JPH0243015Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to an air conditioner mainly applied to a computer room.

Conventionally, an air conditioner used in a computer room is shown in, for example, Japanese Patent Laid-Open No. 51-93534, and as shown in FIG. A reheat circuit C is provided to supply part of the discharged gas to the reheater B, and during operation, part of the discharged gas is used to reheat the outlet air of the evaporator A to control the temperature of the blown air. ing. In Fig. 3, D is a compressor, E is a condenser, F is a fan, G is an expansion valve, and H
is a temperature regulator, and I is a reheat amount control valve.

By the way, the total amount of heat required for air cooling is divided into sensible heat amount, which is the amount of heat used only for changing the temperature of the air, and
It consists of the sum of the amount of latent heat, which is the amount of heat required to condense the water vapor contained in the air.In a computer room, the air is cooled only by the amount of sensible heat, that is, the sensible heat ratio /(sensible heat amount + latent heat amount)]
It is desirable to be able to operate in a state where (SHF) is close to 1, that is, without dehumidification.For this reason, a humidifier is generally used to perform humidification when the relative humidity decreases.

However, in conventional air conditioners, as the humidifier, an ultrasonic humidifier or a humidifier incorporating an electric heater or a refrigerant heater is used. There are problems such as releasing water and other impurities into the blown air and scattering water droplets, and according to the latter, a detection circuit is required to detect whether the heater is on or off. At the same time, it became difficult to control the humidifying capacity, making it difficult to perform proper humidification.

The purpose of this invention is to heat the drain water that is dehumidified in the evaporator with a part of the discharge gas supplied to the reheater and re-evaporate it, and to humidify it with this re-evaporation, thereby eliminating the need for a special humidifier. It is possible to humidify both types of air, eliminate the risk of impurities being released or water droplets being scattered, and the humidification capacity can be controlled using a simple control circuit, and the humidifier can also be controlled accurately. At the point.

The configuration of the present invention provides an air conditioner that includes a compressor, an evaporator, and a reheater, and is provided with a reheat circuit that supplies part of the discharged gas to the reheater. A reevaporator for heating and reevaporating drain water is provided in the water tray, and a temperature controller is provided on the leeward side of the reheater to detect the temperature of the air blown from the reheater. The reheat circuit includes a reheat amount control valve that adjusts the amount of discharged gas supplied to the reheater of the reheat circuit so that the temperature of the blown air is constant based on the temperature signal detected by the temperature controller. A reevaporation circuit is interposed between the reheat amount control valve and the reheater in the reheat circuit, and a reevaporation circuit that supplies a part of the discharged gas to the reevaporator is branched. Utilizing the control of the reheat amount of the reheater by the reheater and the reheat amount control valve,
It is also possible to perform humidification control by re-evaporating drain water at the same time as the reheating, making it possible to perform humidification control commensurate with the amount of drain generated, that is, the amount of dehumidification.

Next, an embodiment of the air conditioner of the present invention will be described based on FIG.

In Figure 1, 1 is a compressor, 2 is a water condenser that exchanges heat with cooling water, 3 is an expansion valve, and 4 is an air evaporator that exchanges heat with indoor air. The pipes are systematically connected by pipes 5, high pressure liquid pipes 6, low pressure liquid pipes 7, and suction gas pipes 8, respectively.

Further, a fan 9 is attached to the evaporator 4, and a reheater 10 is installed in parallel on the leeward side of the fan 9. Below the evaporator 4, a reheater 10 is installed. A drain water receiving tray 11 is provided.

The reheater 10 forms a reheat circuit 12 that supplies a portion of the discharge gas flowing through the discharge gas pipe 5. That is, in the middle of the discharge gas pipe 5,
A high pressure gas pipe 14 connected to one port of the reheat amount control valve 13 consisting of a three-way solenoid valve is interposed,
A liquid pipe 15 is connected to the inlet side of the reheater 10 and a liquid pipe 15 is connected to the outlet side, and the liquid pipe 15 is communicated with the condenser 2, the reheat amount control valve 13, the high pressure gas pipe 14, A reheat circuit 12 is formed by the reheater 10 and the liquid pipe 15.

In the air conditioner configured as described above, a re-evaporator 20 is provided in the tray 11 to heat and re-evaporate the drain water received in the tray 11. A reevaporation circuit 21 that supplies one portion is branched from the reheating circuit 12.

In the system shown in FIG. 1, a branch pipe 22 is connected in the middle of the high-pressure gas pipe 14 in the reheat circuit 12, and this branch pipe 22 is connected to the inlet side of the reevaporator 20, and the branch pipe 22 is connected to the outlet side of the reevaporator 20. A liquid pipe 23 is connected to the branch pipe 2, and this liquid pipe 23 is connected to the middle of the liquid pipe 15 in the reheat circuit 12, and the branch pipe 2
2, a solenoid valve 24 is installed in the middle to close the re-evaporation circuit 21 and enable dehumidifying operation.

In FIG. 1, reference numeral 30 denotes a temperature regulator, which is disposed on the leeward side of the reheater 10 so as to detect the temperature of the air blown out.
The temperature signal detected by the reheat amount control valve 1
3, the amount of discharged gas flowing into the reheat circuit 12 is controlled, and the amount of reheat in the reheater 10 is controlled to maintain the temperature of the blown air constant. . That is, even if the temperature of the intake air flowing into the evaporator 4 changes, the amount of reheat in the reheater 10 is controlled so that the temperature of the blown air is always constant.

Therefore, in the above configuration, when controlling the temperature of a computer room, for example, the compressor 1 is driven to circulate the refrigerant as shown by the solid arrow, and the indoor air is cooled by the evaporator 4. Moreover, when the indoor air is excessively cooled by the evaporator 4, the reheater circuit 12 is released from the reheat amount control valve 13 based on the temperature signal detected by the temperature controller 30. The cooling air is reheated in the reheater 10 until it reaches a set temperature by adjusting the amount of discharge gas supplied to the evaporator 4, and is always blown into the room at a constant temperature. The condensed drain water is reevaporated in the reevaporator 20, and the air reheated in the reheater 10 is humidified and blown into the room. At this time, the reevaporator 20 is connected to the reheat circuit. The reheating circuit 12 is heated by the discharged gas supplied to the reevaporation circuit 21 branched from the reheating circuit 12, so the reheating circuit 12 is heated by controlling the amount of reheating in the reheating circuit 12 by the temperature regulator 30 and the reheating amount control valve 13. The humidification of the evaporator circuit 21 can also be controlled, and the blown air can be humidified to have the same humidity as the indoor air before being cooled by the evaporator 4.

Therefore, with this humidification, it is possible to perform humidification commensurate with the amount of dehumidification without using a special humidifier such as an ultrasonic humidifier, and as a result, the sensible heat ratio (SHF) can be reduced to 1.
It is possible to drive in conditions close to that of the previous model.

That is, in general, when comparing when the temperature of the suction air to the evaporator 4 is high and when it is low, assuming that the capacity of the air conditioner (the total amount of heat used to cool the suction air) is constant, And, assuming that the absolute humidity at each temperature is the same, when the intake air temperature is high, is the water vapor partial pressure at the temperature after cooling of the water vapor contained in the intake air smaller than the saturated water vapor partial pressure at that temperature? , or even if the water vapor partial pressure becomes larger than the saturated water vapor partial pressure, the difference is small, so the amount of sensible heat used only for changing the temperature of the air is larger, and the amount of latent heat used to condense water vapor is larger. As a result, less drain water is generated, and when the suction air temperature is low, the water vapor contained in the suction air at the temperature after cooling becomes smaller than when the suction air temperature is high. The partial pressure becomes considerably larger than the saturated steam partial pressure at that temperature, and the amount exceeding the saturated steam partial pressure condenses to become drain water, so the sensible heat change is smaller than the latent heat change. The larger the size, the more the drain water will be generated. Moreover, when the suction air temperature is high, the difference between the air temperature blown from the evaporator 4 due to excessive cooling and the set air temperature is small, so the amount of reheating is small, and when the suction air temperature is low, Since the difference between the blowing air temperature of the evaporator 4 and the set air temperature is large,
This increases the amount of reheating.

Therefore, in response to changes in the suction air temperature, when the suction air temperature is high, that is, when the temperature difference between the temperature of the blowing air cooled by the evaporator 4 and the set air temperature is small and the amount of drain water is small, In this case, the amount of reheat is reduced, and when the intake air temperature is low, that is, when the temperature difference between the temperature of the blowing air cooled by the evaporator 4 and the set air temperature is large and the amount of drain water is large, the amount of reheat is reduced. Therefore, the amount of reheat in the reheat circuit 12 can be controlled by the temperature regulator 30 and the reheat amount control valve 13 without providing a special humidification amount control circuit in the reevaporation circuit 21. The re-evaporation circuit 2 can be operated with a simple configuration using control.
This makes it possible to perform humidification control (1), that is, control the amount of humidification commensurate with the amount of drain generated.

Further, even if an amount of heat greater than the amount of heat required to re-evaporate the drain water is applied to the re-evaporation circuit 21, this excess amount of heat is used for reheating, so humidification is not performed more than necessary.

In the embodiment shown in FIG. 1, the reevaporator 20 provided in the saucer 11 is arranged so that the heat exchange tube is immersed in the saucer 11, but as shown in FIG. A coil type may also be used. In this case, the re-evaporator 20 is preferably disposed directly below the evaporator 4.

As described above, the present invention provides a re-evaporator 20 for heating and re-evaporating the drain water in the drain water receiving tray 11 condensed in the evaporator 4, and a re-evaporator 20 for heating the drain water to re-evaporate it. A temperature regulator 30 is provided to detect the temperature of the air blown from the heater 10, and the reheat circuit 12 is configured to maintain the temperature of the blown air constant based on the temperature signal detected by the temperature regulator 30. A reheat amount control valve 13 that adjusts the amount of discharged gas supplied to the reheater 10 of the reheat circuit 12 is interposed, and between the reheat amount control valve 13 and the reheater 10 in the reheat circuit 12. , the re-evaporator 2
Since the reevaporation circuit 21 that supplies part of the discharged gas to the reheating circuit 12 is branched, the reheating circuit 12 is made up of the temperature regulator 30 and the reheat amount control valve 13.
It is possible to perform humidification control of the reevaporation circuit 21 by using the control of the reheat amount of the evaporator 4, and it becomes possible to perform humidification commensurate with the amount of drain water generated in the evaporator 4, and as a result, the air conditioner is not dehumidified. In other words, it is possible to operate with a sensible heat ratio (SHF) close to 1, and furthermore, there is no need for a special humidification control circuit, and the configuration can be simplified.

Furthermore, humidification can be achieved by re-evaporating the drain water generated by cooling the evaporator 4 without providing a special humidifier such as a conventional ultrasonic humidifier. Unlike humidifiers, dust and other impurities are not emitted into the blown air, and there is no risk of water droplets flying around.

[Brief explanation of the drawing]

Fig. 1 is a refrigerant piping system diagram showing an embodiment of the air conditioner of the present invention, Fig. 2 is a schematic sectional view showing another embodiment of the re-evaporator, and Fig. 3 is a refrigerant piping system diagram showing a conventional technique. be. 1...Compressor, 4...Evaporator, 10...Reheater, 11...Saucer, 12...Reheat circuit, 13...
Reheat amount control valve, 20... re-evaporator, 21... re-evaporation circuit, 30... temperature regulator.

Claims (1)

[Scope of utility model registration request] In an air conditioner that includes a compressor 1, an evaporator 4, and a reheater 10, and is provided with a reheat circuit 12 that supplies part of the discharged gas to the reheater 10, the evaporator 4
A re-evaporator 20 for heating and re-evaporating the drain water is provided in the drain water receiving tray 11 condensed in the drain water, and a temperature of the air blown from the reheater 10 is detected on the leeward side of the reheater 10. A temperature regulator 30 is provided in the reheat circuit 12, and the temperature signal detected by the temperature regulator 30 is used to control the temperature of the blown air to be constant. A reheat amount control valve 13 that adjusts the amount of discharge gas to be supplied is interposed between the reheat amount control valve 13 and the reheater 10 in this reheat circuit 12, and the amount of discharge gas is supplied to the reevaporator 20. An air conditioner characterized in that a reevaporation circuit 21 that supplies one part of the air is branched.