the dehumidifying air conditioning system according to another embodiment of the present invention. FIG. 9 is a Th diagram of the heat pump cycle in the embodiment of FIG.

FIG. 10 is a diagram showing a unit configuration in the embodiment of FIG.

FIG. 11 is a graph showing power consumption of the dehumidifying air conditioning system in the embodiment of FIG.

FIG. 12 is a graph showing annual fluctuations in power consumption of the dehumidifying air conditioning system in the embodiment of FIG.

FIG. 13 is an overall system diagram of a dehumidifying air conditioning system according to another embodiment of the present invention.

BEST MODE FOR CARRYING OUT THE INVENTION

Example 1 will be described with reference to FIG. 1, FIG. 2, and FIG. FIG. 1 is an overall system diagram of the dehumidifying air conditioning system according to the present embodiment. FIG. 2 is a diagram showing the heat pump cycle used in this example on a temperature-enthalpy diagram. Fig. 3 is a graph comparing the energy consumption and breakdown of the dehumidifying air conditioning system according to this example with a similar system.

As shown in FIG. 1, a dehumidifying air conditioning system includes a desiccant rotor (hereinafter referred to as a dehumidifying rotor) 10, a heat pump 30, an electric heater 70, a refrigerator 80, and a duct through which treated air and desiccant regenerated air are passed. And power such as fans is also configured.

[0020] The dehumidifying rotor 10 includes a processing zone 11 that adsorbs moisture from the processing air to dehumidify, a regeneration zone 12 that desorbs moisture from the rotor with high-temperature regeneration air, and a rotor whose temperature has increased in the regeneration zone. Then, dehumidification is performed by sequentially rotating the purge zone 13 for branching and cooling a part of the processing air. The dehumidifying rotor 10 holds a dehumidifying member such as silica gel zeolite.

[0021] The heat pump 30 heats the rotor regeneration air 95 using a compressor 31 that compresses the refrigerant gas to a supercritical state and raises the temperature, and a refrigerant that is compressed to a supercritical pressure by the compressor 31 and reaches a high temperature. Air heater 32, the outside air radiator 33 that further cools the refrigerant whose temperature has been lowered by the air heater 32 with the outside air for heat dissipation 99, and the refrigerant that exits the outside air heater 33 is reduced from the supercritical state to the two-phase region. The pressure reducing valve 34, the air coolers 35 and 36 for cooling the processing air, that is, the indoor return air 94 from the low dew point room (not shown) and the introduced outside air by evaporating the refrigerant liquid of the two-phase refrigerant and the like. Power is also configured, such as the connecting refrigerant pipe 37.

[0022] Further, in each part of the duct, a temperature sensor 39 for controlling the capacity of the heat pump 30, and A temperature sensor 79 for detecting the temperature of the rotor regeneration air 95 for controlling the electric heater 70, and a direct expansion type cooling coil provided in the refrigerator 80 for operation control including on / off of the refrigerator 80 A temperature sensor 89 for measuring the temperature of the introduced outside air 91 after passing through 81 is provided. That is, the refrigerator 80 and the direct expansion type cooling coil 81 constitute auxiliary cooling means for precooling the introduced outside air (process air).

Next, the basic operation of the dehumidifying air conditioning system according to the present embodiment will be described. In the dehumidifying air conditioning system, the outside air 91 introduced for supplying air is first preliminarily cooled by the direct expansion type cooling coil 81 provided in the refrigerator 80. Further, after the precooled outside air is cooled by the air cooler 36 of the heat pump 30, the return air 94 from the low dew point chamber is joined with the air cooled by the air cooler 35 of the heat pump 30. This merged air is partly branched and guided to purge zone 13 as purge air 92, and the rest is guided to treatment zone 11 to reduce humidity and not shown as supply air! Led.

On the other hand, the purge air 92 cools the dehumidifying rotor 10 in the purge zone 13. As a result, as is well known as a feature of the purge-type desiccant dehumidifier, air is supplied only from a sufficiently cooled region, and as a result, air supply with very low humidity can be obtained. Dehumidification The purge air 92 whose temperature has been increased by cooling the rotor 10 joins with the recirculation regenerated air 96 to become regenerated air, and is further heated in turn by the air heater 32 and the electric heater 70 of the heat pump 30 and then the regeneration zone 12 Regeneration, that is, desorption / removal of moisture from the dehumidifying rotor 10 is conducted.

[0025] A part of the regeneration air 95 from the regeneration zone 12 is branched as described above to join the purge air 92 as the recirculation regeneration air 96, and the rest is exhausted together with the water removed from the dehumidification rotor 10 97. Is discharged outside the machine.

Next, the operation of the heat pump 30 at this time will be described with reference to FIG. In this embodiment, carbon dioxide is used as the working medium of the heat pump 30. Symbols A to F in FIG. 2 indicate the state of the refrigerant on the temperature-enthalpy diagram shown in FIG. Represents a saturation line.

[0027] The refrigerant compressed to the supercritical pressure by the compressor 31 rises in temperature to state A, and is guided to the air calorie heater 32. In the air heater 32, the regenerative air 97 is discharged as the refrigerant drops in temperature. Heated to state B and led to outside air radiator 33. In the outside air radiator 33, since the introduced outside air 99 for heat dissipation has a temperature lower than that of the regenerated air flowing into the air heater 32, the refrigerant further falls in temperature and enters the state C. After that, the refrigerant is led to the expansion valve 34 and depressurized to become a state D which is a two-phase state consisting of the refrigerant liquid and the refrigerant vapor force. In the air coolers 35 and 36, the refrigerant returns to the room by the latent heat of vaporization of the refrigerant liquid. The air 94 and the introduced outside air 91 are cooled. In the air cooler 36, all the refrigerant liquid evaporates to become a state E on the saturation line, and further becomes a superheated steam state F by heat exchange with the outside air 91, and then is sucked into the compressor 31 and compressed again. Is done.

[0028] In reality, there is a pressure loss in each heat exchanger, but in Fig. 2, the influence is omitted, and states A, B, and C are shown on the isobaric line in the supercritical region, and states D, E, F is shown on the isobaric lines of the two-phase region and gas region.

Next, operation control of the dehumidifying air conditioning system according to the present embodiment will be described. In the present embodiment, the heat pump 30 has an upper limit of capacity and refrigerant circulation amount based on the maximum amount of heat that can be recovered by the regenerated air 95 in the air heater 32. Therefore, it is considered that the cooling capacity is insufficient when the outside air temperature is high, and the refrigerator 80 is installed in preparation for this. The refrigerator 80 is controlled based on the output of a temperature sensor 89 that measures the temperature of the outside air cooled by the refrigerator 80.

[0030] When the outside air temperature is high, the refrigerator 80 is controlled so that the air temperature measured by the temperature sensor 89 becomes a substantially constant value. This air temperature value is determined in accordance with the cooling capacity of the heat pump 30 in an operation state in which the heat pump 30 can supply the maximum amount of heat that can be recovered by the regenerative air 95 in the air heater 32. .

When the outside air temperature is low, the cooling load is reduced, and the operation of the refrigerator 80 is stopped because the outside air 91 and the indoor return air 94 can be sufficiently cooled only by the cooling capacity of the heat pump 30. In this case, it is not preferable to stop the operation of the heat pump 30 because the heating amount of the air heater 32 becomes zero and the power consumption of the electric heater 70 increases. In the present embodiment, when the air temperature measured by the temperature sensor 89 becomes lower than a predetermined value, the operation of the refrigerator 80 is stopped, and the air temperature rises again to maintain the predetermined operating gap at the predetermined value. When the value exceeds (hysteresis), the operation of the refrigerator 80 is resumed. The heat pump 30 is controlled based on the output of the temperature sensor 39 that measures the temperature of the processing air after the indoor return air 94 and the outside air 91 that have been cooled by the air coolers 35 and 36 are mixed. At this time, the temperature of the indoor return air 94 at the inlet of the air cooler 35 is substantially constant, and the temperature of the outside air 91 at the inlet of the air cooler 36 is maintained below a certain temperature by the refrigerator 80 as described above. Therefore, the temperature of the processing air measured by the temperature sensor 39 is controlled to a substantially constant value within the capacity control range of the heat pump 30. This value is determined from the specifications of the supply air supplied from the dehumidification air conditioning system to the low dew point room.

[0032] In the state where the refrigerator 80 whose outside air temperature is low is stopped by the control operation, the volume of the heat pump 30 is controlled as described above to maintain the temperature of the mixed air substantially constant. Thus, the air heating amount in the air heater 32 also changes. For this change, the amount of heating by the electric heater 70 is controlled based on the output of the temperature sensor 79 that detects the temperature of the regenerating air 95 from the electric heater 70 toward the regeneration zone 12 of the dehumidifying rotor 10. The dehumidifying capacity in the treatment zone 11 is maintained by maintaining the temperature of the tank at a predetermined value.

[0033] As described above, in this embodiment, the heat absorption part of the heat pump cycle, that is, the evaporator, is used as the cooling source for the processing air, and the heat radiation part is used as the heating source for the regeneration air 95, thereby reducing the load on the electric heater 70. Reduce energy consumption through actions such as reducing! In addition, by providing the outside air radiator 33, after the carbon dioxide as a refrigerant heats the regenerative air 95 at the heat radiating part of the heat pump cycle to become the state B, the outside air for heat radiation 99 is further cleaned. Dissipates heat and the temperature drops to state C. In other words, the cooling capacity of the air coolers 35 and 36 is QE, which is the enthalpy difference between state D and state F in FIG. Compared to the case where the outside air radiator 33 is not used, this cooling capacity is reduced from the state B to the state D ′ when the outside air radiator 33 is used, and the cooling capacity is changed to the state D′—state. QE, which is the enthalpy difference between F. Therefore, it can be seen that the installation of the outside air radiator 33 increases the cooling capacity per unit coolant flow rate by (QE—QE ′), and the electric energy input to the compressor 31 is reduced. Alternatively, the increase in the cooling capacity reduces the cooling load of the precooling refrigerator 80, and energy saving of the entire dehumidifying air conditioning system can be achieved. In this embodiment, the temperature of the air flowing into the processing zone 11 of the dehumidifying rotor 10 is controlled by controlling the capacity of the heat pump 30 based on the temperature of the processing air cooled by the air coolers 35 and 36. As a result, low dew point air can be supplied stably.

In this embodiment, since the electric heater 70 is provided, the regeneration air 95 can be heated to a temperature higher than the highest temperature that can be heated by the heat pump. As a result, the moisture of the dehumidifying member is reduced during the regeneration of the rotor, so that it is possible to supply low dew point air such as 50 ° C. Further, a temperature sensor 79 for detecting the temperature of the regeneration air 95 heated by the electric heater 70 is provided, and the heating amount of the electric heater 70 is controlled so that the temperature of the regeneration air 95 becomes a constant value. As a result, even when the operating state of the heat pump 30 changes, it is possible to stabilize the temperature of the regenerative air to secure the dehumidifying capacity in the treatment zone 11 and to supply the low dew point air stably. .

In the present embodiment, a refrigerator 80 for auxiliary cooling of the introduced outside air 91 is installed to make up for the lack of cooling capacity by the heat pump 30. Therefore, the cycle capacity of the heat pump 30 can be set in accordance with the amount of heat in the air heater 32, that is, the amount of heat that can be recovered when the temperature of the regeneration air 95 rises. Therefore, there is an effect that it is possible to prevent a decrease in energy use efficiency due to an excessive heating capacity of the heat pump 30 in the heat radiating portion.

[0037] This effect will be described with reference to FIG. Fig. 3 compares the energy required for air heating and cooling in the dehumidifying air conditioning system according to this example with other methods. Each method (1) to (3) has the following configuration. In the configuration (1), the regeneration air 95 in the dehumidification system is all heated by the electric heater 70, and the processing air is all cooled by the refrigerator 80, and the heat pump 30 is not used. Next, in the configuration (2), the cooling of the processing air is all performed by the evaporator of the heat pump 30 !, the regeneration air 95 is heated by the heat discharge part of the heat pump 30 and the electric heater 70, and the refrigerator 80 is not used. Is the case.

[0038] Configuration (3) is the configuration of the present embodiment, in which the heat pump 30 and the electric heater 70 are used for heating the regeneration air, and the heat pump 30 and the refrigerator 80 are used for cooling the processing air as described above. It should be noted that the heat pump used in configuration (2) has an outside air cooler 33 installed. And within the scope of the present invention.

[0039] In Fig. 3, the total energy consumption in configuration (1) is 100%, and the energy consumption in each configuration is classified and compared for each component device. In the comparison between (1) and (2), the energy required for cooling the processing air is greatly increased in the heat pump in (2) compared to the refrigerator in (1). This is because the refrigerant used in the heat pump 30 is a low-theoretical coefficient of performance and is carbon dioxide, whereas the refrigerant is an alternative fluorocarbon refrigerant.

[0040] However, in (2), the energy consumption of the electric heater 70 is smaller as shown in the figure due to the heating of the regenerated air 95 by the heat pump 30. As a result, the energy consumption is lower than in (1). Has been reduced. This indicates that even when the refrigerator 80 is not used, energy can be saved by adopting the heat pump 30 provided with the outside air cooler 33.

[0041] Next, in the comparison between (2) and (3), the power consumption of the heat pump 30 is reduced because the capacity of the heat pump 30 is set according to the amount of heat that can be recovered by the regenerated air 95. Instead, the power consumption of the refrigerator 80 that supplements the cooling heat of the processing air that has become insufficient is generated. The difference between (2) and (3) arises because the electric heater 70 is used for the purpose of heating the regeneration air 95 from the maximum temperature that can be heated by the heat pump 30 to a higher temperature. Not in.

[0042] In the comparison of total energy consumption, (3), which is the configuration of the present example, is further reduced from (2). This is because, in (2), the capacity of the heat pump 30 is set according to the cooling load, so the heating capacity becomes excessive, the loss due to releasing that energy to the outside air, and part of the air cooling. By using a refrigerator 80 with a high coefficient. When the cooling load of the refrigerator 80 is increased in configuration (3) and the capacity of the heat pump 30 is decreased, the energy consumption increases because the system configuration approaches (1).

[0043] Further, since the refrigerator 80 is installed, it is possible to cope with the load fluctuation of the outside air cooling due to the season by controlling the capacity of the refrigerator 80, so that the load of the heat pump 30 is stabilized and the air heater 32 There is an advantage that the heating amount can be secured. For example, when the outside air temperature is low and the cooling load is small, this can be dealt with by turning off the refrigerator 80. [0044] In addition, the start and stop and capacity control of the refrigerator 80 are performed based on the detected value of the temperature of the outside air 91 (the detected value of the temperature sensor 89) from the cooling coil 81 to the air cooler 36, and the outside air cooling load is controlled. Of these, only the amount exceeding the maximum capacity of the heat pump 30 is covered by the refrigerator 80, thereby ensuring the maximum operating capacity of the heat pump 30 and maximizing the amount of heating in the air heater 32, and the input of the electric heater 70. By reducing this, it is possible to achieve the energy saving effect shown in Fig. 3.

[0045] In this embodiment, the desiccant dehumidifier used in the dehumidification system is a purge type. 1S The same applies to a standard type desiccant dehumidifier having no purge zone as seen in JP 2005-34838 A. The effect is obtained. That is, the heat pump heat release part is not limited to the air heater introduced as process air as disclosed in JP-A-2005-34838, but the cooling air is introduced and the refrigerant after heating the process air is used. In addition, by installing an outside air radiator that lowers the temperature, the cooling capacity can be increased and the energy of the entire system can be saved.

[Example 2]

Next, another embodiment of the present invention will be described with reference to FIGS. Fig. 4 is an overall system diagram of the dehumidifying air-conditioning system according to this example, Fig. 5 is a diagram showing the heat pump cycle used in this example on the temperature-enthalpy diagram, and Fig. 6 is the internal heat used in this example. Figure 7 shows the relationship between the temperature efficiency of the exchanger and the power consumption of the dehumidifying air-conditioning system according to this example. Figure 7 shows the energy consumption and its breakdown of the dehumidifying air-conditioning system according to this example. It is the graph compared with the system of. In each figure, the same components as those in the embodiment of FIG. 1 are denoted by the same reference numerals as in FIG. In the following description, only the differences between the present embodiment and the embodiment of FIG. 1 will be described.

As shown in FIG. 4, the dehumidifying air-conditioning system according to the present embodiment is different from the embodiment of FIG. 1 in that the heat pump 30 is provided without providing the refrigerator 80, the cooling coil 81 attached thereto, and the temperature sensor 89. In this cycle, an internal heat exchanger 38 for exchanging heat between the refrigerant in the supercritical state cooled by the outside air radiator 33 and the refrigerant cooled to the outside air by the air cooler 36 is provided. It is a configuration. The pressure reducing valve 34 is provided on the downstream side of the internal heat exchange. [0048] In the dehumidifying air conditioning system of the present embodiment, the outside air 91 introduced for supply of air is directly cooled by the air cooler 36 and joined with the indoor return air 94 cooled by the air cooler 35. As in the embodiment of FIG. 1, part of the air is purged air 92 and the rest is dehumidified by the dehumidifying rotor 10 to become air supply 93. The system of purge air 92 and regeneration air 95 is the same as that of the embodiment of FIG.

[0049] The operation of the heat pump 30 in the present embodiment is indicated by a thick line (4) in FIG. Symbols P to W represent the state of the refrigerant in the same manner as symbols A to F in FIG. The refrigerant whose pressure has been increased to the supercritical pressure by the compressor 31 rises to the state P, passes through the air heater 32 and the outside air radiator 33, and then enters the state R, and then enters the air cooler 36 in the internal heat exchanger 38. Then, heat is applied to the refrigerant vapor toward the compressor 31 and the state S is reached. Then, it enters the two-phase state T through the expansion valve 34, becomes saturated steam U and superheated steam V in the air coolers 35 and 36, and then further heats in the internal heat exchanger 38 and rises in temperature. After reaching W, the air is sucked into the suction side of the compressor 31.

[0050] When the heat pump cycle in this example is compared with the site of the example of Fig. 1 indicated by the dotted line in Fig. 5, the refrigerant changes from state R to state S in the internal heat exchange after heat is radiated by the external air radiator 33. The cooling capacity per unit amount of refrigerant in the air coolers 35 and 36 is also increased to QE "as shown in the figure. This effect is mainly due to the use of carbon dioxide as a cooling medium. This is generally known as an increase in the refrigeration effect due to internal heat exchange in the refrigeration cycle.

Furthermore, in the present embodiment, the refrigerant vapor led to the compressor 31 is heated by the internal heat exchange 38 and the temperature rises. Here, when the discharge pressure of the compressor is the same as that in the embodiment of FIG. 1, the discharge temperature of the compressor rises.In this embodiment, however, the discharge temperature is set as shown in FIG. 1 by setting the discharge pressure of the compressor low. It is the same as the embodiment. Therefore, the compression ratio of the compressor 31 is smaller than that of the embodiment of FIG. Here, since it is generally better for the compressor to have a small compression ratio, in this embodiment, the efficiency of the compressor increases due to a decrease in the discharge pressure and the pressure ratio, and the power consumption is further reduced. Next, these relationships will be described with reference to FIG.

[0052] In FIG. 6, the horizontal axis is the temperature efficiency ε of the internal heat exchanger 38, the vertical axis is the power consumption, the ratio of the compression ratio, and the compressor efficiency that varies with the compression ratio, and the discharge temperature of the compressor 31 is As a constant value These relationships are shown. The point of temperature efficiency ε = 0 represents the same configuration as (2) in Fig. 3 when the internal heat exchanger 38 is not installed in Fig. 4, that is, the heat pump cycle is shown in Fig. 1 on the Th diagram. Similar to the previous example, the cycle indicated by the broken line in FIG. 2 or FIG. The internal heat exchange 38 of the heat pump 30 in this embodiment operates at the temperature efficiency indicated by (4) on the horizontal axis during rated operation.

[0053] First, considering only the increase in the refrigeration effect, that is, the compressor efficiency is a constant value, the result of calculating the power consumption of the entire dehumidifying air conditioning system is indicated by a thin line. When the temperature efficiency of the internal heat exchanger increases, the work of the compressor is reduced due to the effect of increasing the cooling capacity per unit refrigerant volume, reducing the overall power consumption of the system! /

Next, the change in the compression ratio at this time is indicated by a broken line. As the temperature efficiency ε increased and the compressor inlet temperature increased, the discharge pressure was determined so that the discharge temperature was constant, and as a result, the discharge pressure and compression ratio were as shown in Fig. 6. It is falling. The result of deriving the compressor efficiency η from this compression ratio is shown by the dotted line in Fig. 6. The relationship between the compression ratio and the compressor efficiency is shown, for example, in the formula (5.1-4) on page 106 of the NEDD 2001 Survey Report. As shown in the figure, the compressor efficiency increases as the temperature efficiency of the internal heat exchanger 38 increases.

[0055] Figure 6 shows the results of recalculating the power consumption of the entire dehumidifying air conditioning system in consideration of this increase in compressor efficiency. By installing the internal heat exchanger 38, the compressor efficiency is increased, and the power consumption is further reduced compared to the power consumption reduction effect due to the increased cooling capacity shown by the thin line. In the operating condition (4) of this embodiment, a power consumption reduction effect of about 15% is obtained compared to the case without internal heat exchange.

FIG. 7 shows a comparison of the energy required for heating and cooling the air by the dehumidifying air conditioning system according to the present embodiment with the three types of systems compared in FIG. It can be seen that the power consumption is further reduced with respect to the embodiment shown in FIG.

[0057] As described above, in this embodiment, the internal heat exchanger 38 is added to the heat pump 30, so that in addition to the generally known effect of increasing the cooling capacity, the compressor efficiency can be improved by reducing the compression ratio. The improvement and the reduction effect of the power consumption accompanying this are acquired. That is, Figure 1 Although the compressor discharge pressure and compression ratio are lower than those of this example, the same compressor discharge temperature can be obtained.This is a major feature of this example, and the heat pump cycle is applied to the dehumidifying air conditioning system. This is a unique effect that occurs when

[0058] Although the refrigerator 80 is not used in this embodiment, the internal heat exchanger 38 may be added to the heat pump of the dehumidification air conditioning system using the refrigerator 80 as in the embodiment of FIG. It is clear that a similar effect can be obtained. Further, when the refrigerator 80 is not used as in the present embodiment, the system is simplified, and the refrigerant of the heat pump 30 is made of carbon dioxide and carbon dioxide, so that alternative CFCs with a high global warming potential can be used. It is not necessary to use a refrigerant, and it is possible to obtain a dehumidifying air conditioning system that is extremely advantageous in terms of environmental conservation in combination with the effect of reducing energy consumption.

[0059] In each of the embodiments described above, the refrigerant of the heat pump 30 dissipates heat at the supercritical pressure in the air heater 32, so that the regeneration air 95 can be heated to a high temperature. As shown in the comparison of the configuration (1) in Fig. 3 or Fig. 7 with the implementation of the present invention (2) (3) (4), the power consumption of the electric heater 70 is reduced and the energy saving effect of the entire dehumidification air conditioning system is reduced. Is obtained!

[0060] Further, in each of the above-described embodiments, as the refrigerant of the heat pump 30, carbon dioxide with a relatively low critical temperature of 31.1 ° C is used, so that the high pressure side of the cycle is easily supercritical. Thus, the supercritical heat dissipation effect is obtained. Also, as is well known, carbon dioxide has a very low global warming potential, so it is possible to obtain a dehumidifying air conditioning system that addresses environmental problems that do not require refrigerant recovery.

Further, in each of the embodiments described above, the outside air radiator 33 is installed as a cooling means for the refrigerant after exiting the air heater 32 and is cooled by the outside air 99 for heat radiation. There is an advantage that no system facilities are required.

[0062] On the other hand, when introducing this system in a factory or the like where the cooling water system has been prepared in advance, a configuration in which a water-cooled refrigerant cooler is installed instead of the outside air radiator 33 and the cooling water is cooled. Also good. In this case, instead of requiring a cooling water system, cooling can be performed with a smaller heat transfer area compared to the air-cooled outside air radiator 33, so there is an advantage that the refrigerant cooler and the dehumidifying air conditioning system can be downsized. is there. This cooling water is river water or seawater. It is clear that it may be.

[Example 3]

A third embodiment will be described with reference to FIGS. FIG. 8 is an overall system diagram of the dehumidifying air conditioning system according to the present embodiment. FIG. 9 is a diagram showing the heat pump cycle used in this example on the temperature-enthalpy diagram. FIG. 10 is a diagram showing the unit configuration of the present embodiment. FIG. 11 is a graph comparing the energy consumption and the breakdown of the dehumidifying air-conditioning system according to the present embodiment under the summer peak conditions without using a heat pump. Also, FIG. 12 is a graph comparing the monthly average energy consumption according to this example with the case without using a heat pump as in FIG.

FIG. 8 differs from FIG. 1 in that a direct expansion type cooling coil (first cooling coil) 81, which is the output of the refrigerator 80, is provided with an on-off valve 83 and a direct cooling system for cooling the indoor return air 94. An expansion cooling coil (second cooling coil) 82 and an on-off valve 84 are provided. Further, the air cooler 36 connected to the heat pump 30 is not provided, and the indoor atmosphere 94 that has passed through the air cooler 35 is further cooled by the refrigerator 80 and supplied to the dehumidifying rotor 10 together with the outside air 91. Yes. Furthermore, instead of providing the temperature sensor 89, the temperature sensor 39 is also used for controlling the refrigerator. Other configurations are the same as those in FIG.

[0065] Therefore, the basic operation of the dehumidifying air conditioning system according to the present embodiment will be described. In the dehumidifying air conditioning system, the introduced outside air 91 (process air) is cooled by the first cooling coil 81 provided in the refrigerator 80, and the indoor return air 94 from the low dew point room is cooled by the air cooler 35 of the heat pump 30 and It cools with the 2nd cooling coil 82 of the refrigerator 80, and joins these. As described above, a part of the combined processing air is branched and guided to the purge zone 13 as purge air 92, and the rest is guided to the processing zone 11 to reduce the humidity, and then the air is supplied as air supply 93. Led to. On-off valve 83 (solenoid valve) for controlling the refrigerant in the middle of the piping from the refrigerator 80 to the first cooling coil 81 1S Similarly on-off valve in the middle of the piping from the refrigerator 80 to the second cooling coil 82 84 (solenoid valve) is provided.

On the other hand, the purge air 92 cools the dehumidifying rotor 10 in the purge zone 13. As a result, as is well known as a feature of the purge-type desiccant dehumidifier, power is supplied only in a sufficiently cooled region, and as a result, air supply with very low humidity can be obtained. Removal The purge air 92 whose temperature has been increased by cooling the wet rotor 10 is merged with the recirculation regenerated air 96 to become regenerated air, which is further heated by the air heater 32 of the heat pump 30 and the electric heater 70 in order, and then the regeneration zone 12 Regeneration, that is, desorption / removal of moisture from the dehumidifying rotor 10 is conducted.

[0067] The regeneration air 95 from the regeneration zone 12 partially diverges as described above and merges with the purge air 92 as the recirculation regeneration air 96, and the rest is exhausted together with the water removed from the dehumidification rotor 97. Is discharged outside the machine.

Next, the operation of the heat pump 30 at this time will be described with reference to FIG. In this embodiment, carbon dioxide is used as the working medium of the heat pump 30. Symbols A to F in FIG. 9 indicate the state of the refrigerant on the temperature-enthalpy diagram shown in FIG. 9, and the curve H is the saturation line. It expresses and expresses.

[0069] The refrigerant compressed to the supercritical pressure by the compressor 31 rises in temperature to state A and is guided to the air-caloric heater 32. In the air heater 32, the regenerative air 95 is heated to the state B while the refrigerant drops in temperature, so that the refrigerant enters the state B and is led to the outside air radiator 33. In the outside air radiator 33, the introduced outside air 99 for heat dissipation has a lower temperature than the regenerative air 95 flowing into the air heater 32, so that the temperature of the cooling medium further drops to state C. Thereafter, the refrigerant is led to the expansion valve 34 to reduce the pressure, and the refrigerant enters the state D in which the refrigerant liquid and the refrigerant vapor force are in the two-phase state D. Cool 94. In the air cooler 35, all the refrigerant liquid evaporates to a state E on the saturation line, and further becomes a superheated steam state F by heat exchange with the indoor return air 94, and then is sucked into the compressor 31 and compressed again. Is done.

[0070] Actually, there is pressure loss in each heat exchanger, but in Fig. 9, the influence is omitted, and states A, B, and C are shown on the isobaric lines in the supercritical region, and states D, E, F is shown on the isobaric lines of the two-phase region and gas region.

FIG. 10 shows the unit configuration of the dehumidifying air conditioning system in this embodiment and the installation status of each component of the heat pump cycle. The dehumidifying air conditioning system is mainly composed of a heat exhausting unit 101 and a dehumidifying unit 102. The exhaust heat unit 101 includes a compressor 31, an outside air radiator 33, a fan 38 that allows the outside air radiator 33 to vent the outside air, an expansion valve 34, and the like. [0072] The dehumidifier unit 102 is provided with an air heater 32 and an air cooler 35 among the components of the heat pump cycle. Although not shown in FIG. 10, the dehumidifying rotor 10, the electric heater 70, the first cooling coil 81 and the second cooling coil 82 of the refrigerator 80 shown in FIG. Duct, fan, etc. are built in the dehumidifier unit 102. The refrigerant pipe 37 forming the heat pump cycle connects the exhaust heat unit 101 and the dehumidifier unit 102.

[0073] Next, the operation control of the dehumidifying air conditioning system of the present embodiment will be described. For changes in the outside air temperature, the temperature of the processing air supplied to the processing zone 11 of the dehumidification rotor 10 is maintained substantially constant by controlling the capacity of the refrigerator 80. This treated air is a mixture of air obtained by cooling the outside air 91 using the first cooling coil 81 and air obtained by cooling the indoor return air 94 using the air cooler 35 of the heat pump 30 and the second cooling coil 82 of the refrigerator 80. Is. Therefore, even when the cooling load in the air-conditioned room or the temperature of the indoor return air 94 changes, the capacity control of the refrigerator 80 can cope with it.

[0074] Furthermore, even when the outside air temperature fluctuates and the refrigerant outlet temperature of the outside air radiator 33 changes, and the influence causes the cooling heat amount of the air cooler 35 and the outlet temperature of the indoor return air 94 to fluctuate. The capacity of the refrigerator 80 can be controlled. Further, the heating amount of the regeneration air 95 in the air heater 32 changes with the change of the heat pump cycle. This change is dealt with by keeping the regenerated air temperature measured by the temperature sensor 79 constant by controlling the capacity of the electric heater 70.

[0075] Accordingly, the influence of fluctuations in the outside air temperature and the indoor load on the heat pump cycle is small, and the heat pump is operated at a substantially constant output during operation of this system. The capacity of the heat pump is set so that the cooling capacity of the indoor return air 94 determined by the set temperature of the air-conditioned room set at the time of planning is lower than the cooling capacity of the air cooler 35.

Next, FIG. 11 and FIG. 12 will be described with respect to the energy saving effect according to the present embodiment. Fig. 11 shows the calculation results of the power consumption of the dehumidifying air conditioning system in the summer peak period when the heat pump 30 is not used (the heat pump is not used), that is, the outside air 91 and the indoor return air 94 are cooled only by the refrigerator 80. This compares the case where the regeneration air 95 is heated only by the electric heater 70 and the case where the heat pump 30 is used. As shown in Figure 11, Power consumption is reduced by about 10%.

[0077] Fig. 12 shows the result of calculating the power consumption for each month of the year using the monthly average temperature in a certain region. The comparison at summer peak shown in Fig. 11 is also shown in Fig. 12. As shown in Fig. 12, almost constant reduction in power consumption is obtained regardless of the season. This is because the heating and cooling loads by the heat pump are almost constant throughout the year, so that the heat pump can always be operated at its rated capacity.

[0078] As described above, in this embodiment, since the air cooler 35 of the heat pump 30 is provided in the flow path of the indoor return air 94 having a cooling load throughout the year, the annual operation state of the heat pump is stabilized, As shown in Fig. 12, energy saving effects can be obtained throughout the year. In this example, the amount of power consumption reduction shown in Fig. 11 was obtained throughout the year, and the total power consumption value decreased in the middle and winter seasons, so the reduction rate exceeded 10%. As a result, the annual power consumption reduction rate is also over 10%.

[0079] Further, according to the present embodiment, the capacity of the heat pump 30 is set by a value that does not exceed the cooling load of the indoor return air, so that the scale of the device is zJ compared to the case of bearing the cooling load of the outside air. Therefore, it is possible to suppress an increase in initial cost. Furthermore, as the operating state of the heat pump 30 is stabilized, the operating state of the electric heater 70, that is, the heating amount is also stable throughout the year, as shown in Fig. 12 when the heat pump is used, and the capacity of the electric heater 70 is reduced. Thus, it is possible to reduce the size.

In addition, since these devices operate effectively throughout the year, the energy saving effect on the increase in initial costs is increased.

In this embodiment, a refrigerator 80 for cooling the introduced outside air 91 is provided, and the refrigerator 80 is controlled so that the temperature of the processing air supplied to the processing zone 11 of the dehumidifying rotor 10 is constant. Therefore, it is possible to supply stable low-humidity air to the air-conditioned room and stabilize the operation state of the heat pump 30 regardless of fluctuations in the outside air temperature.

Furthermore, in the present embodiment, a second cooling coil 82 for recooling the indoor return air 94 cooled by the air cooler 35 of the heat pump 30 using a part of the cooling capacity of the refrigerator 30 is provided. Since the cooling is performed, it is possible to cope with the fluctuation of the indoor load in addition to the fluctuation of the outside air temperature without changing the operation state of the heat pump 30. [0082] Further, in this embodiment, since the outside air radiator 33 is installed as the heat radiating part of the heat pump 30 in addition to the air heater 32 that heats the regeneration air 95, as shown in FIG. The refrigerant enthalpy at the evaporator inlet drops to the value of state B in Fig. 9 as the value. As a result, if the outside air radiator 33 is not installed, the cooling capacity of the air cooler is changed from the enthalpy difference between state B and state F to the difference in enthalpy between state D and state F, that is, QE shown in Fig. 9. It is increasing. Accordingly, the refrigeration load of the refrigerator 80 is reduced, and the effect of reducing the size of the refrigerator 80 and saving energy can be obtained.

[0083] Further, in this embodiment, the entire dehumidifying air conditioning system is composed of a waste heat unit 101 including a compressor 31, an outside air radiator 33, a fan 38, a dehumidifying rotor 10, an air heater 32, an air cooler 35, and the like. Therefore, the exhaust heat unit 101 can be installed outdoors, and the dehumidifier unit 102 can be installed outdoors.

[0084] Since the dehumidifier unit 102 circulates the processing air, there is an advantage that installation of waterproofing or the like becomes unnecessary by installing the dehumidifier unit 102 indoors such as a machine room. On the other hand, in the exhaust heat unit 101, the lower the refrigerant outlet temperature from the outside air radiator 33, the greater the cooling capacity QE of the air cooler shown in FIG. 9 and the load on the refrigerator 30 is reduced, thereby saving energy. . Therefore, this energy saving effect is increased by installing the exhaust heat unit 101 outdoors and dissipating heat to the outside air whose temperature is lower than that in the machine room. In this embodiment, these advantages can be obtained simultaneously.

[0085] Further, in this embodiment, the refrigerant of the heat pump 30 dissipates heat at a supercritical pressure in the air heater 32, so that the refrigerant continuously passes through the air heater 32. Since heat is dissipated to the regenerative air 95 while the temperature is reduced, counter-flow heat exchange with the regenerative air 95 is possible, and as shown in the comparison of the use of heat pump “Yes” and “No” in FIGS. The power consumption of the electric heater 70 has been reduced and the energy saving effect of the entire dehumidifying air conditioning system has been obtained.

[0086] Further, in the present embodiment, carbon dioxide is used as the refrigerant of the heat pump 30 and the critical temperature is relatively low at 31.1 ° C, so that the high pressure side of the cycle easily enters the supercritical state. As a result, the supercritical heat dissipation effect can be obtained. In addition, as is well known, carbon dioxide has a very low global warming potential, which is an environmental problem that does not require refrigerant recovery. A corresponding dehumidifying air conditioning system can be obtained.

[0087] Further, in each of the embodiments described above, since the outside air radiator 33 is installed as a cooling means for the refrigerant after exiting the air heater 32 and cooled by the outside air 99 for heat dissipation, There is an advantage that water system facilities are unnecessary.

On the other hand, when the present system is introduced in a factory where a cooling water system has been prepared in advance, a water-cooled refrigerant cooler may be installed in place of the outside air radiator 33 and cooled by the cooling water. In this case, instead of requiring a cooling water system, cooling can be performed with a smaller heat transfer area compared to the air-cooled outside air radiator 33, so there is an advantage that the refrigerant cooler and the dehumidifying air conditioning system can be downsized. is there. Obviously, this cooling water may be river water or seawater.

[0088] Example 4

Next, a fourth embodiment of the present invention will be described with reference to FIG. The dehumidifying air conditioning system in Fig. 13 has almost the same configuration as in Fig. 8, but the following points are different. In the embodiment of FIG. 8, the indoor return air 94 recirculated from the inside of the room is cooled by the second cooling coil 82, whereas in this embodiment, the indoor return air 94 and the outside air 91 introduced from the outside merge. After that, the processing air is cooled by the second cooling coil 82.

In this embodiment, the processing air immediately before flowing into the processing zone 11 of the dehumidifying rotor 10 is cooled by the second cooling coil 82. As a result, as compared with the third embodiment, the rotor inlet air temperature detected by the temperature sensor 39 can be stably controlled near the target value by the capacity control of the refrigerator 80. As described above, in the dehumidifying rotor holding the dehumidifying member, the dehumidifying performance is influenced by the inlet temperature of the processing air, and in this embodiment, the inlet temperature is stabilized, so that the temperature of the rotor outlet air, that is, the supply air 93 is increased. And there is an advantage that humidity can be controlled stably near the target value. This is particularly important from the viewpoint of improving production quality in applications where a low humidity environment is required, such as in manufacturing processes for semiconductors and displays.

[0090] It should be noted that the heat pump cycle, the power consumption, and the annual variation of the power consumption in this example are shown in Figs. 9, 11, and 12, respectively, as in the third example, and the same effects can be obtained. it can. A unit configuration similar to that shown in Fig. 10 is also possible. The same effect as the example can be obtained.

Claims

The scope of the claims

[1] A treatment zone that absorbs moisture from the treatment air, a regeneration zone that releases this moisture to the high-temperature regeneration air, and a purge zone that cools the area where the moisture has been released due to the temperature rise in the regeneration zone. The dehumidification rotor sequentially rotates, the purge type desiccant dehumidifier passing through the processing zone, the regeneration zone and the purge zone, a heat pump having a heat absorbing portion and a heat radiating portion, and cooling the heat absorbing portion. In a dehumidification air conditioning system having a cooler that cools the processing air as a source, and a heater that heats the regeneration air at the regeneration zone inlet side using the heat dissipating unit as a heating source,

The dehumidifying air conditioning system is characterized in that the heat radiating section includes a first heat radiator that releases heat to the regeneration air, a second heat radiator that releases heat to an external cooling medium, and a fan. .

[2] In the dehumidifying air-conditioning system according to claim 1,

The dehumidifying air conditioning system according to claim 1, wherein the heat pump is provided with an internal heat exchange for exchanging heat between the refrigerant radiated by the second radiator and the refrigerant absorbed by the heat absorbing unit.

[3] In the dehumidifying air conditioning system according to claim 1 or 2,

A dehumidifying air-conditioning system comprising a control device that detects the temperature of the treated air that has been cooled and controls the capacity of the heat pump.

[4] In the dehumidifying air-conditioning system according to any one of claims 1 and 2,

After the regeneration air is heated in the first radiator, reheating means for heating is further provided, and this reheating means force is also configured to guide the regeneration air to the regeneration zone of the desiccant dehumidifier. Dehumidification air conditioning system.

[5] In the dehumidifying air conditioning system according to claim 3,

[6] In the dehumidifying air-conditioning system according to claim 4,

A dehumidifying air-conditioning system comprising a control device for detecting a temperature of regenerated air heated by the reheating means and adjusting a heating amount of the reheating means.

[7] In the dehumidifying air-conditioning system according to claim 5,

[8] In the dehumidifying air-conditioning system according to claim 6,

A dehumidifying air-conditioning system comprising auxiliary cooling means for cooling the processing air

[9] In the dehumidifying air-conditioning system according to claim 7,

[10] In the dehumidifying air-conditioning system according to claim 8,

A temperature sensor for detecting the temperature of the processing air cooled by the auxiliary cooling means is provided, and a control device for starting / stopping or controlling the capacity of the auxiliary cooling means using an output of the temperature sensor power is provided. And dehumidifying air conditioning system.

[11] In the dehumidifying air-conditioning system according to claim 9,

[12] In the dehumidifying air-conditioning system according to claim 10,

The dehumidifying air conditioning system, wherein the external cooling medium is air.

[13] In the dehumidifying air-conditioning system according to claim 11,

[14] In the dehumidifying air-conditioning system according to claim 12,

The dehumidifying air conditioning system, wherein the external cooling medium is cooling water.

[15] In the dehumidifying air-conditioning system according to claim 13,

[16] In the dehumidifying air-conditioning system according to claim 14,

The dehumidifying air conditioning system characterized in that the refrigerant of the heat pump radiates heat at a supercritical pressure in the heat radiating section.

[17] In the dehumidifying air-conditioning system according to claim 15,

[18] In the dehumidifying air-conditioning system according to claim 16,

The dehumidifying air conditioning system characterized in that the refrigerant of the heat pump is carbon dioxide.

[19] In the dehumidifying air-conditioning system according to claim 17,

[20] The dehumidification rotor has a treatment zone that absorbs moisture of the treatment air and a regeneration zone that releases this moisture to the high-temperature regeneration air, and the treatment zone and the regeneration are obtained by rotating the dehumidification rotor. A desiccant dehumidifier that sequentially passes through a zone, a heat pump having an endothermic part and a heat radiating part, an air cooler that cools the processing air using the endothermic part as a cooling source, and the regeneration air using the radiating part as a heating source. A dehumidifying air conditioning system with an air heater that heats the air at the regeneration zone entrance! /

The treated air is a mixed air of outside air introduced from the outside and indoor return air to be recirculated by being guided from the room to be air-conditioned, and an air cooler using the heat absorption part as a cooling source A dehumidifying air conditioning system provided in a flow path.

[21] A treatment zone in which the dehumidification rotor absorbs moisture from the treatment air, a regeneration zone that releases this moisture to the high-temperature regeneration air, and a region where the moisture is released due to a temperature rise in the regeneration zone are And a purge type desiccant dehumidifier that sequentially passes through the treatment zone, the regeneration zone and the purge zone as the dehumidifying rotor rotates, and a heat pump having a heat absorbing portion and a heat radiating portion. An air cooler that cools the processing air using the heat absorption part as a cooling source, and an air heater that heats the regeneration air on the regeneration zone inlet side using the heat dissipation part as a heating source. And

The treated air is a mixed air of introduced outside air introduced from the outside and indoor return air that is guided and recirculated from the room to be air-conditioned, and the air cooler is provided in the flow path of the indoor return air, and A dehumidifying air conditioning system comprising a refrigerator that cools the introduced outside air upstream of the mixing section with the indoor return air.

[22] In the dehumidifying air-conditioning system according to claim 21,

The refrigerator cools the introduced outside air upstream of the mixing portion with the indoor return air and introduces the indoor return air cooled by the air cooler using the heat absorption portion of the heat pump as a cooling source. A dehumidifying air conditioning system characterized by recooling before or after merging with outside air.

[23] In the dehumidifying air-conditioning system according to claim 22,

The heat dissipation part of the heat pump is composed of an air heater that radiates heat to the regeneration air as a heating source of the regeneration air, and an outside air radiator that releases heat to an external cooling medium. .

[24] The dehumidification rotor has a treatment zone that absorbs moisture of the treatment air and a regeneration zone that releases this moisture to the high-temperature regeneration air, and the treatment zone and the regeneration are obtained by rotating the dehumidification rotor. In a dehumidifying air conditioning system comprising a desiccant dehumidifier that sequentially passes through a zone, a heat pump having a heat absorbing portion and a heat radiating portion, and a cooler that cools the processing air using the heat absorbing portion as a cooling source,

The heat radiating section is composed of an air heater that heats the regeneration air on the regeneration zone inlet side, and an outside air radiator that releases heat to an external cooling medium. Further, the entire apparatus includes the dehumidification rotor and the heat pump. A dehumidifier unit consisting of a heat absorption part, that is, a cooler, an air heater of a heat pump, and the like, and a heat exhaust unit such as the compressor and the second radiator, and a refrigerant pipe connecting them. Dehumidifying air conditioning system.

[25] In the dehumidifying air-conditioning system according to claim 24,

The dehumidifying air conditioning system characterized in that the dehumidifier unit is installed indoors and the exhaust heat unit is installed outdoors.

[26] In the dehumidifying air-conditioning system according to claim 24,

The dehumidifying air conditioning system, wherein the external cooling medium is air or cooling water.

[27] In the dehumidifying air-conditioning system according to claim 24,

[28] In the dehumidifying air-conditioning system according to claim 27, The dehumidifying air conditioning system characterized in that the refrigerant of the heat pump is carbon dioxide.