JP2008151460A - Desiccant air conditioner and its dew protection device - Google Patents

Abstract

The present invention provides a desiccant device for a desiccant air conditioner for preventing dew condensation from occurring in a sensible heat exchanger during ventilation operation.
In A latent rotor 15 and regeneration heater 13 stops the first and second blowers 10 and 11 of ventilation operation being actuated state, minus the room air temperature T _in the outdoor air dew-point temperature T _Dewout When the temperature difference (evaluation temperature difference value) exceeds a predetermined threshold value, the first air blower 10 is stopped and only the second air blower 11 is operated, or the first and second air blowers 10 and 11 are operated. A dew proof control means is provided for performing control to operate and perform either of the purge operation for operating the latent heat rotor 15 and the purge heater 14.
[Selection] Figure 1

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 or humidifies the outside air to be taken into the air-conditioned space. A desiccant air conditioner is equipped with a honeycomb-structured latent heat rotor carrying a desiccant (desiccant) such as silica gel or zeolite powder, and dehumidifies or humidifies by adsorbing or desorbing moisture to the latent heat rotor. It is an adsorption type dehumidifier (see, for example, Patent Documents 1 and 2, Non-Patent Documents 1 and 2).

  FIG. 11 is a diagram illustrating a configuration of a desiccant air conditioner described in Patent Document 1. The desiccant air conditioner 100 includes a housing 101. Inside the housing 101, a sensible heat exchanger 102, a desiccant rotor (latent heat rotor) 103, heaters 104 and 105, coolers 106 and 107, blowers 108 and 109, a heat pump 110, And expansion valves 111 and 112. The heat pump 110 includes a compressor 113 and a three-way valve 114.

  The indoor air RA, which is an air-conditioned space, is circulated in the ventilation path 121 by the blower 109, and is blown in the order of the sensible heat exchanger 102, the blower 109, the heater 104, the desiccant rotor 103, and the cooler 106, and is sent to the outside. Is done. On the other hand, the outdoor air OA is circulated through the ventilation path 122 by the blower 108 and introduced into the ventilation path 122, and is blown in the order of the sensible heat exchanger 102, the blower 108, the heater 105, the desiccant rotor 103, and the cooler 107. And sent to the room.

  In the dehumidifying operation, the direction of the three-way valve 114 is set so that the compressor 113 and the cooler 107 communicate with each other. Thereby, the cooler 107 and the heater 104 are operated by the operation of the compressor 113, and heat is deprived from the air by the cooler 107, and this heat is heated to the air by the heater 104.

  The indoor air RA introduced into the ventilation path 121 is heated by exchanging heat with the air in the ventilation path 122 in the sensible heat exchanger 102, and the enthalpy increases. And it passes along the air blower 109, is sent to the heater 104, is heated to 45-60 degreeC, and relative humidity falls. The discharged air whose relative humidity is reduced flows into the desiccant rotor 103 and removes moisture from the desiccant rotor 103. As a result, the desiccant rotor 103 is dehumidified and regenerated. The discharged air that has passed through the desiccant rotor 103 is sent to the cooler 106. At the time of cooling, the cooler 106 is stopped, and the discharged air passes through the cooler 106 as it is and is discharged outside the room.

  On the other hand, the outdoor air OA introduced into the ventilation path 122 is cooled by exchanging heat with the air in the ventilation path 121 in the sensible heat exchanger 102, and enthalpy is lowered. Then, it is sent to the heater 105 through the blower 108. During cooling, the heater 105 is stopped, and the air in the ventilation path 122 passes through the heater 105 as it is and flows into the desiccant rotor 103. In the desiccant rotor 103, moisture in the air in the ventilation path 122 is adsorbed by the desiccant rotor 103 and dehumidified. The discharged air that has passed through the desiccant rotor 103 is sent to the cooler 107. During cooling, the cooler 107 is in operation, and the discharged air is deprived of heat and cooled by the cooler 107 and discharged into the room.

  In the humidifying operation, the direction of the three-way valve 114 is set so that the compressor 113 and the heater 105 communicate with each other. Accordingly, the cooler 106 and the heater 105 are operated by the operation of the compressor 113, and heat is deprived from the air by the cooler 106, and this heat is heated to the air by the heater 105.

  The indoor air RA introduced into the ventilation path 121 is cooled by exchanging heat with the air in the ventilation path 122 in the sensible heat exchanger 102, and the enthalpy is lowered. Then, it is sent to the heater 104 through the blower 109. At this time, since the heater 104 is in a stopped state, the discharged air passes through the heater 104 as it is and is sent to the desiccant rotor 103. The moisture of the air flowing into the desiccant rotor 103 is adsorbed by the desiccant rotor 103 and dehumidified. The discharged air that has passed through the desiccant rotor 103 is sent to the cooler 106. At the time of heating, the cooler 106 is operated, and the discharged air is deprived of heat and cooled by the cooler 106 and discharged to the outside.

On the other hand, the outdoor air OA introduced into the ventilation path 122 is heated by exchanging heat with the air in the ventilation path 121 in the sensible heat exchanger 102, and the enthalpy increases. Then, it is sent to the heater 105 through the blower 108. In the heater 105, the air in the ventilation path 122 is heated and flows into the desiccant rotor 103 to remove moisture from the desiccant rotor 103. As a result, the desiccant rotor 103 is dehumidified and regenerated. The discharged air that has passed through the desiccant rotor 103 is sent to the cooler 107. During heating, the cooler 107 is stopped, and the discharged air passes through the cooler 107 as it is and is discharged indoors.
Japanese Patent Laid-Open No. 10-205820 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 100 also performs “ventilation operation” in addition to “humidification operation” and “dehumidification operation”. “Ventilation operation” means indoor air without humidification or dehumidification by operating only the blowers 108 and 109 while the heaters 104 and 105, the coolers 106 and 107, and the desiccant rotor 103 are stopped. And the operation which ventilates outdoor air.

  In the ventilation operation, when the temperature difference between the outdoor air and the indoor air is large, high-temperature air containing moisture flows into the sensible heat exchanger 102 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 102, dew condensation occurs in the sensible heat exchanger 102. Therefore, drain water is generated in the sensible heat exchanger 102 in 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 102.

  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, there has been a demand for a technique for preventing the generation of drain water in the sensible heat exchanger during ventilation operation.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a desiccant device for a desiccant air conditioner for preventing dew condensation in a sensible heat exchanger during ventilation operation.

The first configuration of the dew protection device for a desiccant air conditioner according to the present invention includes a first ventilation path and a second ventilation path communicating the air-conditioned space and the outside air space, and the outside air through the first ventilation path. A first blower that circulates air in the space to the conditioned space, a second blower that circulates air in the conditioned space to the outside air 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. A regenerative heater for heating the air to be discharged, and the latent heat low through the second ventilation path A desiccant air conditioner equipped with a purge heater that heats air flowing into the sensible heat exchanger is a dew prevention device that prevents condensation in the sensible heat exchanger, and is referred to as the temperature of the air-conditioned space (hereinafter referred to as “inside air temperature”). ) Inside air temperature detecting means for detecting T _in , humidity of the air-conditioned space (hereinafter referred to as “inside air humidity”), inside air humidity detecting means for detecting ρ _in and temperature of the outside air space (hereinafter referred to as “outside air temperature”) T _Outside air temperature detecting means for detecting _out , outside air space humidity (hereinafter referred to as “outside air humidity”) ρ _out , and outside air temperature T _out and outside air humidity ρ _out from the outside dew point temperature T _{Dew point} is calculated, or dew point temperature calculating means for calculating 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 latent heat rotor, the regenerative heater and the purge heater are stopped and the first 1 and 2 In the state of the ventilation operation that operates the wind machine, by subtracting the outside air temperature T _out from the dew-point temperature T _Dewin the differential temperature or the inside air by subtracting the inside air temperature T _in from the outside air dew-point temperature T _Dewout differential temperature ( (Hereinafter referred to as “evaluation differential temperature value”) exceeds a predetermined threshold value, the first air blower is stopped and only the second air blower is operated, or the first and second air blowers are turned on. And a dew proof control means for performing a control to operate and perform any one of a purge operation for operating the latent heat rotor and the purge heater.

  According to this configuration, in the ventilation operation state, the dew prevention control means performs control to execute either the exhaust operation or the purge operation when the evaluation differential temperature value exceeds a 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 first ventilation path is cooled while flowing through the first ventilation path. And if it cools below to the dew point temperature _{Tdewout of} external air, dew condensation will arise in a 1st ventilation path. The magnitude of the temperature drop of the air while circulating in the first ventilation path becomes larger as the inside air temperature becomes lower. 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 condensation may occur in the first ventilation path when the evaluation differential temperature value ΔT exceeds the “predetermined threshold value”, and either the exhaust operation or the purge operation is determined. To execute.

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

  When the purge operation is performed, the first and second blowers are operated to operate the latent heat rotor and the purge heater. As a result, the air that has flowed into the first 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 second ventilation path is heated by the purge heater. Accordingly, the moisture adsorbed on the latent heat rotor is desorbed and released to the air in the second ventilation path. Here, the heat of the air flowing through the heated second ventilation path is partially absorbed by the latent heat rotor, but becomes higher than the temperature of the air-conditioned space. Therefore, by adjusting the heating temperature of the purge heater, it becomes possible to keep the temperature of the air in the second ventilation path that circulates through the sensible heat exchanger above the dew point temperature, thereby preventing condensation in the sensible heat exchanger. be able to.

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 second ventilation path is cooled while flowing through the second ventilation path. And if it cools below the dew point temperature _{Tdewin of} inside air, dew condensation will arise in a 2nd ventilation path. The magnitude of the temperature drop of the air while flowing through the second 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 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 performs exhaust operation, humidification operation, or purge. Either of driving is executed.

  When the exhaust operation is performed, the first blower is stopped and only the second blower is operated. Thereby, since the inflow of cold outside air into the first ventilation path is eliminated, the sensible heat exchanger is not cooled by the air flowing into the first ventilation path. Therefore, the temperature drop of the temperature rise of the sensible heat exchanger and the temperature of the air in the second ventilation path in the sensible heat exchanger can be reduced. This prevents condensation in the second ventilation path of the sensible heat exchanger.

  When the purge operation is performed, the first and second blowers are operated to operate the latent heat rotor and the purge heater. Thereby, since the air which flowed into the 2nd ventilation path is heated by a purge heater, the temperature of the air which distribute | circulates the 2nd ventilation path in a sensible heat exchanger rises, and saturated water vapor amount also becomes large. 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 “purge heater” is a heating device that heats the air flowing from the sensible heat exchanger to the latent heat rotor through the second ventilation path. As the purge 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 regeneration heater and the purge 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.

  The “exhaust operation” refers to an operation in which the first blower is stopped and only the second 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.

  “Purge operation” is an operation that removes odorous components adsorbed on the rotor, and operates the first and second blowers, stops the regenerative heater, and operates the latent heat rotor and purge heater. Say. In the purge 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 odor component adsorbed on the rotor together with the humidity of the supplied outside air is , Moved to exhausted inside air. The purge operation is usually performed prior to the humidification / ventilation operation.

  The “humidification operation” refers to an operation in which the first and second blowers are operated, the purge heater is stopped, and the latent heat rotor and the regenerative heater are operated. In the humidification 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 exhausted inside air is transferred to the outside air to be aired. By performing such a humidification operation, the humidity on the downstream side of the latent heat rotor in the ventilation path B is lowered, and it is possible to prevent dew condensation even if cold outside air flows into the sensible heat exchanger.

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 purge operation or the humidification operation are alternately controlled 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 is consumed in the purge operation or the humidification operation. Energy can be saved.

  That is, dew condensation in the sensible heat exchanger can be more effectively prevented when the purge operation is performed than when the exhaust operation is performed. Therefore, in order to obtain the maximum dew-proof effect, the purge operation may be performed continuously. However, in the purge operation or humidification operation, in order to operate the heater, it is necessary to supply thermal energy to the heater. Accordingly, the purge operation or the humidification operation consumes more energy than the exhaust operation. The purging operation in this case is not intended to remove the odorous component adsorbed on the rotor.

  Therefore, by alternately executing the exhaust operation and the purge operation or the humidification 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. 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 purge operation or humidification operation is performed. It is characterized by performing control to be executed.

  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 purge operation are performed. or alternately to execute the humidifying operation at predetermined time intervals, the evaluation difference temperature value, when it exceeds a third threshold temperature T ₃ higher than the second threshold temperature T _2, the purge operation or the humidifying operation It is characterized by performing control to be executed continuously.

  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.

  Thus, when the evaluation differential temperature value is large and it is difficult to prevent dew condensation even by the purge operation or the humidification operation, dew condensation in the sensible heat exchanger is stopped by stopping the first and second blowers. Can be prevented.

  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 means performs either the exhaust operation, the purge operation, or the humidification operation when the evaluation differential temperature value exceeds the predetermined threshold value. By performing the control, 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 processing air suction port 8 that is an air supply port for the inside air of the second ventilation path B and a regeneration air outlet 7 that is an exhaust port of the first ventilation path A are formed. Has been. In addition, on the side surface of the housing 2 facing the outside air space, a regeneration air suction port 6 that is an air supply port for outside air in the first ventilation path A and a processing air outlet 9 that is an exhaust port for the second ventilation path B are provided. Is formed.

  Further, inside the housing 2, a first blower 10, a second blower 11, a sensible heat exchanger 12, a regeneration heater 13, a thermal valve 13 a, a regeneration heat exchange temperature sensor 13 b, a purge heater 14, heat A valve 14a, a purge heat exchanger temperature sensor 14b, a latent heat rotor 15, an inside air temperature humidity sensor 16, an outside air temperature humidity sensor 17, and a control panel 18 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 outside air space to the air-conditioned 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 distributes the air in the air-conditioned space to the outside air 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 15 adsorbs moisture in the air flowing into the sensible heat exchanger 12 through the second ventilation path B (or the first ventilation path A), and the moisture is absorbed into the first ventilation path A ( Or it discharge | releases in the air which flows out out of the sensible heat exchanger 12 through the 2nd ventilation path B). The latent heat rotor 15 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 19 (see FIG. 2).

  The regenerative heater 13 is a heat exchanger that heats air flowing into the latent heat rotor 15 through the first ventilation path A. As a result, the side of the first ventilation path A of the latent heat rotor 15 is heated, moisture adsorbed on the latent heat rotor 15 is desorbed, the latent heat rotor 15 is dehumidified, and the air flowing through the first ventilation path A Is humidified.

  The purge heater 14 is a heat exchanger that heats the air flowing into the latent heat rotor 15 through the second ventilation path B. As a result, the side of the second ventilation path B of the latent heat rotor 15 is heated, the moisture adsorbed on the latent heat rotor 15 is desorbed, the dehumidification of the latent heat rotor 15 is performed, and the air flowing through the second ventilation path B Is humidified.

  Note that when one of the regeneration heater 13 and the purge heater 14 is operating, the other is stopped.

  The thermal valve 13 a is a valve that disconnects hot water supplied to the regenerative heater 13. The regenerative heat exchanger temperature sensor 13 b is a temperature sensor that detects the temperature of hot water supplied to the regenerative heater 13. The thermal valve 14 a is a valve that disconnects the hot water supplied to the purge heater 14. The purge heat exchanger temperature sensor 14 b is a temperature sensor that detects the temperature of hot water supplied to the purge heater 14.

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

  The outside air temperature / humidity sensor 17 is installed in the vicinity of the regenerative air inlet 6 of the first ventilation path A. The outside air temperature / humidity sensor 17 is a sensor that detects the temperature and humidity of the air (outside air) in the outside air space that flows into the first ventilation path A from the regeneration air suction port 6.

  Based on the temperatures and humidity detected by the regenerative heat exchanger temperature sensor 13b, the purge heat exchanger temperature sensor 14b, the internal air temperature / humidity sensor 16, and the external air temperature / humidity sensor 17, the control panel 18 performs the first blower 10 and the second The circuit board for controlling the operation of the blower 11, the thermal valves 13 a and 14 a, and the latent heat rotor 15.

[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, a first blower 10, a second blower 11, a thermal valve 13a, a regenerative heat exchanger temperature sensor 13b, a thermal valve 14a, a purge heat exchanger temperature sensor 14b, an internal air temperature humidity sensor 16, and an external air temperature humidity sensor. 17 and the control panel 18 are the same as those in FIG.

  The desiccant air conditioner 1 includes a rotor motor 19 and a remote controller 20. As described above, the rotor motor 19 is a motor that rotationally drives the latent heat rotor 15 at a low speed. The remote controller 20 is an input device for a user to input an operation instruction to the desiccant air conditioner 1.

  The control panel 18 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.

  The analog temperature detection signal or humidity detection signal output from the regenerative heat exchange temperature sensor 13b, the purge heat exchange temperature sensor 14b, the inside air temperature humidity sensor 16, and the outside air temperature humidity sensor 17 is an A / D converter of the control panel 18. 21 is input. The A / D converter 21 performs AD conversion on these analog signals and outputs them as digital signals to the input circuit 22. The input circuit 22 is an input interface for inputting the digitized temperature detection signal and humidity detection signal and the operation instruction signal from the remote controller 20 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 19, the thermal valves 13 a, 14 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 19, the thermal valves 13 a and 14 a 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, the first blower 10, the second blower 11, the thermal valves 13a and 14a, the internal air temperature / humidity sensor 16, the external air temperature / humidity sensor 17, the control panel 18, and the rotor motor 19 are respectively shown in FIG. This corresponds to the same reference numerals in FIG.

  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 16. The inside air temperature detecting means 31 and the inside air humidity detecting means 32 are realized by the outside air temperature / humidity sensor 17. The dew point temperature calculation means 35 and the dew prevention control means 36 are realized by the control panel 18.

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 dew condensation of the sensible heat exchanger 12 by controlling the first blower 10, the second blower 11, the thermal valves 13 a and 14 a, and the rotor motor 19. .

[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 regeneration heater 13, the purge heater 14, and the latent heat rotor 15 are in a stopped state. At this time, the air in the air-conditioned space is exhausted as it is to the outside air space through the second ventilation path B, and the air in the outside air space is directly supplied to the air-conditioned space through the first ventilation path A. 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 16 (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 17 (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 first ventilation path A is cooled to near the inside 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. 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 that condensation will occur, performs a dew condensation prevention control operation (S15), and ends the summer dew 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 operation”, the dew prevention control means 36 performs any one of the following controls (1) to (3).

(1) The operation of the first blower 10 is stopped, and an exhaust operation state in which only the second blower 11 is operating is set. In this case, since high temperature and high humidity outside air does not flow into the first ventilation path A side of the sensible heat exchanger 12, dew condensation in the sensible heat exchanger 12 can be prevented.
(2) While operating the 1st air blower 10 and the 2nd air blower 11, the thermal valve 14a is opened, the purge heater 14 is operated, the rotor motor 19 is started, and the latent heat rotor 15 is made. The purge operation is activated. 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 purge heater 14. Therefore, in the sensible heat exchanger 12, the temperature drop width of the air flowing through the first ventilation path A 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 second ventilation path B 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 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. 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, when ΔT> ΔT _th , the dew prevention control means 36 determines that there is a possibility of causing condensation, performs the condensation prevention control operation (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 operation”, the dew prevention control means 36 performs any one of the following controls (1) to (3).

(1) The operation of the first blower 10 is stopped, and an exhaust operation state in which only the second blower 11 is operating is set. In this case, since low temperature outside air does not flow into the first ventilation path A side of the sensible heat exchanger 12, dew condensation in the sensible heat exchanger 12 can be prevented.
(2) While operating the 1st air blower 10 and the 2nd air blower 11, the thermal valve 14a is opened, the purge heater 14 is operated, the rotor motor 19 is started, and the latent heat rotor 15 is made. Set the dehumidifying operation to work. 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 purge heater 14. Therefore, in the sensible heat exchanger 12, even if the temperature of the air flowing through the second ventilation path B drops, the temperature becomes the dew point temperature or more, 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 purge operation (S38) and ends the summer dew condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th3 , it is determined that condensation cannot be prevented only by purge 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 purge operation (S48), and ends the winter condensation prevention operation. On the other hand, when ΔT ≧ ΔT _th3 , it is determined that condensation cannot be prevented only by purge 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, a purge operation with a large dew prevention effect is performed, and when the evaluation differential temperature value ΔT is further large, the dew condensation prevention operation is switched step by step such that the dew prevention control is impossible and the 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. In the third embodiment, the operations of the summer condensation prevention operation (step S3 in FIG. 4) and the winter condensation prevention operation (step S5 in FIG. 4) are different from those in the first and second embodiments. 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 prevention control unit 36 switches the desiccant air conditioner 1 to an operation state in which the exhaust operation and the purge 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 prevention control means 36 switches the desiccant air conditioner 1 to the purge operation (S60), and ends the summer condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th4 , it is determined that condensation cannot be prevented only by the purge 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 prevention control unit 36 switches the desiccant air conditioner 1 to an operation state in which the exhaust operation and the purge 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 purge operation (S80) and ends the summer condensation prevention operation. On the other hand, if ΔT ≧ ΔT _th4 , it is determined that condensation cannot be prevented only by purge 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 purge operation are performed alternately. When the evaluation differential temperature value ΔT is further large, the purge operation with 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 showing the structure of the 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 air blower 12 Sensible heat exchanger 13 Regenerative heater 13a Thermal valve 13b Regenerative heat exchanger temperature sensor 14 Purge heater 14a Thermal valve 14b Purge heat exchanger temperature sensor 15 Latent heat rotor 16 Internal air temperature humidity sensor 17 External air temperature humidity sensor 18 Control Panel 19 Rotor / Motor 20 Remote Control 21 A / D Converter 22 Input Circuit 23 Central Processing Unit 24 Memory 25 Timer 26 Output Circuit 31 Inside Air Temperature Detection Means 32 Inside Air Humidity Detection Means 33 Outside Air Temperature Detection Means 34 Outside Air Humidity Detection Means 35 Dew point temperature calculation 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 that circulates air in the outside air space to the air-conditioned space through the first ventilation path;
A second blower for circulating air in the air-conditioned space to the outside air 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;
A purge heater for heating air flowing into the latent heat rotor through the second 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,
The latent rotor, in the state of ventilation operation that the stops regeneration heater and the purge heater operating said first and second blowers, subtracting the inside air temperature T _in from the outside air dew point temperature T _Dewout When the temperature difference or the temperature difference 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 temperature difference value”) exceeds a predetermined threshold, the first blower is stopped. Thus, it is possible to prevent the exhaust operation for operating only the second blower or the purge operation for operating the first and second blowers to operate the latent heat rotor and the purge heater. Dew control means;
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 purge 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 that is higher than the first threshold temperature T ₁ , the purge operation is performed. 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 purge operation and the exhaust operation at predetermined time intervals,
The evaluation difference temperature value, when it exceeds a third threshold temperature T ₃ higher than the second threshold temperature T _2, according to claim 1, wherein the continuously performing control to execute the purge operation Dew protection device. The dew prevention control means includes
In the state of the ventilation operation,
When the evaluation differential temperature value exceeds the second threshold temperature T ₂ and the fourth threshold temperature T ₄ higher than the third threshold temperature T ₃ , the first and second blowers are stopped. The dew proofing device according to claim 3 or 4, characterized in that.   A desiccant air conditioner comprising the dew proof device according to any one of claims 1 to 5.

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