JP2008151458A - Desiccant air conditioner and its dew proofing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a dew proofing device of a desiccant air conditioner capable of preventing dew condensation in a sensible-heat heat exchanger in ventilating operation. <P>SOLUTION: This desiccant air conditioner comprises a dew-proofing control means for executing either an exhausting operation where only a first blower 10 is operated while stopping a second blower 11, or a dehumidifying operation for operating the first and second blowers 10, 11 and operating a latent heat rotor 14 and a regenerative heater 13, when a differential temperature (evaluated differential temperature value) obtained by subtracting an inside air temperature T<SB>in</SB>from an outside air dew point temperature T<SB>dewout</SB>is over a prescribed threshold value in a state of the ventilating operation in which the latent heat rotor 14 and the regenerative heater 13 are stopped and the first and second blowers 10, 11 are operated. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a dew proof device for preventing condensation in a sensible heat exchanger of a desiccant air conditioner that performs dehumidification using a desiccant rotor by an adsorption method.

  In recent years, a desiccant air conditioner has been developed that ventilates air in an air-conditioned space and dehumidifies outside air in the outside air space so that the air is taken into the air-conditioned space. A desiccant air conditioner is an adsorption-type dehumidifier equipped with a honeycomb-structured latent heat rotor carrying a desiccant (desiccant) such as silica gel or zeolite powder, and dehumidifying the latent heat rotor by adsorbing moisture. (For example, see Patent Document 1, Non-Patent Documents 1 and 2).

  In the desiccant air conditioner, simply by adsorbing moisture to the latent heat rotor, the supply air temperature increases due to the heat of adsorption. Therefore, a desiccant air conditioner equipped with a sensible heat exchanger for exchanging heat between dehumidified air for dehumidification and regenerated air (humidified air) for drying and regenerating the desiccant of the latent heat rotor. Has been developed (see Patent Document 1).

  In FIG. 11, the structure of the typical desiccant air conditioner of patent document 1 is shown. The desiccant air conditioner 100 includes a housing 101, and the interior of the housing 101 is partitioned into a first ventilation path 103 and a second ventilation path 104 by a partition wall 102.

  A regeneration air suction port 105 and a processing air outlet 106 are formed at one end of the housing 101 facing the indoor side, and a processing air suction port 107 and a regeneration air are formed at the other end of the housing 101 facing the outdoor side. An air outlet 108 is formed. The regeneration air suction port 105 and the regeneration air outlet 108 are respectively an inlet and an outlet of the first air passage 103, and the processing air inlet 107 and the processing air outlet 106 are respectively a second air passage. 104 entrances and exits.

  Near the regeneration air outlet 108 of the first ventilation path 103, a first blower 109 is provided for circulating the air in the first ventilation path 103 from the regeneration air inlet 105 to the regeneration air outlet 108. ing. In addition, a second blower 110 for circulating the air in the second ventilation passage 104 from the treatment air suction port 107 to the treatment air outlet 106 is provided in the vicinity of the treatment air suction port 107 of the second ventilation passage 104. Is provided.

  Furthermore, a sensible heat exchanger 111, a regenerative heater 112, a latent heat rotor 113, and a drive motor 114 are disposed inside the housing 101. The latent heat rotor 113 is driven to rotate at a low speed by a drive motor 114.

  The indoor air that has flowed into the first ventilation path 103 from the regenerative air suction port 105 exchanges heat with the air flowing through the second ventilation path 104 in the sensible heat exchanger 111. Then, after being heated by the regenerative heater 112, it passes through the latent heat rotor 113. At this time, moisture adsorbed by the latent heat rotor 113 is desorbed and moisture is taken in. And it is discharged | emitted from the regeneration air blower outlet 108 outdoor.

  On the other hand, outdoor air that has flowed into the second ventilation path 104 from the processing air suction port 107 first passes through the latent heat rotor 113. At this time, moisture contained in the outside air is adsorbed by the latent heat rotor 113, and the air flowing out from the latent heat rotor 113 to the second ventilation path 104 becomes dry air. In the sensible heat exchanger 111, heat exchange is performed with the air flowing through the first ventilation path 103, and then the air is discharged into the room from the processing air outlet 106.

In this way, the outdoor air is dehumidified and taken into the room, and the heat of the room air is transferred to the air taken into the room by the sensible heat exchanger 111. Such operation of the desiccant air conditioner is referred to as “dehumidification operation”.
JP 2000-346400 A Air Conditioning and Sanitation Engineering Association, “Air Conditioning and Sanitation Engineering Handbook”, 13th edition, Japan Air Conditioning and Hygiene Engineering Association, November 30, 2001, pp.451-452 Satoshi Kuwabara, Mitsugu Hiraoka, Norio Otsuka, “Humidification and Dehumidification (6) Dehumidification-Desiccant Air Conditioning”, [online], September 3, 2002, Japan Society for Air Conditioning and Sanitation, [August 2006 8 days search], <http://www.shasej.org/gakkaishi/0211/0211-koza-01.html>

  By the way, this desiccant air conditioner performs not only “dehumidification operation” but also “ventilation operation”. “Ventilation operation” means that only the first blower 109 and the second blower 110 are operated in a state where the regenerative heater 112 and the latent heat rotor 113 are stopped, so that indoor air and outdoor air are not dehumidified. This refers to driving with ventilation.

  In the ventilation operation, when the temperature difference between the outdoor air and the indoor air is large, high-temperature air including moisture flows into the sensible heat exchanger 111 and is rapidly cooled by heat exchange. In this case, when high-temperature air containing moisture is cooled to a dew point temperature or lower by the sensible heat exchanger 111, condensation occurs in the sensible heat exchanger 111. Accordingly, drain water is generated in the sensible heat exchanger 111 during the ventilation operation. Therefore, it is necessary to provide a drain drain pipe for draining drain water at the lower part of the sensible heat exchanger 111.

  Usually, the desiccant air conditioner is often installed behind the ceiling near the ceiling duct provided on the ceiling of the room. For this reason, piping for pulling the drain drain pipe to the outside is often difficult. Therefore, a technique for preventing the generation of drain water in the sensible heat exchanger during ventilation operation has been demanded.

  Accordingly, an object of the present invention is to provide a dew-proofing device for a desiccant air conditioner for preventing condensation from occurring in a sensible heat exchanger during ventilation operation.

The first configuration of the dew protection device for the desiccant air conditioner according to the present invention is the first air passage and the second air passage communicating the air conditioned space and the outside air space, and the air conditioner through the first air passage. A first blower that circulates air in the space to the outside air space; a second blower that circulates air in the outside air space to the conditioned space through the second ventilation path; and the first ventilation path. A sensible heat exchanger that exchanges heat between the air flowing through the air and the air flowing through the second ventilation path, and moisture in the air that flows into the sensible heat exchanger through the second ventilation path And the latent heat rotor for releasing the moisture into the air flowing from the sensible heat exchanger through the first ventilation path, and flowing into the latent heat rotor through the first ventilation path. In a desiccant air conditioner equipped with a regenerative heater for heating air to be A anti-condensation device for preventing dew condensation in the sensible heat exchanger, the temperature of the conditioned space (hereinafter referred to as "inside air temperature".) And the inside air temperature detection means for detecting a T _in, humidity in the conditioned space (hereinafter "room air humidity" The inside air humidity detecting means for detecting ρ _in , the temperature of the outside air space (hereinafter referred to as “outside air temperature”), the outside air temperature detecting means for detecting T _out , and the humidity of the outside air space (hereinafter referred to as “outside air humidity”). ) The outside air humidity detecting means for detecting ρ _out and the outside air dew point temperature T _dewout is calculated from the outside air temperature T _out and the outside air humidity ρ _out , or the inside air dew point temperature T from the inside air temperature T _in and the inside air humidity ρ _{in. In} the state of ventilation operation in which the dew point temperature calculating means for calculating _dewin , the latent heat rotor and the regenerative heater are stopped and the first and second blowers are operated, the inside air is _deduced from the dew point temperature T _{dewout of the} outside air. minus the temperature T _in When the difference temperature or the difference temperature obtained by subtracting the outside air temperature T _out from the inside air dew point temperature T _dewin (hereinafter referred to as “evaluation difference temperature value”) exceeds a predetermined threshold, the second blower is stopped. Dew prevention control for performing control to execute either an exhaust operation for operating only the first blower or a dehumidifying operation for operating the first and second blowers to operate the latent heat rotor and the regenerative heater And means.

  According to this configuration, in the ventilation operation state, the dew prevention control means performs control to execute either the exhaust operation or the dehumidification operation when the evaluation differential temperature value exceeds the predetermined threshold value. Thereby, it is possible to prevent the sensible heat exchanger from condensing according to the following principle.

First, (if conditioned space is in a cooling state) when the outside air temperature is higher than the inside air temperature, the evaluation difference Yutakachi is differential temperature ΔT = _T dewout minus inside air temperature T _in the outdoor air dew-point temperature T _Dewout -T _in . In this case, the side facing the air-conditioned space of the desiccant air conditioner is lower than the outside air temperature _Tout . Therefore, the air flowing into the air-conditioned space through the second ventilation path is cooled while flowing through the second ventilation path. And if it cools below the dew point temperature _{Tdewout of} external air, dew condensation will arise in a 2nd ventilation path. The magnitude of the temperature drop of the air while circulating in the second ventilation path increases as the inside air temperature decreases. Therefore, the evaluation differential temperature value ΔT is a parameter for evaluating the degree of temperature drop of the air in the second ventilation path, and condensation becomes easier as the evaluation differential temperature value ΔT is larger.

  Therefore, the dew prevention control means determines that condensation may occur in the second ventilation path when the evaluation differential temperature value ΔT exceeds the “predetermined threshold value”, and either the exhaust operation or the dehumidification operation is performed. To execute.

  When the exhaust operation is performed, the second blower is stopped and only the first blower is operated. As a result, no outside air flows into the second ventilation path, so that moisture in the outside air space does not flow into the second ventilation path, and condensation is prevented from occurring in the second ventilation path. .

Further, when the dehumidifying operation is performed, the first and second blowers are operated, and the latent heat rotor and the regenerative heater are operated. As a result, the air that has flowed into the second ventilation path is dehumidified by adsorbing moisture in the latent heat rotor. On the other hand, the air flowing into the latent heat rotor from the first ventilation path is heated by the regenerative heater. Accordingly, the moisture adsorbed on the latent heat rotor is desorbed and released to the air in the first ventilation path. Here, the heat of the air flowing through the heated first ventilation path is absorbed by the latent heat rotor. Then, the air in the second ventilation path is dehumidified, receives heat from the latent heat rotor, and rises in temperature. Then, the air whose temperature has risen flows down the second ventilation path, passes through the sensible heat exchanger, and is discharged into the conditioned space. Therefore, the temperature of the air in the second air passage passing through the sensible heat exchanger, to become higher than the inside air temperature T _in, cooling width of the air flowing through the first air passage in the sensible heat exchanger is small Become. Therefore, it becomes possible to keep the temperature of the air in the 2nd ventilation path which distribute | circulates a sensible heat exchanger more than a dew point temperature, and can prevent dew condensation in a sensible heat exchanger.

On the other hand, when the temperature of the inside air is higher than the temperature of the outside air (when the air-conditioned space is in a heating state), the evaluation differential temperature value is a difference temperature ΔT = T _{dewin obtained} by subtracting the outside air temperature T _out from the dew point temperature T _{dewin of the} inside air. -T _out . In this case, the side facing the outside air space of the desiccant air conditioner, lower than the inside air temperature T _in. Therefore, the air flowing out to the outside air space through the first ventilation path is cooled while flowing through the first ventilation path. And if it cools to below the dew point temperature _{Tdewin of} inside air, dew condensation will arise in the 1st ventilation path. The magnitude of the temperature drop of the air while circulating in the first ventilation path increases as the outside air temperature decreases. Therefore, the evaluation differential temperature value ΔT is a parameter for evaluating the degree of temperature drop of the air in the first ventilation path, and condensation becomes easier as the evaluation differential temperature value ΔT is larger.

  Therefore, the dew prevention control means determines that there is a possibility that condensation occurs in the first ventilation path when the evaluation differential temperature value ΔT exceeds the “predetermined threshold value”, and either the exhaust operation or the dehumidification operation is performed. To execute.

  When the exhaust operation is performed, the second blower is stopped and only the first blower is operated. Thereby, since the inflow of cold outside air into the second ventilation path is eliminated, the sensible heat exchanger is not cooled by the air flowing into the second ventilation path. Therefore, the temperature drop of the sensible heat exchanger rises and the temperature drop in which the temperature of the air in the first ventilation path falls in the sensible heat exchanger can be reduced. Thereby, the dew condensation in the 1st ventilation path of a sensible heat exchanger is prevented.

  Further, when the dehumidifying operation is performed, the first and second blowers are operated, and the latent heat rotor and the regenerative heater are operated. As a result, the air that has flowed into the second ventilation path is dehumidified by moisture adsorbed by the latent heat rotor. Accordingly, since the humidity of the air in the second ventilation path flowing into the sensible heat exchanger is lowered, the dew point temperature is lowered. This prevents condensation in the second ventilation path of the sensible heat exchanger.

  Here, “air-conditioned space” refers to a space where air conditioning is performed, for example, an indoor space. “Outside air space” refers to a space outside the air-conditioned space, for example, an outdoor space.

  The “regenerative heater” is a heating device that heats the air flowing from the sensible heat exchanger to the latent heat rotor through the first ventilation path. As the regenerative heater, a hot water heat exchanger or an electric heater is used. Etc. are used.

  “Inside air temperature” refers to the temperature in the air-conditioned space, “Inside air humidity” refers to the humidity in the air-conditioned space, “Outside air temperature” refers to the temperature in the outside air space, and “Outside air humidity” refers to the humidity in the outside air space. Say. As the inside air temperature detecting means and the inside air humidity detecting means, individual temperature sensors or humidity sensors may be used, or a temperature / humidity sensor in which the temperature sensor and the humidity sensor are integrated may be used. As for the outside air temperature detecting means and the outside air humidity detecting means, individual temperature sensors and humidity sensors may be used, or a temperature and humidity sensor in which the temperature sensor and the humidity sensor are integrated may be used.

  “Ventilation operation” refers to an operation in which the latent heat rotor and the regenerative heater are stopped and the first and second blowers are operated. In the ventilation operation, the inside air in the air-conditioned space is exhausted as it is to the outside air space, and the outside air in the outside air space is supplied as it is into the air-conditioned space.

  “Exhaust operation” refers to an operation in which the second blower is stopped and only the first blower is operated. In the exhaust operation, the inside air in the air-conditioned space is exhausted as it is to the outside air space, and air supply from the outside air space is not performed.

  “Dehumidifying operation” refers to an operation in which the first and second blowers are operated and the latent heat rotor and the regenerative heater are operated. In the dehumidifying operation, the inside air in the air-conditioned space is exhausted to the outside air space, the outside air in the outside air space is supplied into the air-conditioned space, and the humidity of the supplied outside air is transferred to the discharged inside air.

The "evaluation difference temperature value", refers to a temperature difference obtained by subtracting the outside air temperature T _out from the outside air dew-point temperature _T dewout from the differential temperature or shy minus the inside air temperature T _in the dew-point temperature _T dewin. As described above, the evaluation differential temperature value is a parameter representing the ease of condensation of air supplied to the air-conditioned space or air discharged from the air-conditioned space.

  The “predetermined threshold value” is a value determined experimentally, and is a value equal to or less than a value obtained by subtracting the temperature of the air at which dew condensation starts to occur in the sensible heat exchanger from the dew point temperature. That is, the “predetermined threshold value” may be set so as to ensure that condensation does not occur in the sensible heat exchanger when the temperature difference belongs to a section equal to or less than the “predetermined threshold value”.

According to a second configuration of the dew proofing device for a desiccant air conditioner according to the present invention, in the first configuration, the dew proof control means has the evaluation temperature difference value exceeding a predetermined threshold value in the state of the ventilation operation. In this case, the exhaust operation and the dehumidifying operation are controlled alternately at predetermined time intervals.

  According to this configuration, the dew prevention control means effectively prevents condensation inside the first ventilation path or the second ventilation path in the sensible heat exchanger and saves energy consumed in the dehumidifying operation. can do.

  That is, it is possible to more effectively prevent condensation in the sensible heat exchanger when the dehumidifying operation is performed than when the exhaust operation is performed. Therefore, in order to obtain the maximum dew-proof effect, the dehumidifying operation may be performed continuously. However, in the dehumidifying operation, in order to operate the regenerative heater, it is necessary to supply heat energy to the regenerative heater. Therefore, the dehumidifying operation consumes more energy than the exhaust operation.

  Therefore, by alternately performing the exhaust operation and the dehumidifying operation at predetermined time intervals, it is possible to suppress energy consumption as much as possible while obtaining a high dew-proof effect.

The third configuration of the dew protection device for the desiccant air conditioner according to the present invention is the first configuration, wherein the dew control unit is configured such that the evaluation differential temperature value is a first threshold temperature in the ventilation operation state. If the value exceeds T _1, wherein to execute the exhaust operation, the evaluation difference temperature value, when it exceeds a higher second threshold temperature T ₂ than the first threshold temperature T _1, the control to execute the dehumidifying operation It is characterized by performing.

  In this way, the more the condensation is more likely to occur depending on the size of the evaluation differential temperature value, the more the dew-proofing effect is obtained by switching to the operation with a higher dew-proofing effect, while the energy consumption associated with the dew-proofing operation is reduced. It can be kept low.

According to a fourth configuration of the dew protection device for the desiccant air conditioner according to the present invention, in the first configuration, the dew control unit is configured such that the evaluation differential temperature value is a first threshold temperature in the state of the ventilation operation. When T ₁ is exceeded, the exhaust operation is executed, and when the evaluation differential temperature value exceeds a _second threshold temperature T ₂ higher than the first threshold temperature T ₁ , the exhaust operation and the dehumidifying operation are performed. was performed alternately at predetermined time intervals the control, the evaluation difference temperature value, when exceeding the second threshold temperature T ₂ third threshold temperature T ₃ higher than, for executing the dehumidifying operation continuously It is characterized by performing.

  In this way, the more the condensation is more likely to occur depending on the size of the evaluation differential temperature value, the more the dew-proofing effect is obtained by switching to the operation with a higher dew-proofing effect, while the energy consumption associated with the dew-proofing operation is reduced. It can be kept low.

In a fifth configuration of the dew proofing device for a desiccant air conditioner according to the present invention, in the third or fourth configuration, the dew proof control means has the evaluation differential temperature value in the state of the ventilation operation. When the second threshold temperature T ₂ exceeds the _fourth threshold temperature T ₄ higher than the third threshold temperature T ₃ , the first and second blowers are stopped.

  As described above, when the evaluation temperature difference is large and it is difficult to prevent condensation even by dehumidifying operation, the condensation in the sensible heat exchanger is prevented by stopping the first and second blowers. be able to.

  A desiccant air conditioner according to the present invention includes the dew proofing device having any one of the first to fifth configurations.

  As described above, according to the present invention, in the ventilation operation state, the dew prevention control unit performs control to execute either the exhaust operation or the dehumidification operation when the evaluation differential temperature value exceeds the predetermined threshold value. Thus, it is possible to effectively prevent dew condensation inside the first ventilation path or the second ventilation path in the sensible heat exchanger.

  The best mode for carrying out the present invention will be described below with reference to the drawings.

[1] Overall Configuration of Desiccant Air Conditioner FIG. 1 is a diagram showing an overall configuration of a desiccant air conditioner including a dew proof device according to Embodiment 1 of the present invention.

  The desiccant air conditioner 1 in FIG. 1 includes a housing 2, and the interior of the housing 2 is divided into a first ventilation path A and a second ventilation path B by partition walls 3, 4, and 5. One end side of the housing 2 faces the air-conditioned space, and the other end side faces the outside air space.

  Here, the “air-conditioned space” is a space where air conditioning is performed, and in the case of the present embodiment, means an indoor space. Further, the “outside air space” refers to a space outside the air-conditioned space, and in the present embodiment, refers to an outdoor space.

  On the side surface of the housing 2 facing the air-conditioned space, a regeneration air suction port 6 that is an air supply port for the inside air of the first ventilation path A and a processing air outlet 9 that is an exhaust port of the second ventilation path B are formed. Has been. Further, on the side surface of the housing 2 facing the outside air space, a processing air suction port 8 that is an air supply port for the outside air in the second ventilation path B and a regeneration air outlet 7 that is an exhaust port for the first ventilation path A are provided. Is formed.

  Further, in the housing 2, there are a first blower 10, a second blower 11, a sensible heat exchanger 12, a regenerative heater 13, a thermal valve 13 a, a heat exchanger temperature sensor 13 b, a latent heat rotor 14, an inside air temperature humidity. A sensor 15, an outside air temperature / humidity sensor 16, and a control panel 17 are disposed.

  The first blower 10 is disposed in the vicinity of the regeneration air outlet 7 in the first ventilation path A. The first blower 10 distributes the air in the air-conditioned space to the outside air space through the first ventilation path A. The second blower 11 is disposed in the vicinity of the processing air outlet 9 in the second ventilation path B. The second blower 11 circulates the air in the outside air space to the air-conditioned space through the second ventilation path B.

  The sensible heat exchanger 12 exchanges heat between the air flowing through the first ventilation path A and the air flowing through the second ventilation path B.

  The latent heat rotor 14 adsorbs moisture in the air flowing into the sensible heat exchanger 12 through the second ventilation path B, and flows the moisture out of the sensible heat exchanger 12 through the first ventilation path A. To air. The latent heat rotor is formed of a cylindrical porous material whose central axis is parallel to the partition wall 5, and is rotated at a low speed by a rotor motor 18 (see FIG. 2).

  The regenerative heater 13 is a heat exchanger that heats the air flowing into the latent heat rotor 14 through the first ventilation path A. As a result, the first ventilation path A side of the latent heat rotor 14 is heated, and moisture adsorbed on the latent heat rotor 14 is desorbed.

  The thermal valve 13 a is a valve that disconnects hot water supplied to the regenerative heater 13. The heat exchanger temperature sensor 13 b is a temperature sensor that detects the temperature of hot water supplied to the regenerative heater 13.

  The inside air temperature / humidity sensor 15 is installed in the vicinity of the regenerative air inlet 6 of the first ventilation path A. The inside air temperature / humidity sensor 15 is a sensor that detects the temperature and humidity of air (inside air) in the air-conditioned space that flows into the first ventilation path A from the regeneration air suction port 6.

  The outside air temperature / humidity sensor 16 is installed in the vicinity of the processing air inlet 8 of the second ventilation path B. The outside air temperature / humidity sensor 16 is a sensor that detects the temperature and humidity of the air (outside air) in the outside air space that flows into the second ventilation path B from the processing air suction port 8.

  The control panel 17 includes a first air blower 10, a second air blower 11, and a thermal valve 13a based on the temperatures and humidity detected by the heat exchanger temperature sensor 13b, the internal air temperature / humidity sensor 15, and the external air temperature / humidity sensor 16. And a circuit board for controlling the operation of the latent heat rotor 14.

[2] Configuration of Control Mechanism FIG. 2 is a block diagram showing a hardware configuration of a control circuit of the desiccant air conditioner 1 of FIG. In FIG. 2, the 1st air blower 10, the 2nd air blower 11, the thermal valve 13a, the heat exchanger temperature sensor 13b, the inside air temperature humidity sensor 15, the outside air temperature humidity sensor 16, and the control panel 17 are the same as in FIG. Is.

  The desiccant air conditioner 1 includes a rotor motor 18 and a remote controller 19. As described above, the rotor motor 18 is a motor that rotationally drives the latent heat rotor 14 at a low speed. The remote controller 19 is an input device for a user to input an operation instruction to the desiccant air conditioner 1.

  The control panel 17 includes an A / D converter 21, an input circuit 22, a central processing unit 23, a memory 24, a timer 25, and an output circuit 26.

  Analog temperature detection signals or humidity detection signals output from the heat exchanger temperature sensor 13 b, the inside air temperature humidity sensor 15, and the outside air temperature humidity sensor 16 are input to the A / D converter 21 of the control panel 17. The A / D converter 21 A / D converts these analog signals and outputs them to the input circuit 22 as digital signals. The input circuit 22 is an input interface that inputs digitized temperature detection signal and humidity detection signal and an operation instruction signal from a remote controller to the central processing unit 23.

  The central processing unit 23 controls the operation of the first blower 10, the second blower 11, the rotor motor 18, the thermal valve 13 a and the like based on various signals input from the input circuit 22. Further, the central processing unit 23 is connected to a memory 24 and a timer 25 necessary for arithmetic processing.

  The output circuit 26 is an output interface for outputting a control signal transmitted from the central processing unit 23 to the first blower 10, the second blower 11, the rotor motor 18, the thermal valve 13a, and the like. The control signal output from the output circuit 26 is transmitted to each device, whereby the desiccant air conditioner 1 is controlled.

[3] Configuration of Dew Protecting Device FIG. 3 is a block diagram showing a functional configuration of the dew preventing device of the desiccant air conditioner 1 of FIG. In FIG. 3, a first blower 10, a second blower 11, a thermal valve 13a, an inside air temperature / humidity sensor 15, an outside air temperature / humidity sensor 16, a control panel 17, and a rotor motor 18 are shown in FIGS. Of the same sign.

  The dew protection device of this embodiment includes an inside air temperature detection means 31, an inside air humidity detection means 32, an outside air temperature detection means 33, an outside air humidity detection means 34, a dew point temperature calculation means 35, and a dew prevention control means 36.

  The inside air temperature detecting means 31 and the inside air humidity detecting means 32 are realized by the inside air temperature / humidity sensor 15. The outside air temperature detecting means 33 and the outside air humidity detecting means 34 are realized by the outside air temperature / humidity sensor 16. The dew point temperature calculation means 35 and the dew prevention control means 36 are realized by the control panel 17.

Inside air temperature detecting means 31 detects the temperature of the conditioned space (inside air temperature) T _in. The inside air humidity detecting means 32 detects the humidity (inside air humidity) ρ _in the air-conditioned space. The outside air temperature detection means 33 detects the temperature (outside air temperature) _Tout of the outside air space. The outside air humidity detecting means 34 detects the humidity (outside air humidity) ρ _out of the outside air space.

Dew point temperature calculating means 35 calculates the outdoor air dew-point temperature T _Dewout from the outside air temperature T _out and ambient humidity [rho _out, or to calculate the inside air of dew point temperature T _Dewin from the inside air temperature T _in and the room air humidity [rho _in. The dew prevention control means 36 performs control to prevent condensation of the sensible heat exchanger 12 by controlling the first blower 10, the second blower 11, the thermal valve 13 a, and the rotor motor 18.

[4] Operation of the dew proof device during the ventilation operation The operation of the dew proof device according to the present embodiment configured as described above will be described below.

  First, as a precondition, it is assumed that the desiccant air conditioner 1 is in a ventilation operation state. That is, it is assumed that the first blower 10 and the second blower 11 are operating, and the regenerative heater 13 and the latent heat rotor 14 are in a stopped state. At this time, the air in the conditioned space is exhausted as it is to the outside air space through the first ventilation path A, and the air in the outside air space is directly supplied to the conditioned space through the second ventilation path B. Yes.

  In this way, in the state where the ventilation operation is being performed, dew condensation is likely to occur in the sensible heat exchanger 12, and therefore the dew condensation prevention operation by the dew prevention device is executed.

  FIG. 4 is a flowchart showing the operation of the dew protection device of the desiccant air conditioner 1.

First, in step S1, the dew point temperature calculating means 35 acquires the inside air temperature T _in and the inside air humidity ρ _in output from the inside air temperature / humidity sensor 15 (the inside air temperature detecting means 31 and the inside air humidity detecting means 32) as digital values. The outside air temperature T _out and the outside air humidity ρ _out output by the outside air temperature / humidity sensor 16 (the outside air temperature detecting unit 33 and the outside air humidity detecting unit 34) are acquired as digital values.

Next, in step S2, the dew point temperature calculation means 35 determines whether or not the outside air temperature T _out is _{equal to} or higher than the summer determination outside air temperature T _summer for preventing condensation. Here, the “summer determination outdoor temperature for countermeasure against condensation” refers to a temperature threshold value for determining that the current climate is a summer climate and that a condensation prevention operation for summer is necessary.

Here, if T _out ≧ T _summer , after performing “summer condensation prevention operation” described later in step S3, the process returns to step S1 again. On the other hand, if T _out <T _summer in step S2, the process _proceeds to the next step S4.

In step S4, the dew-point temperature calculating section 35 determines whether or not the outside air temperature T _out condensation countermeasure winter determination outside air temperature T _winter below. Here, the “determination winter temperature for dew condensation prevention” refers to a temperature threshold value for determining that the current climate is a winter climate and that a dew condensation prevention operation for winter is necessary.

Here, when T _out ≦ T _winter , after performing “winter condensation prevention operation” described later in step S5, the process returns to step S1 again. On the other hand, if T _out > T _winter in step S4, the process returns to step S1.

[5] Summer condensation prevention operation Next, the summer condensation prevention operation in step S3 will be described. In summer conditions, a case is assumed where the outside air temperature is higher than the inside air temperature. In this case, the air flowing from the outside air space to the air-conditioned space through the second ventilation path B is cooled to near the inside air temperature in the sensible heat exchanger 12. Therefore, dew condensation occurs when the air in the second ventilation path B falls below the dew point temperature by this cooling. Therefore, the dew condensation prevention operation is performed so that the air in the second ventilation path B does not become the dew point temperature or lower.

  FIG. 5 is a flowchart illustrating the operation of the dew protection device in the summer dew condensation prevention operation according to the first embodiment.

First, in step S11, the dew point temperature calculating means 35 calculates the dew point temperature T _{dewout of the} outside air from the outside air temperature T _out and the outside air humidity ρ _out . The dew point temperature T _dewout is calculated as follows. First, from the outside air temperature T _out, referring to the previously stored saturated absolute humidity table in the memory 24, and out measures the saturation set humidity at the ambient temperature T _out. Next, the saturated absolute humidity issued policy by applying the ambient humidity [rho _out, to calculate the absolute humidity D _out at the ambient temperature T _out. Finally, the dew point temperature table stored in advance in the memory 24 is referred to from the calculated absolute humidity D _out , and the dew point temperature T _dewout at the absolute humidity D _out is calculated. Thereby, the dew point temperature T _dewout of the outside air is calculated.

Next, in step S12, anti-condensation control means 36 calculates the differential temperature ΔT obtained by subtracting the inside air temperature T _in the outdoor air dew-point temperature T _Dewout as the evaluation difference temperature value.

Next, in step S13, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is larger than the threshold value ΔT _th . Here, if ΔT> ΔT _th , the dew prevention control means 36 determines that there is a possibility of condensation, performs dew condensation prevention control (S15), and ends the summer condensation prevention operation. On the other hand, if ΔT ≦ ΔT _th , the dew prevention control means 36 continues the normal ventilation operation as it is (S14), and ends the summer condensation prevention operation.

  Here, in the “dew condensation prevention control”, the dew prevention control means 36 performs any one of the following controls (1) to (3).

(1) The operation of the second blower 11 is stopped, and an exhaust operation state in which only the first blower 10 is operating is set. In this case, since high temperature and high humidity outside air does not flow into the second ventilation path B side of the sensible heat exchanger 12, dew condensation in the sensible heat exchanger 12 can be prevented.
(2) The first blower 10 and the second blower 11 are operated, the thermal valve 13a is opened to operate the regenerative heater 13, and the rotor motor 18 is started to operate the latent heat rotor 14. Set to the state of dehumidifying operation. As a result, moisture from outside air is adsorbed to the latent heat rotor 14 and the humidity is lowered. In addition, the heat supplied from the regenerative heater 13 through the latent heat rotor 14 flows into the sensible heat exchanger 12 through the first ventilation path A. Air temperature rises. Therefore, in the sensible heat exchanger 12, the temperature drop width of the air flowing through the second ventilation path B is reduced, and condensation in the sensible heat exchanger 12 can be prevented.
(3) The exhaust operation and the dehumidifying operation are executed while alternately switching at predetermined time intervals.

[6] Winter condensation prevention operation Finally, the winter condensation prevention operation in step S5 will be described. In winter conditions, the case where the inside air temperature is higher than the outside air temperature is assumed. In this case, the air flowing from the air-conditioned space to the outside air space through the first ventilation path A is cooled to the vicinity of the outside air temperature in the sensible heat exchanger 12. Therefore, dew condensation occurs when the air in the first ventilation path A falls below the dew point temperature by this cooling. Therefore, the dew condensation prevention operation is executed so that the air in the first ventilation path A does not become the dew point temperature or lower.

  FIG. 6 is a flowchart illustrating the operation of the dew protection device in the winter dew condensation prevention operation according to the first embodiment.

First, in step S21, the dew point temperature calculating means 35 calculates the dew point temperature T _dewin of the inside air from the inside air temperature T _in and the inside air humidity ρ _in . The calculation of the dew point temperature T _dewin is performed in the same manner as in step S11 of the summer dew condensation prevention operation.

Next, in step S22, the dew prevention control means 36 calculates a difference temperature ΔT obtained by subtracting the outside air temperature T _out from the inside air dew point temperature T _dewin as an evaluation difference temperature value.

Next, in step S23, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is larger than the threshold value ΔT _th . Here, if ΔT> ΔT _th , the dew prevention control means 36 determines that there is a possibility that condensation will occur, performs dew condensation prevention control (S25), and ends the winter condensation prevention operation. On the other hand, if ΔT ≦ ΔT _th , the dew prevention control means 36 continues the normal ventilation operation as it is (S24), and ends the winter condensation prevention operation.

  Here, in the “dew condensation prevention control”, the dew prevention control means 36 performs any one of the following controls (1) to (3).

(1) The operation of the second blower 11 is stopped, and an exhaust operation state in which only the first blower 10 is operating is set. In this case, since low temperature outside air does not flow into the second ventilation path B side of the sensible heat exchanger 12, dew condensation in the sensible heat exchanger 12 can be prevented.
(2) The first blower 10 and the second blower 11 are operated, the thermal valve 13a is opened to operate the regenerative heater 13, and the rotor motor 18 is started to operate the latent heat rotor 14. Set to the state of dehumidifying operation. Thereby, the temperature of the air flowing into the sensible heat exchanger 12 through the second ventilation path B is increased by the heat supplied from the regenerative heater 13 via the latent heat rotor 14. Therefore, in the sensible heat exchanger 12, even if the temperature of the air flowing through the first ventilation path A is lowered, the temperature becomes equal to or higher than the dew point temperature, and condensation in the sensible heat exchanger 12 can be prevented.
(3) The exhaust operation and the dehumidifying operation are executed while alternately switching at predetermined time intervals.

  By the above operation, dew condensation is prevented in the sensible heat exchanger 12, so there is no generation of drain water in the sensible heat exchanger 12, and a drain drain pipe becomes unnecessary.

  The configurations of the desiccant air conditioner and the dew proofing device of the second embodiment are the same as those shown in FIGS. Further, regarding the operation of the dew proofing device, the portions described in the flowchart of FIG. 4 are the same as those in the first embodiment, and thus the description thereof is omitted. The second embodiment is different from the first embodiment in the operations of the summer condensation prevention operation (step S3 in FIG. 4) and the winter condensation prevention operation (step S5 in FIG. 4). The present embodiment is characterized in that the condensation prevention operation is executed by switching to the condensation prevention control suitable for the magnitude of the evaluation differential temperature value ΔT.

  First, summer condensation prevention operation will be described. FIG. 7 is a flowchart illustrating the operation of the dew prevention device in the summer dew condensation prevention operation according to the second embodiment.

First, in step S31, the dew point temperature calculating means 35 calculates the dew point temperature T _{dewout of the} outside air from the outside air temperature T _out and the outside air humidity ρ _out . The method for calculating the dew point temperature T _dewout is as described in the first embodiment (see the description of step S11).

Next, in step S32, anti-condensation control means 36 calculates the differential temperature ΔT obtained by subtracting the inside air temperature T _in the outdoor air dew-point temperature T _Dewout as the evaluation difference temperature value.

Next, in step S33, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is equal to or greater than the first threshold value ΔT _th1 . Here, if ΔT <ΔT _th1 , the dew prevention control means 36 continues the normal ventilation operation as it is (S34), and ends the summer condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th1 , it is determined that condensation may occur, and the process proceeds to the next step S35.

In step S35, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is not less than the first threshold value ΔT _{th1 and} less than the second threshold value ΔT _th2 . Here, in the case of ΔT _th1 ≦ ΔT <ΔT _th2 , the dew prevention control means 36 switches the desiccant air conditioner 1 to the exhaust operation (S 36) and ends the summer dew condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th2 , the process proceeds to the next step S37.

In step S37, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is equal to or greater than the second threshold value ΔT _{th2 and} less than the third threshold value ΔT _th3 . Here, in the case of ΔT _th2 ≦ ΔT <ΔT _th3 , the dew prevention control means 36 switches the desiccant air conditioner 1 to the dehumidifying operation (S38), and ends the summer condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th3 , it is determined that condensation cannot be prevented only by dehumidification control, the operation of the desiccant air conditioner 1 is stopped (S39), and the summer condensation prevention operation is terminated.

  Next, winter condensation prevention operation will be described. FIG. 8 is a flowchart illustrating the operation of the dew prevention device in the winter dew condensation prevention operation according to the second embodiment.

First, in step S41, the dew point temperature calculating means 35 calculates the dew point temperature T _dewin of the inside air from the inside air temperature T _in and the inside air humidity ρ _in . The method for calculating the dew point temperature T _dewin of the inside air is as described in the first embodiment (see the description of step S11).

Next, in step S42, the dew prevention control means 36 calculates a temperature difference ΔT obtained by subtracting the outside air temperature T _out from the inside air dew point temperature T _dewin as an evaluation temperature difference value.

Next, in step S43, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is equal to or greater than the first threshold value ΔT _th1 . Here, when ΔT <ΔT _th1 , the dew prevention control means 36 continues the normal ventilation operation as it is (S44), and ends the winter condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th1 , it is determined that condensation may occur, and the process proceeds to the next step S45.

In step S45, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is not less than the first threshold value ΔT _{th1 and} less than the second threshold value ΔT _th2 . Here, in the case of ΔT _th1 ≦ ΔT <ΔT _th2 , the dew prevention control means 36 switches the desiccant air conditioner 1 to the exhaust operation (S46), and ends the winter condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th2 , the process proceeds to the next step S47.

In step S47, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is not less than the second threshold value ΔT _{th2 and} less than the third threshold value ΔT _th3 . Here, in the case of ΔT _th2 ≦ ΔT <ΔT _th3 , the dew prevention control means 36 switches the desiccant air conditioner 1 to the dehumidifying operation (S48), and ends the winter condensation prevention operation. On the other hand, in the case of ΔT ≧ ΔT _th3 , it is determined that condensation cannot be prevented only by dehumidification control, the operation of the desiccant air conditioner 1 is stopped (S49), and the winter condensation prevention operation is terminated.

  As described above, even if it is determined that it is necessary to prevent condensation, if the evaluation differential temperature value ΔT is relatively small, the exhaust operation is performed with a small dew-proof effect but low energy consumption. When the temperature value ΔT is large, dehumidifying operation with a large dew-proofing effect is performed, and when the evaluation differential temperature value ΔT is large, step-by-step dew-condensing operation switching is performed such that dew-proofing control is impossible and operation is stopped By doing so, it is possible to suppress energy consumption in the dew prevention control while maintaining the dew condensation prevention function.

  Since the configurations of the desiccant air conditioner and the dew proof device of the third embodiment are the same as those shown in FIGS. Further, regarding the operation of the dew proofing device, the portions described in the flowchart of FIG. 4 are the same as those in the first embodiment, and thus the description thereof is omitted. The third embodiment is different from the first embodiment in the operation of the summer condensation prevention operation (step S3 in FIG. 4) and the winter condensation prevention operation (step S5 in FIG. 4). The third embodiment is also characterized in that the condensation prevention operation is executed by switching to the condensation prevention control suitable for the magnitude of the evaluation differential temperature value ΔT.

  First, summer condensation prevention operation will be described. FIG. 9 is a flowchart illustrating the operation of the dew protection device in the summer dew condensation prevention operation according to the third embodiment.

First, in step S51, the dew point temperature calculating means 35 calculates the dew point temperature T _{dewout of the} outside air from the outside air temperature T _out and the outside air humidity ρ _out . The method for calculating the dew point temperature T _dewout is as described in the first embodiment (see the description of step S11).

Next, in step S52, anti-condensation control means 36 calculates the differential temperature ΔT obtained by subtracting the inside air temperature T _in the outdoor air dew-point temperature T _Dewout as the evaluation difference temperature value.

Next, in step S53, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is equal to or greater than the first threshold value ΔT _th1 . Here, if ΔT <ΔT _th1 , the dew prevention control means 36 continues the normal ventilation operation as it is (S54), and ends the summer condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th1 , it is determined that condensation may occur, and the process proceeds to the next step S55.

In step S55, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is not less than the first threshold value ΔT _{th1 and} less than the second threshold value ΔT _th2 . Here, in the case of ΔT _th1 ≦ ΔT <ΔT _th2 , the dew prevention control means 36 switches the desiccant air conditioner 1 to the exhaust operation (S56), and ends the summer condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th2 , the process proceeds to the next step S57.

In step S57, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is equal to or greater than the second threshold value ΔT _{th2 and} less than the third threshold value ΔT _th3 . Here, in the case of ΔT _th2 ≦ ΔT <ΔT _th3 , the dew proof control means 36 switches the desiccant air conditioner 1 to an operation state in which the exhaust operation and the dehumidification operation are alternately switched at regular intervals ( S58), summer condensation prevention operation is terminated. On the other hand, if ΔT ≧ ΔT _th3 , the process proceeds to the next step S59.

In step S59, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is not less than the third threshold value ΔT _{th3 and} less than the fourth threshold value ΔT _th4 . Here, in the case of ΔT _th3 ≦ ΔT <ΔT _th4 , the dew proof control means 36 switches the desiccant air conditioner 1 to the dehumidifying operation (S60) and ends the summer dew condensation preventing operation. On the other hand, in the case of ΔT ≧ ΔT _th4 , it is determined that condensation cannot be prevented only by dehumidification control, the operation of the desiccant air conditioner 1 is stopped (S61), and the summer condensation prevention operation is terminated.

  Next, winter condensation prevention operation will be described. FIG. 10 is a flowchart illustrating the operation of the dew protection device in the winter dew condensation prevention operation according to the third embodiment.

First, in step S71, the dew point temperature calculating means 35 calculates the dew point temperature T _dewin of the inside air from the inside air temperature T _in and the inside air humidity ρ _in . The method for calculating the dew point temperature T _dewin of the inside air is as described in the first embodiment (see the description of step S11).

Next, in step S72, the dew prevention control means 36 calculates a temperature difference ΔT obtained by subtracting the outside air temperature T _out from the inside air dew point temperature T _dewin as an evaluation temperature difference value.

Next, in step S73, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is equal to or greater than the first threshold value ΔT _th1 . Here, when ΔT <ΔT _th1 , the dew prevention control unit 36 continues the normal ventilation operation as it is (S74), and ends the winter condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th1 , it is determined that condensation may occur, and the process proceeds to the next step S75.

In step S75, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is not less than the first threshold value ΔT _{th1 and} less than the second threshold value ΔT _th2 . Here, in the case of ΔT _th1 ≦ ΔT <ΔT _th2 , the dew prevention control means 36 switches the desiccant air conditioner 1 to the exhaust operation (S76) and ends the winter condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th2 , the process proceeds to the next step S77.

In step S77, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is not less than the second threshold value ΔT _{th2 and} less than the third threshold value ΔT _th3 . Here, in the case of ΔT _th2 ≦ ΔT <ΔT _th3 , the dew proof control means 36 switches the desiccant air conditioner 1 to an operation state in which the exhaust operation and the dehumidification operation are alternately switched at regular intervals ( S78), the winter condensation prevention operation is terminated. On the other hand, if ΔT ≧ ΔT _th3 , the process proceeds to the next step S79.

In step S79, the dew prevention control means 36 determines whether or not the evaluation differential temperature value ΔT is not less than the third threshold value ΔT _{th3 and} less than the fourth threshold value ΔT _th4 . Here, in the case of ΔT _th3 ≦ ΔT <ΔT _th4 , the dew prevention control means 36 switches the desiccant air conditioner 1 to the dehumidifying operation (S80), and ends the winter condensation prevention operation. On the other hand, in the case of ΔT ≧ ΔT _th4 , it is determined that condensation cannot be prevented only by dehumidification control, the operation of the desiccant air conditioner 1 is stopped (S81), and the winter condensation prevention operation is terminated.

  As described above, when it is determined that it is necessary to prevent dew condensation, if the evaluation differential temperature value ΔT is relatively small, an exhaust operation is performed in which the dew prevention effect is small but the energy consumption is small. When the temperature value ΔT is large, the exhaust operation and the dehumidifying operation are performed alternately. When the evaluation differential temperature value ΔT is further large, the dehumidifying operation having a large dew-proof effect is performed, and when the evaluation differential temperature value ΔT is large. It is possible to reduce energy consumption in dew prevention control while maintaining the dew condensation prevention function by switching the dew condensation prevention operation more finely and gradually, such as stopping operation because dew prevention control is impossible It becomes.

It is a figure which shows the whole structure of a desiccant air conditioner provided with the dew prevention apparatus which concerns on Example 1 of this invention. It is a block diagram showing the hardware constitutions of the control circuit of the desiccant air conditioner 1 of FIG. It is a block diagram showing the functional structure of the dew prevention apparatus of the desiccant air conditioner 1 of FIG. It is a flowchart showing operation | movement of the dew prevention apparatus of the desiccant air conditioner. 3 is a flowchart illustrating the operation of the dew proof device in the summer dew condensation prevention operation according to the first embodiment. 3 is a flowchart showing the operation of the dew prevention device in the winter dew condensation prevention operation according to the first embodiment. 6 is a flowchart showing the operation of a dew prevention device in a summer dew condensation prevention operation according to a second embodiment. 6 is a flowchart illustrating the operation of a dew proof device in a winter dew condensation prevention operation according to a second embodiment. 6 is a flowchart showing the operation of a dew proof device in a summer dew condensation prevention operation according to a third embodiment. 6 is a flowchart showing the operation of a dew proof device in a winter condensation prevention operation according to a third embodiment. It is a figure which shows the structure of the typical desiccant air conditioner of patent document 1.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Desiccant air conditioner 2 Housing 3,4,5 Bulkhead A 1st ventilation path B 2nd ventilation path 6 Regenerative air inlet 7 Regenerated air outlet 8 Process air inlet 9 Process air outlet 10 1st blower 11 Second blower 12 Sensible heat exchanger 13 Regenerative heater 13a Thermal valve 13b Heat exchanger temperature sensor 14 Latent heat rotor 15 Inside air temperature humidity sensor 16 Outside air temperature humidity sensor 17 Control panel 18 Rotor motor 19 Remote control 21 A / D converter 22 Input circuit 23 Central processing unit 24 Memory 25 Timer 26 Output circuit 31 Inside air temperature detecting means 32 Inside air humidity detecting means 33 Outside air temperature detecting means 34 Outside air humidity detecting means 35 Dew point temperature calculating means 36 Dew prevention control means

Claims (6)

A first ventilation path and a second ventilation path communicating the air-conditioned space and the outside air space;
A first blower for circulating the air in the air-conditioned space to the outside air space through the first ventilation path;
A second blower that circulates the air in the outside air space to the air-conditioned space through the second ventilation path;
A sensible heat exchanger that exchanges heat between the air flowing through the first ventilation path and the air flowing through the second ventilation path;
Moisture in the air flowing into the sensible heat exchanger through the second ventilation path is adsorbed, and the moisture flows into the sensible heat exchanger through the first ventilation path. A latent heat rotor that discharges to
A regenerative heater for heating air flowing into the latent heat rotor through the first ventilation path;
In a desiccant air conditioner comprising: a dew proof device for preventing condensation in the sensible heat exchanger,
Temperature of air-conditioned space (hereinafter referred to as "shy temperature.") And the inside air temperature detection means for detecting a T _in,
An inside air humidity detecting means for detecting the humidity (hereinafter referred to as “inside air humidity”) ρ _{in the} air-conditioned space;
An outside air temperature detecting means for detecting the temperature of the outside air space (hereinafter referred to as “outside air temperature”) T _out ;
An outside air humidity detecting means for detecting the humidity of the outside air space (hereinafter referred to as “outside air humidity”) ρ _out ;
A dew-point temperature calculating means for calculating the internal air of dew point temperature T _Dewin from the outside air temperature T _out and calculates the outdoor air dew-point temperature T _Dewout from ambient humidity [rho _out, or the inside air temperature T _in and the room air humidity [rho _in,
In the latent rotor and the regeneration heater stops with the operating and ventilation operation said first and second fan status, differential temperature or the from the outside air dew point temperature T _Dewout minus the room air temperature T _in When the differential temperature obtained by subtracting the outside air temperature T _out from the dew point temperature T _{dewin of the} inside air (hereinafter referred to as “evaluation differential temperature value”) exceeds a predetermined threshold, the second blower is stopped and the first air blower is stopped. Dew prevention control means for performing control to perform either exhaust operation for operating only the blower or dehumidification operation for operating the first and second blowers to operate the latent heat rotor and the regenerative heater;
A dew proofing device characterized by comprising: The dew prevention control means includes
2. The control according to claim 1, wherein when the evaluation differential temperature value exceeds a predetermined threshold in the ventilation operation state, control is performed to alternately execute the exhaust operation and the dehumidifying operation at predetermined time intervals. Dew proof device. The dew prevention control means includes
In the state of the ventilation operation,
If the evaluation difference temperature value exceeds the first threshold temperature T _1, to execute the pumping operation,
2. The dew proof according to claim 1, wherein when the evaluation differential temperature value exceeds a _second threshold temperature T ₂ higher than the first threshold temperature T ₁ , the dehumidifying operation is controlled. apparatus. The dew prevention control means includes
In the state of the ventilation operation,
If the evaluation difference temperature value exceeds the first threshold temperature T _1, to execute the pumping operation,
The evaluation difference temperature value, when it exceeds the first threshold temperature T ₂ higher second than the threshold temperature T _1, alternately to execute the dehumidifying operation and the exhaust operation at predetermined time intervals,
The evaluation difference temperature value, when exceeding the second third threshold temperature T ₃ higher than the threshold temperature T _2, according to claim 1, wherein the continuously performing control to execute the dehumidifying operation Dew protection device. The dew prevention control means includes
In the state of the ventilation operation,
The evaluation difference temperature value, the second threshold temperature T _2, when it exceeds a higher fourth threshold temperature T ₄ than the third threshold temperature T _3, to stop the first and second blower The dew proof device according to claim 3 or 4.   A desiccant air conditioner comprising the dew proof device according to any one of claims 1 to 5.

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