JP3873218B2 - Constant temperature and humidity air conditioning method - Google Patents

Description

  The present invention relates to an air conditioning method for maintaining a target room in a constant temperature and humidity state, and more specifically, heating and humidifying air once supercooled by a conventional air cooler to a temperature and humidity suitable for a cooling load in the target room. The temperature detector and humidity that were installed only in the target room are improved by improving the method of blowing air into the target room as air at a constant air flow, omitting the heating and humidification process immediately after the air cooler or cooling coil. Install the detector or only the temperature detector in front of the air blower outlet that blows air into the target room, and control the cooling capacity of the air cooler or cooling coil and the air volume of the blower simultaneously or individually. The state room (temperature and humidity) of the air to be blown into the target room is made constant, and the air is blown into the target room with an air volume corresponding to the cooling load in the target room. Held in a constant temperature and humidity conditions, to a good constant temperature and humidity conditioning method extremely energy efficient.

  That is, in brief, in the conventional constant temperature and humidity air conditioning method, the state point of the air to be blown is changed by the process of cooling, heating and humidification according to the change of the cooling load in the target room, and the air is blown with a constant air volume. However, the present invention eliminates the heating and humidification process immediately after the cooling coil, makes the state point of the air to be blown constant, and changes the air volume of the blown air according to the change in the cooling load in the target room. This is an epoch-making method that focuses on the variable air volume, which is a so-called blind spot of the conventional constant temperature and humidity air conditioning method. is there.

However, when the cooling load in the target room becomes extremely small, a method of slightly heating and humidifying with a heater and a humidifier installed at the subsequent stage of the blower is also included.

  Conventionally, a method as shown in a circuit diagram of FIG. 8 has been known as an air conditioning method for keeping a target room in a constant temperature and humidity state.

In FIG. 8, R ′ is a target room, 1D is an air conditioner, and an air cooler 2D, a heater 6D, a humidifier 7D, and a blower 3D are stored in a package 1Da. The air cooler 2D includes a compressor 2Da and a cooling coil 2Db.

4D is a temperature detector (dry bulb temperature detector) installed in the target room, 5D is a humidity detector installed in the target room, 8D is a blower port for blowing air from the blower 3D into the target room R ′, 9Da is an outside air intake port for taking in outside air, and 9Db is an air recirculation port for returning the air in the target room into the air conditioner 1D .

  10Da is a blower duct that guides outside air taken in from the outside air intake 9Da to the air cooler 2D, and 10Db is a blower duct that guides air taken from the air recirculation port 9Db to the air cooler 2D.

11Da is an air duct that guides air from the air cooler 2D to the heater 6D, 11Db is an air duct that guides air from the heater 6D to the humidifier 7D, and 12D is an air duct that guides air from the humidifier 7D to the fan 3D. , 13D is an air duct that guides air from the blower 3D to the air outlet 8D.

14D is a temperature information transmission path for transmitting temperature information from the temperature detector 4D to the heater 6D, and 15D is a humidity information transmission path for transmitting humidity information from the humidity detector 5D to the humidifier 7D.

The operation of the conventional air conditioning method having the above configuration will be described with reference to the circuit diagram of FIG. 8 and the air diagram of FIG. In the air diagram of FIG. 9, the horizontal axis represents dry bulb temperature and the vertical axis represents absolute humidity.

In the air diagram of FIG. 9, D0 is the outside air state point, D1 is the air state point of the target room R ′, and D1 is also the desired air state point. The following description will be made assuming that the SHF (sensible heat ratio) is 0.9.

The air at the state point D0 (outside air) is taken in from the outside air intake port 9Da, and the air at the state point D1 (air in the target room R ′) is taken in from the air recirculation port 9Db and mixed to be air at the state point D2 (mixed) Qi).

The air at the state point D2 is sent to the air cooler 2D to be cooled, passes through the state point D3, and reaches the state point D4. Since the air at the state point D4 is in a supercooled state as compared with the air at the state point D1, it is sent to the heater 6D by the blower duct 11Da and heated to become the air at the state point D5.

Since the air at the state point D5 is in a dehumidified state as compared with the air at the state point D1, it is sent to the humidifier 7D by the blower duct 11Db and humidified to become the air at the state point D6. The air at the state point D6 is air having a temperature and humidity commensurate with the cooling load in the target room R ′.

The air at the state point D6 is sent to the blower 3D by the blower duct 12D, further passes through the blower duct 13D, and is blown into the target chamber R ′ from the blower port 8D.

When the cooling load in the target room R ′ is large, the state point D5 approaches the state point D4, and when the cooling load in the target room R ′ is small, the state point D5 moves away from the state point D4. The cooling load in the target room R ′ is detected by the temperature detector 4D and the humidity detector 5D.

The temperature (dry bulb temperature) information in the target chamber R ′ is detected by the temperature detector 4D and transmitted to the heater 6D through the temperature information transmission path 14D. Further, the humidity information in the target room R ′ is detected by the humidity detector 5D and transmitted to the humidifier 7D through the humidity information transmission path 15D.

In FIG. 9, the air-fuel mixture (state point D2) is supercooled by the air cooler 2D, becomes air at the state point D4, and is sent to the heater 6D via the air duct 11Da as described above.

The control mechanism 6Da is interposed in the path 14D, and the control mechanism 6Da controls the output of the heater 6D according to the temperature information in the target chamber R ′ detected by the temperature detector 4D, so that the state point of FIG. Control the position of D5.

The control mechanism 7Da is interposed in the path 15D, and the control mechanism 7Da controls the output of the humidifier 7D according to the humidity information in the target room R ′ detected by the humidity detector 5D, so that the state point of FIG. Control the position of D6.

The air at the state point D6 is blown into the target chamber R ′ from the blower port 8D by the blower 3D. Since the air at the state point D6 is separated from the state point D1 by the cooling load in the target room R ′, the dry bulb temperature and humidity in the target room R ′ are thereby held at the state point D1.

Due to the above action, the target room R ′ is maintained at a desired temperature and humidity. However, this method has a big problem in terms of energy efficiency.

In this method, as described above, the air once cooled by the air cooler 2D is reheated by the heater 6D and further humidified by the humidifier 7D.

However, if the cooling load in the target room R ′ is large, the state point D5 in FIG. 9 approaches the state point D4 and the heating amount is small, but the cooling load in the target room R ′ is small. The state point D5 is separated from the state point D4, that is, the necessary heating amount is increased.

In short, even when the cooling load in the target room R ′ becomes small, the output of the air cooler 2D does not change and the position of the state point D4 does not change, so that the cooling load in the target room R ′ is small. The more heating is required, the greater the energy loss.

Various methods have been developed to eliminate the above-described energy loss in the conventional air conditioning method, and the method described in Patent Document 1 described below is one of them.

In the method described in Patent Document 1, not only the compressor 2Da of the air cooler 2D has a variable capacity by a control mechanism (not shown) and temperature information in the target chamber R ′ is transmitted to the heater 6D. A temperature detector (not shown) is also installed immediately before the air outlet 8D, temperature information from the detector is transmitted to the air cooler 2D, and the output of the air cooler 2D is controlled by the temperature information. It is.

According to the temperature information, when the cooling load in the target room R ′ is small, the capacity of the compressor 2Da is reduced and the output of the air cooler 2D is reduced. When the cooling load in the target room R ′ is large, the compressor The capacity of 2Da is increased and the output of the air cooler 2D is increased.

Thereby, both the energy consumed by the compressor 2Da and the energy consumed by the heater 6D are suppressed, and the energy consumed by the entire apparatus is saved.
JP 3-168556

  Certainly, in the method described in Patent Document 1, a large energy saving occurred particularly when the cooling load in the target room R ′ was small. However, there are many unimproved parts in this method.

  That is, even in the method described in Patent Document 1, the process of reheating the air once cooled, and further the process of rehumidification remain, and the state in which energy loss occurs in this part is It has not been resolved.

  Therefore, omitting all the heating and humidification steps, the air cooled by the air cooler is simply blown into the target chamber, and the target chamber is kept in a constant temperature and humidity state with a desired temperature and humidity. Development of an air conditioning method that minimizes energy loss was set as a basic problem of the present invention.

  However, in winter when the temperature and humidity setting conditions and the outside air temperature are lower than the temperature in the target room, the heating process and humidification process may not be omitted. The development of an air conditioning method that minimizes the amount of energy was also set as an issue.

  The present invention has been made to solve the above problems, and provides the following Solution 1 to Solution 3 in order to solve the above problems.

<Solution 1>
An air conditioning method for maintaining a target room in a constant temperature and humidity state,
An air cooler,
An outside air intake port for taking air outside the target room into the air cooler;
A blower for blowing the temperature-controlled air into the target room by the air cooler;
A temperature detector for detecting the temperature of the dry bulb in the target room;
A humidity detector that detects the humidity of the target room;
A temperature detector for detecting the dry bulb temperature of air immediately before the blower outlet of the blower;
A humidity detector for detecting the humidity of the air immediately before the air outlet;
A temperature information transmission path and a humidity information transmission path for transmitting dry bulb temperature information and humidity information of the target room to the air cooler and the blower;
A temperature information transmission path and a humidity information transmission path for transmitting the dry bulb temperature information and humidity information of the air immediately before the blower opening to the air cooler and the blower;
A control mechanism for controlling the cooling capacity of the air cooler according to the transmitted dry-bulb temperature information and humidity information of the target room and the dry-bulb temperature information and humidity information of the air immediately before the air blowing port;
A control mechanism for controlling the blowing capacity of the blower according to the transmitted dry-bulb temperature information and humidity information of the target room and the dry-bulb temperature information and humidity information of the air immediately before the blower opening;
With
Control the cooling capacity of the air cooler according to the transmitted dry-bulb temperature information and humidity information of the target room and the dry-bulb temperature information and humidity information of the air immediately before the air outlet,
And by controlling the dry bulb temperature information and humidity information of the transmitted target room and the dry bulb temperature information and humidity information of the air immediately before the blow outlet, the blowing capacity of the blower is controlled,
A constant temperature and humidity control method characterized by maintaining the dry bulb temperature and humidity of a target room at values within a certain range.

<Solution 2>
An air conditioning method for maintaining a target room in a constant temperature and humidity state,
An air cooler,
An outside air intake port for taking air outside the target room into the air cooler;
An air recirculation port for recirculating air in the target room to the air cooler;
A blower for blowing the temperature-controlled air into the target room by the air cooler;
A temperature detector for detecting the temperature of the dry bulb in the target room;
A humidity detector that detects the humidity of the target room;
A temperature detector for detecting the dry bulb temperature of air immediately before the blower outlet of the blower;
A humidity detector for detecting the humidity of the air immediately before the air outlet;
A temperature information transmission path and a humidity information transmission path for transmitting dry bulb temperature information and humidity information of the target room to the air cooler and the blower;
A temperature information transmission path and a humidity information transmission path for transmitting the dry bulb temperature information and humidity information of the air immediately before the blower opening to the air cooler and the blower;
A control mechanism for controlling the cooling capacity of the air cooler according to the transmitted dry-bulb temperature information and humidity information of the target room and the dry-bulb temperature information and humidity information of the air immediately before the air outlet;
A control mechanism for controlling the blowing capacity of the blower according to the transmitted dry-bulb temperature information and humidity information of the target room and the dry-bulb temperature information and humidity information of the air immediately before the blower opening;
With
Control the cooling capacity of the air cooler according to the transmitted dry-bulb temperature information and humidity information of the target room and the dry-bulb temperature information and humidity information of the air immediately before the air outlet,
And by controlling the dry bulb temperature information and humidity information of the transmitted target room and the dry bulb temperature information and humidity information of the air immediately before the blow outlet, the blowing capacity of the blower is controlled,
A constant temperature and humidity control method characterized by maintaining the dry bulb temperature and humidity of a target room at values within a certain range.

<Solution 3>
An air conditioning method for maintaining a target room in a constant temperature and humidity state,
A cooling coil through which cooling water is fed;
A cooling water control mechanism for controlling the amount of cooling water sent to the cooling coil, an outside air intake for taking air outside the target room into the cooling coil, and
An air recirculation port for recirculating air in the target room to the cooling coil;
A blower for blowing air temperature-adjusted by the cooling coil into the target room;
A blower control mechanism for controlling the blower capacity of the blower;
A heater and a humidifier in the subsequent stage of the blower,
A heater control mechanism that controls the heating capacity of the heater, a humidifier control mechanism that controls the humidification capacity of the humidifier, the cooling water control mechanism, the blower control mechanism, the heater control mechanism, and the humidifier control mechanism A switching machine that transmits control information to each of the
A temperature detector for detecting the temperature of the dry bulb in the target room;
A humidity detector that detects the humidity of the target room;
A temperature detector for detecting the dry bulb temperature of the air blown from the blower;
Temperature information transmission path and humidity information transmission path for transmitting dry bulb temperature information of the target room, humidity information of the target room, temperature information of air blown from the blower to the switch,
An information transmission path for transmitting temperature information of air blown from the blower that has passed through the switching machine or temperature information of a target chamber to the cooling water control mechanism;
An information transmission path for transmitting temperature information of air blown from the blower that has passed through the switching machine or temperature information of a target chamber to the heater control mechanism;
An information transmission path for transmitting humidity information of the target room that has passed through the switching machine to the humidifier control mechanism;
With
Control the amount of cooling water in the cooling coil according to the temperature information of the air blown from the blower or the temperature information of the target chamber,
And if necessary, the heating capacity of the heater is controlled based on the temperature information of the air sent from the blower and the temperature information of the target room,
And, if necessary, control the humidifying capacity of the humidifier according to the humidity information of the target room transmitted,
A constant temperature and humidity control method characterized by maintaining the dry bulb temperature and humidity of a target room at values within a certain range.

The main points of the solving means 1 to 3 will be described as follows.
That is, the conventional constant temperature and humidity air conditioning method unconditionally adopts the cooling, heating and humidification processes according to the variation of the cooling load in the target room, and changes the state point of the air blown by this series of processes, Was blowing at constant.

In Solution 1 to Solution 3 of the present invention, the heating and humidification process immediately after the air cooler or the cooling coil is omitted, the state point of the air to be blown is made constant, and the cooling in the target room is performed. We have developed a completely new constant temperature and humidity air conditioning method in which the air volume of the air to be blown is changed according to the load variation to keep the target room in a constant temperature and humidity state.

In the constant temperature and constant humidity air conditioning method of Solution 1 and Solution 2 of the present invention, the heater and the humidifier, which are indispensable in the conventional method, are removed from the rear stage of the air cooler, instead of the blower and the blower port. In between, a temperature detector for detecting the dry bulb temperature of the air blown into the target room and a humidity detector for detecting the humidity are installed.

  Alternatively, in the constant temperature and humidity air conditioning method of Solution 3 of the present invention, the heater and the humidifier that were placed immediately after the air cooler in the conventional method are placed immediately before the air outlet, and the heater and the A temperature detector that detects the dry-bulb temperature of the blown air is installed immediately before the humidifier (that is, immediately after the blower).

  Further, in the conventional method, the information of the temperature detector that detects the dry bulb temperature in the target room is transmitted to the heater. However, in the constant temperature and humidity control method of Solution 1 and Solution 2 of the present invention, Information is transmitted to a control mechanism that controls the cooling capacity of the air cooler and a control mechanism that controls the blowing capacity (air volume) of the blower.

  Alternatively, in the constant temperature and humidity control method of Solution 3 of the present invention, the information of the temperature detector that detects the dry bulb temperature in the target room is normally transmitted to the blower control mechanism that controls the blower ability of the blower. When the indoor cooling load is extremely reduced, the change is transmitted to the cooling water control mechanism for controlling the amount of cooling water in the cooling coil and the heater control mechanism for controlling the heating capacity of the heater.

Moreover, in the conventional method, the information of the humidity detector that detects the humidity in the target room is transmitted to the humidifier. However, in the constant temperature and humidity control method of Solution 1 and Solution 2 of the present invention, the information is It is transmitted to a control mechanism that controls the cooling capacity of the air cooler and a control mechanism that controls the blowing capacity (air volume) of the blower.

  Alternatively, in the constant temperature and humidity control method of Solution 3 of the present invention, the information of the humidity detector for detecting the humidity in the target room controls the humidifying capacity of the humidifier when the indoor cooling load is extremely reduced. To the humidifier control mechanism.

  FIG. 2 shows an example of an air diagram of the air-conditioning method of Solution 1 of the present invention. In Solution 1, since the air in the target chamber does not recirculate, the state point of the air taken in from the outside air intake is at the position A2. In this example, it is assumed that SHF = 0.9.

  The air at the state point A2 is cooled, becomes saturated at the state point A3, and further moves to the state point A4. State point A4 is a value (dew point) that saturates the air at state point A1 (desired state point) on the line of SHF = 0.9.

  State point A4 also represents the state point of the air at the air outlet of the blower. The state of air in the target room (state point A1) is transmitted to the control mechanism of the air cooler as temperature information from a temperature detector installed in the target room and humidity information from the humidity detector.

Then, the control mechanism calculates the value of the state point A4 based on the information of the state point A1, and controls the cooling capacity of the air cooler so that the state point of the air sent to the blower is the state point A4. .

Even when the cooling load in the target room fluctuates, instead of changing the state point of the air blown from the blower as in the past, the state of the blown air is kept at the state point A4, Change the amount of air to be blown. That is, it responds by changing the output of the blower.

That is, when the cooling load in the target room is large, the amount of air blown from the blower is increased, and when the cooling load in the target room is small, the amount of air blown from the blower is small. By doing so, the state point of the air in the target room is always maintained at the state point A1.

  The air state point A1 in the target room is always detected by the temperature detector and the humidity detector in the target room, and the air at the blower outlet of the blower, that is, the state point A4 of the air blown into the target room is immediately before the blower blower outlet. It is always detected by the temperature detector and humidity detector installed in

  Therefore, the cooling capacity of the air cooler and the blower capacity of the blower are controlled so that the state point A1 and the state point A4 are always kept within a certain range, whereby the air conditioning method described in Solution 1 of the present invention. Is realized.

  The control of the cooling capacity of the air cooler and the control of the blowing capacity of the blower are both performed by an inverter. Further, since it is assumed that the air at the state point A4 is dew point air, the humidity detector installed immediately before the air outlet can be appropriately omitted from the above configuration.

  Next, the air conditioning method of the solution 2 of the present invention will be described with reference to the air diagram of FIG. In Solution 2, since there is a recirculation of air in the target chamber, the state point of the air-fuel mixture of the air (state point B0) taken from the outside air intake and the air recirculated from the target chamber (state point B1) is the position of B2. It becomes. In this example, it is assumed that SHF = 0.9.

  The air at the state point B2 is cooled, becomes saturated at the state point B3, and further moves to the state point B4. State point B4 is a value (dew point) that saturates the air at state point B1 (desired state point) on the line of SHF = 0.9.

  State point B4 also represents the air state point at the blower outlet. The state of the air in the target room (state point B1) is transmitted to the control mechanism of the air cooler as temperature information from the temperature detector installed in the target room and humidity information from the humidity detector in the same manner as the solving means 1. .

Then, the control mechanism calculates the value of the state point B4 based on the information of the state point B1, and controls the cooling capacity of the air cooler so that the state point of the air sent to the blower is the state point B4. .

Even when the cooling load in the target room fluctuates, the amount of air blown from the blower is changed while the state of the blown air is held at the state point B4, as in the solution 1. That is, it responds by changing the output of the blower.

That is, when the cooling load in the target room is large, the amount of air blown from the blower is increased, and when the cooling load in the target room is small, the amount of air blown from the blower is small. By doing so, the state point of the air in the target room is always maintained at the state point B1.

  The air state point B1 in the target room is always detected by the temperature detector and the humidity detector in the target room, and the air at the blower outlet of the blower, that is, the state point B4 of the air blown into the target room is immediately before the blower blower outlet. It is always detected by the temperature detector and humidity detector installed in

  Therefore, the cooling capacity of the air cooler and the blower capacity of the blower are controlled so that the state point B1 and the state point B4 are always kept within a certain range, whereby the air conditioning method described in the solution means 1 of the present invention. Is realized.

  In addition, the control of the cooling capacity of the air cooler and the control of the blowing capacity of the blower are both performed by an inverter, and the humidity detector installed immediately before the blower port can be omitted from the above configuration as appropriate. This is also the same as Solution 1.

    Next, the air conditioning method of the solving means 3 of the present invention will be described with reference to the air diagrams of FIGS. 6 is an air diagram when the outside air state point is in a high temperature and high humidity state compared to the state point of the target room, and FIG. 7 is a low temperature and low humidity state where the outside air state point is lower than the state point of the target room. It is an air line figure in a certain case.

First, FIG. 6 will be described. In Solution 2, since the air in the target chamber is recirculated, the state point of the air-fuel mixture of the air (state point C0) taken from the outside air intake and the air recirculated from the target chamber (state point C1) is the position of C2. It becomes. In this example, it is assumed that SHF = 0.9.

  The air at the state point C2 is cooled to become saturated at the state point C3, and further moves to the state point C4. The state point C4 is a value (dew point) that saturates the air at the state point C1 (desired state point) on the line of SHF = 0.9.

  State point C4 also represents the state point of the air blown from the blower. The dry bulb temperature information of the air blown from the blower is detected by the temperature detector and transmitted to the cooling water control mechanism of the cooling coil through the switching device.

  Then, based on this information, the cooling water control mechanism controls the amount of cooling water sent to the cooling coil so as to keep the state point of the air sent to the blower at the state point C4.

On the other hand, as for the air state (state point C1) in the target room, only temperature information from the temperature detector installed in the target room is transmitted to the blower control mechanism of the blower through the switching device.

Then, the blower control mechanism controls the blowing capacity of the blower to an amount corresponding to the cooling load in the target room based on the information of the state point C1, and the amount corresponding to the cooling load in the target room. Only blow from the air vent. In this case, the heater and humidifier installed in the subsequent stage of the blower are not functioning.

That is, when the cooling load in the target room is large, the amount of air blown from the blower is increased, and when the cooling load in the target room is small, the amount of air blown from the blower is small. By doing so, the state point of the air in the target room is always maintained at the state point C1.

Since the transition from the state point C4 to the state point C1 follows the SHF line, humidity information from the humidity detector installed in the target room is not necessarily required in an environment where the SHF of the target room is constant. Therefore, the solution means 3 presents a form in which this humidity information is omitted.

Of course, when a change in the SHF in the target room is expected, it is possible to adopt a method of adopting humidity information from a humidity detector installed in the target room as in Solution 1 or Solution 2.

Next, the case where the outside air state point is in a low-temperature and low-humidity state as compared with the air state point of the target chamber and the cooling load of the target chamber is extremely low will be described with reference to the air diagram of FIG. In this case, if the state point of the outside air is C10 and the state point of the air in the target chamber is C11, the state point of the air-fuel mixture is C12. It is assumed that SHF = 0.9.

The air at the state point C12 is cooled and moves to the state point C13. Since the air at the state point C13 is in a dehumidified state from the SHF line of the air at the state point C11, the air at the state point C11 is slightly humidified and heated in front of the blower opening, and the SHF line of the air at the state point C11. The air is blown into the target room from the air outlet as the air at the state point C14 located above.

In this case, the temperature information in the target room is sent to the cooling water control mechanism through the switching machine. The cooling water control mechanism determines the position of the state point C13 by adjusting the amount of cooling water sent to the cooling coil in accordance with the cooling load in the target room. In this case, the air volume of the blower is the constant lower air volume.

  In addition, humidity information in the target room is sent to the humidifier installed in front of the air outlet through the switching machine, and temperature information in the target room is sent to the heater installed in front of the air outlet through the switching machine. The air at the state point C13 is transferred to the air at the state point C14.

In short, in the method of Solution 3, if the state point of the mixture of air taken in from the outside air intake and the air returning from the target chamber is higher in temperature and humidity than the state point of the air in the target chamber, the amount of cooling water Is made constant, and the air volume of the blower is variable to an amount commensurate with the cooling load in the target room.

In addition, when the state point of the air-fuel mixture is lower in temperature and humidity than the air state point in the target room and the cooling load in the target room is extremely small, the air volume of the blower is made constant, and the amount of cooling water is set as the cooling load in the target room. This is a method in which the heating is appropriately heated and humidified immediately before the air blowing port, with the amount of the matching being variable. The cooling coil water volume is controlled by an electric flow control valve, and the blower blowing capacity is controlled by an inverter.

Further, in the method of Solution 3, a cooling coil that does not have a cooling source is used, but it goes without saying that an air cooler with a built-in compressor such as Solution 1 or Solution 2 can be used. Absent.

Furthermore, it is naturally conceivable to package the whole as solution means 1 or solution means 2.

In short, Solution 1 or Solution 2 shows a constant temperature and humidity control method that is effective when there is no possibility that the state point of the air-fuel mixture is lower in temperature and humidity than the state point of the air in the target room. This shows a constant temperature and humidity air conditioning method that is effective when the state point of the air-fuel mixture may be lower in temperature and humidity than the state point of the air in the target room.

  According to Solution 1 and Solution 2 of the present invention, the process of heating and humidifying supercooled air, which is indispensable in the conventional constant temperature and humidity air conditioning method, can be completely omitted.

  Therefore, the air is not supercooled, and energy for heating and humidification is not required, and the total amount of energy consumption is reduced, and constant temperature and humidity air conditioning can be realized with less energy.

  The methods of Solution 1 and Solution 2 of the present invention are particularly effective when the cooling load in the target room is small, and air conditioning with constant temperature and humidity can be realized with a fraction of the energy of the conventional method. It is.

  According to the solution 1 and the solution 2 of the present invention, the heating and humidification processes can be completely omitted, so that the configuration is simple, the equipment cost is low, and the failure is reduced, so that maintenance is easy. .

    According to the method of Solution 3 of the present invention, when the state point of the air-fuel mixture is higher in temperature and humidity than the state point of the air in the target chamber, as with the method of Solution 1 or Solution 2, the supercooled air The process of heating and humidifying can be omitted completely. Therefore, the effect in this case is the same as the effect of the solution 1 or the solution 2 method.

  In the method of Solution 3, even when the state point of the air-fuel mixture is lower in temperature and humidity than the state point of the air in the target chamber and the cooling load of the target chamber is significantly reduced, the target chamber is kept constant by constant heating and humidification. Can be kept moist.

  In that case, since the air volume of the blower is fixed at the lower limit, the energy required for heating and humidification is far less than that of the conventional method. That is, even if the state point of the air-fuel mixture is higher or lower than the state point of the air in the target room, it can realize a constant temperature and humidity air conditioning method that is much more efficient than the conventional method. Is.

  The best mode for carrying out the present invention will be described below by Examples 1 to 3. The first embodiment is one embodiment of the solution means 1 of the present invention, the second embodiment is one embodiment of the solution means 2 of the present invention, and the third embodiment is one embodiment of the solution means 3 of the present invention.

<Configuration of Example 1>
FIG. 1 is a circuit diagram of Embodiment 1 of the present invention. In FIG. 1, 1A is an air conditioner, 2 is an air cooler composed of a compressor 2a and a cooling coil 2b, 3 is a blower, and the air cooler 2 and the blower 3 are stored in a package 1a.

  2c is a control mechanism for controlling the capacity of the compressor 2a of the air cooler 2, whereby the air cooling capacity of the air cooler 2 is controlled. 3a is a control mechanism for controlling the blowing capacity (air volume) of the blower 3.

  4 is a temperature detector (dry bulb temperature detector) installed in the target chamber R, 5 is a humidity detector installed in the target chamber R, 6 is an air duct 12, 13 connecting the blower 3 and the air outlet 8. The temperature detector (dry bulb temperature detector) installed in the middle of the temperature detector 7 is a humidity detector installed at the same position as the temperature detector 6.

  Reference numeral 9 is an outside air intake port for taking in outside air, 10 is a blower duct for guiding the outside air taken in from the outside air intake port 9 to the air cooler 2, and 11 is a blower duct for guiding the air from the air cooler 2 to the blower 3. The term “outside air” as used herein means air outside the target room, and both natural air outside the building and air outside the target room inside the building are included in the meaning of this term. is there.

  Reference numeral 14 denotes a temperature information transmission path for transmitting temperature (dry bulb temperature) information detected by the temperature detector 4 installed in the target room R. The path 14a and the control mechanism 3a for transmitting the temperature information to the control mechanism 2c. Branches to a route 14b for transmission to the.

  Reference numeral 15 denotes a humidity information transmission path for transmitting humidity information detected by the humidity detector 5 installed in the target room R, and a path 15a for transmitting the humidity information to the control mechanism 2c and a path 15b for transmitting the humidity information to the control mechanism 3a. Branch to

  Reference numeral 16 denotes a temperature information transmission path for transmitting temperature (dry bulb temperature) information detected by the temperature detector 6 installed between the air ducts 12 and 13, and a path 16a for transmitting the temperature information to the control mechanism 2c; It branches to the path | route 16b which transmits to the control mechanism 3a.

  Reference numeral 17 denotes a humidity information transmission path for transmitting humidity information detected by the humidity detector 7 installed between the air ducts 12 and 13, and the humidity information is transmitted to the control mechanism 2c and to the control mechanism 2c. Branches to the path 17b to be performed.

  18 is a control information transmission path for transmitting control information from the control mechanism 2c to the air cooler 2, and 19 is a control information transmission path for transmitting control information from the control mechanism 3a to the blower 3. 21 is an air discharge port for discharging the air in the target chamber R out of the target chamber R.

<Operation of Example 1>
The operation of the first embodiment will be described with reference to FIGS.
FIG. 2 is an example of an air diagram of the method of the first embodiment. In FIG. 2, A2 represents the state point of the air taken in from the outside air intake 9 of FIG. A1 represents a state point of air in the target room R in FIG.

  The air at the state point A2 taken from the outside air inlet 9 is guided to the air cooler 2 by the air duct 10, is cooled, passes through the state point A3 in FIG. 2, and reaches the state point A4.

  The air at the state point A4 is guided to the blower 3 by the blower duct 11 and blown into the target chamber R through the blower ducts 12 and 13 from the blower port 8.

  The state point A1 of the air in the target room R is always detected by the temperature detector 4 and the humidity detector 5, and the temperature information of the air in the target room R passes through the temperature information transmission path 14 and passes along the path 14a. It branches to the path | route 14b, is transmitted to the control mechanism 2c through the path | route 14a, and is transmitted to the control mechanism 3a through the path | route 14b.

  The humidity information of the air in the target room R passes through the humidity information transmission path 15, and is branched into a path 15a and a path 15b on the way, and is transmitted to the control mechanism 2c through 15a and to the control mechanism 3a through the path 15b.

  The air state point A4 at the air outlet 8 is always detected by the temperature detector 6 and the humidity detector 7, and the temperature information of the air at the air outlet 8 passes through the temperature information transmission path 16 and passes along the path 16a and the path 16b. And is transmitted to the control mechanism 2c through the path 16a and to the control mechanism 3a through the path 16b.

The humidity information of the air at the air outlet 8 passes through the humidity information transmission path 17, and is branched into a path 17a and a path 17b on the way, and is transmitted to the control mechanism 2c through the path 17a and to the control mechanism 3a through the path 17b.

Control information from the control mechanism 2 c is guided to the air cooler 2 through the control information transmission path 18 to control the cooling capacity of the air cooler 2. Control information from the control mechanism 3a is guided to the blower 3 through the control information transmission path 19 to control the cooling capacity of the blower 3.

The air state point A4 at the air blowing port 8 is always controlled to a value within a certain range when the air cooler 2 is controlled by the control mechanism 2c, and the air blown into the target chamber R from the air blowing port 8 is controlled. The air volume is controlled to a value commensurate with the cooling load in the target room R when the blower 3 is controlled by the control mechanism 3a.

Thereby, the state point A4 of the air in the target chamber R is always controlled to a value within a certain range. The control mechanism 2c and the control mechanism 3a are controlled by an inverter.

<Configuration of Example 2>
A circuit diagram of the second embodiment is shown in FIG. The structure of the air conditioner 1B of Example 2 removes the air discharge port 21 from the structure of the air conditioner 1 of Example 1, and adds the air recirculation | reflux port 9b and the ventilation duct 10b (9a is external air intake port 10a. Is an air duct). Therefore, the package 1b is the same as the package 1a (see FIG. 1).

<Operation of Example 2>
In the second embodiment, an air recirculation port 9b for recirculating air in the target chamber R to the air cooler 2 and a blower duct 10b are added. Therefore, in the example of the air diagram of the second embodiment (see FIG. 4), if the state point of the outside air is B0 and the state point of the air in the target chamber R is B1, the state point of the air-fuel mixture is B2.

  The air-fuel mixture at the state point B2 is led to the air cooler 2 to be cooled, passes through the state point B3, and becomes air at the state point B4. The air at the state point B4 is obtained by cooling the air in the target chamber R (state point B1) to the dew point.

  The air at the state point B4 is blown into the target chamber R from the blower port 8 by the blower 3.

The air state point B4 at the air outlet 8 is always controlled to a value within a certain range when the air cooler 2 is controlled by the control mechanism 2c, and the air blown into the target chamber R from the air outlet 8 is controlled. The air volume is controlled to a value commensurate with the cooling load in the target room R when the blower 3 is controlled by the control mechanism 3a.

Thereby, the state point B4 of the air in the target chamber R is always controlled to a value within a certain range. The operations of the temperature detectors 4 and 6 and the humidity detectors 5 and 7 are the same as in the first embodiment. Further, the control mechanism 2c and the control mechanism 3a are controlled by an inverter as in the first embodiment.

<Configuration of Example 3>
A circuit diagram of the third embodiment is shown in FIG. In FIG. 5, 1C is an air conditioner, and 20 is a cooling coil. Cooling water cooled by an external cooler (not shown) is sent to the cooling coil 20 via a cooling water control mechanism 20a by a water supply pipe 20b, and drained. It is drained by the pipe 20c. The cooling water control mechanism 20a is an electric flow control valve mechanism.

Reference numeral 30 denotes a blower, and the blower capacity (air flow) is controlled by the blower control mechanism 30a (inverter control). 40 is a temperature detector (dry bulb temperature detector) installed in the target chamber R, 50 is a humidity detector installed in the target chamber R, and 60 is a temperature detector installed immediately before the air outlet 80 ( Dry bulb temperature detector).

  Reference numeral 71 denotes a heater installed at the subsequent stage of the temperature detector 60, and reference numeral 71 a denotes a heater control mechanism that controls the heating capability of the heater 71. Reference numeral 72 denotes a humidifier installed at the subsequent stage of the heater 71, and reference numeral 72 a denotes a humidifier control mechanism that controls the humidifying capacity of the humidifier 72. Reference numeral 80 denotes an air outlet that blows the adjusted air into the target chamber R.

  90a is an outside air intake port for taking in outside air, 90b is an air return port for returning the air in the target room to the cooling coil 20, 100a is an air duct that guides the outside air taken from the outside air intake port 90a to the cooling coil 20, and 100b is an air return port. A blower duct that guides the air recirculated from 90 b to the cooling coil 20, and 110 is a blower duct that guides the air from the cooling coil 20 to the blower 30.

  120 is a blower duct that guides air from the blower 30 to the temperature detector 60, 130 a is a blower duct that guides air from the temperature detector 60 to the heater 71, and 130 b is a blower that guides air from the heater 71 to the humidifier 72. A duct 130 c is an air duct that guides air from the humidifier 72 to the air outlet 80.

Reference numeral 180 denotes a switching machine, and temperature information from the temperature detector 40 is transmitted to the switching machine 180 through the temperature information transmission path 140. Further, humidity information from the humidity detector 50 is transmitted to the switching machine 180 through the humidity information transmission path 150, and temperature information from the temperature detector 60 is transmitted to the switching machine 180 through the temperature information transmission path 160.

  The temperature information from the switching machine 180 is transmitted to the cooling water control mechanism 20a through the information transmission path 170, to the blower control mechanism 30a through the information transmission path 173, or to the heater control mechanism 71a through the information transmission path 171. Further, the humidity information from the switching machine 180 is transmitted to the humidifier control mechanism 72a through the information transmission path 172.

<Operation of Example 3>
The operation of the third embodiment will be described with reference to FIGS.
FIG. 6 is an example of an air diagram of the method according to the third embodiment, and the outside air state point C0 is higher in temperature and humidity than the air state point C1 in the target room R. FIG. 7 is an example of an air diagram when the outside air state point C10 is at a lower temperature and lower humidity than the air state point C11 in the target room R.

In FIG. 6, C0 represents the state point of the air taken in from the outside air intake port 90a of FIG. C1 represents a state point of air in the target room R of FIG. C2 represents a state point of a mixture of outside air and air in the target room R.

  The air at the state point C0 taken in from the outside air intake port 90a and the air at the state point C1 taken in from the air recirculation port 90b are guided to the cooling coil 20 by the air ducts 100a and 100b and cooled to be the state point of FIG. It passes through C3 and reaches state point C4. C4 is a state point of air obtained by cooling the air at the state point C1 to the dew point.

  The air at the state point C4 is guided to the blower 30 by the blower duct 110, and blown into the target chamber R from the blower port 80 through the blower ducts 120, 130a, and 130b. In this case, the heater 71 and the humidifier 72 are not functioning.

  The state point C1 of air in the target room R is always detected by the temperature detector 40 and the humidity detector 50. The temperature information of the air in the target room R passes through the temperature information transmission path 140 and enters the switching machine 180.

In this state, the switching machine 180 transmits the temperature information received from the temperature information transmission path 140 to the air volume control mechanism 30a through the temperature information transmission path 173, and the blower 30 according to the cooling load of the target room R. The air blowing capacity (air volume) is controlled.

Further, the humidity information of the air in the target room R passes through the humidity information transmission path 150 and enters the switching machine 180. In this case, the humidifier 72 is not working, so the humidity information is stopped at the stage of the switching machine 180. Is done.

  On the other hand, the state point C4 of the air blown from the blower port 80 is always detected by the temperature detector 60. The temperature information detected by the temperature detector 60 is transmitted to the switching device 180 through the temperature information transmission path 160.

  In this state, the temperature information transmitted to the switching machine 180 is transmitted to the cooling water control mechanism 20a through the information transmission path 170, and the amount of cooling water fed to the cooling coil 20 is the temperature. The state point of the air that is controlled by the information and is blown from the blower opening 80 is always held at C4.

Next, in the air diagram shown in FIG. 7, the outside air state point C10 is lower in temperature and humidity than the air state point C11 in the target chamber R. In this case, the state point of the mixture of the outside air and the air in the target chamber R is C12.

The air-fuel mixture at the state point C12 is cooled by the cooling coil 20 and becomes air at the state point C13. However, since the air at the state point C13 is in a dehumidified state from the SHF line of the air at the state point C11, the air at the state point C13 is heated by the heater 71 and the humidifier 72 installed immediately before the air blowing port 80. Humidification and heating are performed, and air is blown into the target chamber R from the air outlet 80 as air at the state point C14 located on the SHF line of the air at the state point C11.

In this case, the temperature information in the target room R reaches the switching device 180 through the temperature information transmission path 140 from the temperature detector 40. In this case, the switching machine 180 is automatically switched so that the temperature information transmitted to the switching machine 180 is sent to the cooling water control mechanism 20a through the information transmission path 170.

Accordingly, the cooling water control mechanism 20a determines the position of the state point C13 by adjusting the amount of cooling water sent to the cooling coil 20 in accordance with the cooling load in the target room R. In this case, the air volume of the blower 30 is a constant lower air volume.

  The temperature information in the target room R is also sent to the heater 71 installed in front of the air outlet 80 through the switching device 180. Furthermore, the humidity information in the target room R is detected by the humidity detector 50 and sent from the humidity information transmission path 150 to the humidifier 72 installed in front of the air outlet 80 through the switching device 180, and the heater 71 and the humidifier 72 works to shift the air at the state point C13 to the air at the state point C14.

In short, when the outside air state point C0 becomes higher in temperature and humidity than the air state point C1 in the target chamber R, the heater 71 and the humidifier 72 stop their functions, and the temperature in the target chamber R The information is sent to the blower 30 by the switching device 180 to control the air volume of the blower 30 to an air volume commensurate with the cooling load in the target room R.

The temperature of the air blown from the blower 30 is always detected by the temperature detector 60, and the temperature information is transmitted to the cooling coil control mechanism 20a by the switching device 180, and the state point C4 of the air blown from the blower 30 Is always controlled to a value with the air state point C1 in the target room R as the dew point.

When the outside air state point C10 is lower in temperature and humidity than the air state point C11 in the target room R, the air volume of the blower 30 is constant at the lower limit, and the temperature information in the target room R is the switching machine. 180 is sent to the cooling coil control mechanism 20a, and the amount of cooling water in the cooling coil 20 is controlled to the amount of water commensurate with the cooling load in the target room R.

Further, the temperature information in the target chamber R is sent to the heater 71 via the switching device 180, and the humidity information in the target chamber R is sent to the humidifier 72 by the switching device 180 and blown from the air outlet 80. This is a method of maintaining the air state point at the position C14. In addition, control of the cooling water amount of the cooling coil 20 is performed by an electric flow control valve, and control of the blowing capacity of the blower 30 is performed by an inverter.

Note that the switching machine 180 constantly compares the state point of the air-fuel mixture and the state point of the air in the target chamber R, and automatically switches the route as described above based on the relationship between the two.

<Comparison of Method of Example 3 and Conventional Method—1>
FIG. 10 compares the method of Example 3 with the conventional method (with air recirculation). For convenience of comparison, the outside air state point C0 of the method of the third embodiment and the outside air state point D0 of the conventional method are the same, and the air state point C1 of the target room R of the method of the third embodiment is the same as that of the conventional method. The air state point D1 in the target chamber R of the method is also the same.

Under such assumption, the state points C2 and D2 of the air-fuel mixture are naturally the same. Of course, the state point C3 of the air that has cooled the air at the state point C2 to the dew point and the state point D3 of the air that has cooled the air at the state point D2 to the dew point are naturally the same.

  If the enthalpy of air at state points C2 and D2 is i1, and the enthalpy of air at state points C3 and D3 is i2, then the air at state points C2 and D2 is cooled to the air at state points C3 and D3. The required enthalpy amount Δi1 is given by the following formula (Formula 1).

(Formula 1)
Δi1 = i1-i2

  Next, in the method of the third embodiment, the air at the state point C3 is further cooled to the state point C4. When the enthalpy of air at the state point C4 is i3, the enthalpy amount Δi2 necessary for this cooling is given by the following equation (Equation 2). In the method of the third embodiment, the air at the state point C4 (enthalpy i3) is directly blown into the target chamber R from the blower port 80 (see FIG. 5).

(Formula 2)
Δi2 = i2−i3

  In the conventional method, the air at the state point D3 is further cooled to the state point D4. If the enthalpy of air at the state point D4 is i4, the enthalpy of air at the state point D3 is i2 as is the air at the state point C3. Therefore, the enthalpy amount Δi3 necessary for this cooling is given by the following equation (Equation 3).

(Formula 3)
Δi3 = i2−i4

  In the conventional method, the air at the state point D4 is heated to the air at the state point D5. The enthalpy amount Δi4 required at this time is given by the following equation (Equation 4), where i5 is the enthalpy of the air at the state point D5.

(Formula 4)
Δi4 = i5-i4

  In the conventional method, it is necessary to further humidify the air at the state point D5 to the air at the state point D6. The enthalpy amount Δi5 required for this is expressed by the following formula (1) where the enthalpy of the air at the state point D6 is i6: It is given by equation 5). In the conventional method, the air of D6 (enthalpy i6) at this state point is blown into the target chamber R ′ from the blower port 8D (see FIG. 8).

(Formula 5)
Δi5 = i6-i5

  As described above, when the amount of enthalpy required in the method of Example 3 and the conventional method are compared, the following equations (Equation 6 and Equation 7) are obtained. However, iC is the amount of enthalpy required to transfer the air at the state point C2 to the air at the state point C4 in the method of the second embodiment, and iD is the air at the state point D2 in the state method D6 in the conventional method. This is the amount of enthalpy required to transfer to the air.

(Formula 6)
iC = Δi1 + Δi2

(Formula 7)
iD = Δi1 + Δi3 + Δi4 + Δi5

  Since Δi1, Δi2, Δi3, Δi4, and Δi5 are all positive numbers and Δi3> Δi2, the following equation (Equation 8) always holds.

iC <iD

  That is, in the air diagram of FIG. 10, the amount of enthalpy required to transfer the air at the state point C2 to the air at the state point C4 by the method of the third embodiment is the state of the air at the state point D2 by the conventional method. The amount of enthalpy required to transfer to the air at the point D6 is always smaller, and the difference between the two becomes larger as the cooling load in the target rooms R and R ′ becomes smaller.

<Comparison of Method of Example 3 and Conventional Method-2>
FIG. 11 is a graph comparing the method of Example 3 and the conventional method (with air recirculation) with actual data.

  Among the graphs of FIG. 11, the data used as the basis at the time of creating the graph of the method of Example 3 are listed in the following table (Table 1).

  Among the graphs in FIG. 11, data used as a basis for creating a graph of the conventional method (with air recirculation) is listed in the following table (Table 2).

  As shown in FIG. 11, when the cooling load is up to 80 percent, the method of Example 3 consumes much less energy than the conventional method (with air recirculation). In particular, when the cooling load is 20%, it is about 11.4% of the conventional method, and when it is 30%, it is about 22.4% of the conventional method. Proven to be the method.

  As the cooling load increases, the difference in the total energy consumption between the two decreases, but even when the cooling load is 60%, the conventional method is about 54.6%, which is the conventional method. The total energy consumption is more than half (with air recirculation). Even if the cooling load increases to 80%, it is apparent that the method of Example 3 is an effective method with less total energy consumption, which is about 85.5% of the conventional method.

  Actually, the case where the cooling load exceeds 80% is limited to a special time zone at a very special time in summer. Therefore, the method of Example 3 is a conventional method (air recirculation) throughout the year. It is clear that this is a method that consumes much less energy compared to (Yes).

  The above is a comparison of the method of Example 3 and the conventional method (with air recirculation) by data. However, when the method of Example 1 and the conventional method (without air recirculation) are compared, Example 2 is also compared. It goes without saying that the same result is obtained when comparing this method with the conventional method (with air reflux).

It is a circuit diagram of the method of Example 1 of this invention. It is an example of the air diagram of the method of Example 1 of this invention. It is a circuit diagram of the method of Example 2 of this invention. It is an example of the air line figure of the method of Example 2 of this invention. It is a circuit diagram of the method of Example 3 of this invention. It is an example of the air line figure of the method of Example 3 of this invention. It is an example of the air line figure of the method of Example 3 of this invention. It is a circuit diagram of an example of the conventional method. It is an example of the air line diagram of the conventional method of FIG. It is an air diagram which compared an example of the air diagram of the method of Example 3 of this invention with an example of the air diagram of the conventional method. It is the graph which compared the energy consumption of the method of Example 3 of this invention with the energy consumption of an example of the conventional method.

Explanation of symbols

1A air conditioner
1B air conditioner
1C air conditioner
1D air conditioner 1a package 1Da package 2 air cooler 2D air cooler 2Da compressor 2Db cooling coil 2a compressor 2b cooling coil 2c control mechanism 3 blower 3D blower 3a control mechanism 4 temperature detector 4D temperature detector 5 humidity detector 5D humidity detector 5D 6 Temperature detector 6D Heater 6Da Control mechanism 7 Humidity detector 7D Humidifier 7Da Control mechanism 8 Blower 8D Blower 9 Outside air inlet 9a Outside air inlet 9b Air recirculation port 9Da Outside air inlet 9Db Air recirculation port 10 Blower duct 10a Air duct 10b Air duct 10Da Air duct 10Db Air duct 11 Air duct 11Da Air duct 11Db Air duct 12 Air duct 12D Air duct 13 Air duct 13D Air duct 14 Temperature information transmission 14a path 14b path 14D temperature information transmission path 15 humidity information transmission path 15a path 15b path 15D humidity information transmission path 16 temperature information transmission path 16a path 16b path 17 humidity information transmission path 17a path 17b path 18 control information transmission path 19 control information transmission Route 20 Cooling coil 20a Cooling water control mechanism 20b Water supply pipe 20c Drain pipe 21 Air outlet 30 Blower 30a Blower control mechanism 40 Temperature detector 50 Humidity detector 60 Temperature detector 71 Heating device 71a Heating device control mechanism 72 Humidifier 72a Humidification Machine control mechanism 80 Blower port 90a Outside air intake port 90b Air reflux port 100a Blower duct 100b Blower duct 110 Blower duct 120 Blower duct 130a Blower duct 130b Blower duct 130c Blower duct 140 Temperature Degree information transmission path 150 Humidity information transmission path 160 Temperature information transmission path 170 Information transmission path 171 Information transmission path 172 Information transmission path 173 Information transmission path 180 Switching machine A1 State point A2 State point A3 State point A4 State point B0 State point B1 State Point B2 State point B3 State point B4 State point C0 State point C1 State point C2 State point C3 State point C4 State point C10 State point C11 State point C12 State point C13 State point C14 State point D0 State point D1 State point D2 State point D3 State point D4 State point D5 State point D6 State point R Target room R 'Target room i1 enthalpy i2 enthalpy i3 enthalpy i4 enthalpy i5 enthalpy i6 enthalpy iC enthalpy amount iD enthalpy amount Δi1 enthalpy amount Δi4 enthalpy amount Δi4 enthalpy amount Δi4 Enthalpy amount Δi5 enthalpy amount

Claims (2)

  When the outside air state point becomes hotter and humid than the air state point in the target room, the heater and humidifier stop their functions, and the temperature information in the target room is sent to the blower by the switching machine. The air flow of the blower is controlled to the air flow suitable for the cooling load in the target room, the temperature of the air blown from the blower is always detected by the temperature detector, and the temperature information is transmitted to the cooling coil control mechanism by the switching machine. When the state point of the air blown from the blower is always controlled to a value with the dew point of the air in the target room, and when the state point of the outside air is lower in temperature and humidity than the air state point in the target room, The air volume of the blower is a constant air volume at the lower limit, and the temperature information in the target room is sent to the cooling coil control mechanism by the switching machine to control the cooling water volume of the cooling coil to the water volume corresponding to the cooling load in the target room. Temperature information The humidity information sent to the heater through the machine is sent to the humidifier by the switching machine and kept at the position of the state point of the air blown from the blower port, and the amount of cooling water in the cooling coil Control is performed by an electric flow control valve, and the air blowing capacity of the blower is controlled by an inverter. The switching machine always compares the state point of the air-fuel mixture and the state point of the air in the target chamber, and the relationship between the two is as described above. The air flow rate according to fluctuations in the cooling load in the target room, with the state of the air to be blown constant by eliminating the heating and humidification processes immediately after the cooling coil. The temperature and humidity control method is characterized in that the target room is kept in a constant temperature and humidity state by changing the direction of the temperature.   The information of the temperature detector that detects the temperature in the target room is transmitted to a humidifier control mechanism that controls the humidifying capacity of the humidifier when the indoor cooling load is extremely reduced. Item 14. The constant temperature and humidity air conditioning method according to Item 1.

Images