JPS606683B2 - Air or gas dehumidifier - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an air or gas dehumidifier that can reduce the cooling temperature of a dehumidifying cooler to about -15 oo or lower.

A conventional air dehumidifier is, for example, as shown in Figure 1. Pressurized air of approximately 60 qo compressed by an air compressor enters the primary heat exchanger b through the humid air introduction pipe a, where it is heated to a low temperature. After exchanging heat with dry air, the pre-cooled air passes through a demister and enters a heat exchanger d into which a cold soot gas evaporator c is inserted.
Here, the dry air is cooled and dehumidified by exchanging heat with the evaporation temperature of 0° C. to -3° C., and the dry air is led out to the use side through the dry air outlet pipe e after passing through the primary heat exchanger b.

In the figure, the dotted line indicates the soot refrigeration cycle, f is the cold soot compressor, g is the cold soot simulator, h' is the cold soot receiver, i
is an expansion valve. If frost forms on the refrigerant evaporator c, the operation of the cold butterfly refrigeration cycle is stopped, and the frost on the cold soot evaporator c is dissolved and removed by high-temperature air introduced from the humid air introduction pipe a. In such a conventional method, a cold soot evaporator c
It is possible to lower the temperature only to about 0°C to -3°C. This is because if the temperature of the cold soot evaporator c is lowered to below -10-odd degrees Celsius, fog formation due to moisture in the air becomes severe, making it difficult to operate the refrigerant evaporator c. However, when dehumidifying humid air or gas, it is axiomatic that the lower the temperature, the more effective the dehumidifier is.

In order to solve these problems, the present invention lowers the temperature of the cooler in the dehumidifying heat exchanger to about -15qC, and then sends humid air to the heat exchanger to form a large amount of frost on the cooler. Then, stop sending the soot to the cooler, and continue sending humid air to melt the frost and cool the humid air, and transfer the cooled, less humid air to the next low-temperature heat exchanger. The temperature of the air or gas is lowered by feeding the air or gas into the air or gas without causing a large amount of cooling in the low-temperature cooler.

Furthermore, the present invention arranges a plurality of heat exchangers in series, makes it possible to effectively use the moist air inlet and dry air outlet provided in each heat exchanger, and furthermore, the heat exchanger can be connected to a cooler housed in each heat exchanger. when the cooler is frosted, the cold soot is stopped, and the first humid air is introduced into the heat exchanger with the frosted cooler; Next, when the air is exposed to another cooler, the feed of cold soot is switched as well as the feed of humid air, and by switching between multiple heat exchangers and coolers, the feed of humid gas is stopped during defrosting. In addition, when changing the soot feeding mode, the differential pressure inside the heat exchanger is detected and the solenoid valve is operated based on this differential pressure, and the switching operation is automatically performed. Furthermore, since the water droplets generated in the heat exchanger are cold water at a low temperature of approximately 0°C, the liquid sent to the cooler is supercooled in the water droplet reservoir to further improve the refrigeration effect.

Next, an embodiment of the present invention will be described with reference to FIG. 2. In FIG. Each heat exchanger la,
Inlet 4a, 4b for introducing air or gas and outlet ports 5a, 5b for dry air or dry gas are formed in lb.
, 4b and outlet ports 5a, 5b' are connected to a primary heat exchanger 7 and a coil 8 of this primary heat exchanger 7 via switching valves 6a, 6b, respectively. Further, the lower bottoms of the respective heat exchangers la and lb are conveyed to a common water droplet reservoir 9.

Furthermore, coolers 10a and 1 are provided in each of the heat exchangers la and lb.
0b is inserted, and the respective coolers oa and 18b' are supercooled and led out through the medium compressor 11, the condenser 12, the liquid pipe 13, and the liquid supercooler 14 inserted into the water droplet reservoir 9. The liquid pipes 15 are branched into branch liquid pipes 16a and 16b, and a solenoid valve 1 is installed in the middle of each of the branch liquid pipes 6a and 16a.
7a, 17b and temperature type expansion valves 18a, 18b are inserted. Furthermore, the gas pipes 19a and 19b led out from the respective coolers 10a and 10b join the suction gas pipe 201, and pass through the pressure regulating valve 21 on the way to the suction gas pipe 20', and are connected to the refrigerant compressor 1.
A lotus is passed through the inhalation side of 1. In addition, a float valve 2 is installed in the water droplet reservoir 9.
2 is inserted, and the cold water pipe 23 that leads out excess water is connected to the condenser 1.
It is electrically connected to the water supply side of the cooling water pipe 24 of No. 2.

Further, gas pipes 19a led out from each cooler 10a, 10b
, 19b, temperature-sensitive expansion valves 18a are provided in branch liquid pipes 16a, 16b, respectively.
, 18M are connected. Furthermore, a solenoid valve 17a is provided with a differential pressure detection device 26a, 26b such as a pressure switch for detecting the pressure difference between the air inlet side and the air outlet side of each heat exchanger la, lb in the middle of each branch liquid pipe 16a, 16b. , 17M are connected. Next, the air compressor 27, aftercooler 28, and air tank 29 are sequentially connected to the air or gas introduction side, and the air introduction pipe 38 led out from the air tank 29 is connected to the
The wet air pipes 32 led out from the primary heat exchanger 7 are passed through one switching valve 6a, and the dry air pipes 32 led out from the other switching valve 6b are passed through the primary heat exchanger 7. The coil 81 in the heat exchanger 7 is passed through and the coil 8 is passed through the dehumidifying air outlet 33. Next, a dehumidifying method using the apparatus of this embodiment will be explained.

The air is compressed by an air compressor 27 to produce high-temperature air containing moisture (resifu).

RO type 15000, screw type 70℃) is the primary heat exchanger via aftercooler 28 and air tank 29? To enter the,
Here, heat is exchanged with dry air cooled to around -10qo, and the temperature is increased to 35o0 in summer and 1500 in winter. −
The refrigerant medium sent from the refrigerant compressor lug 1 passes through the condenser lug 2, the liquid pipe 13, and the subcooler 14 to become a supercooled liquid, and is then sent to the electromagnetic valves Ta and Government from the branch liquid pipes 6a and 6b, respectively. ?b and expansion valves 18a, 18b to the coolers 10a, IQb, and the gas evaporated here returns to the cold soot compressor 11 again to form a refrigeration cycle.

Freon R22, Freon R12, etc. are used as the cold soot. Next, the air precooled by the primary heat exchanger 7 is introduced from the humid air pipe 31 into the first heat exchanger la via the sliding door valve 6a.

Here, heat is exchanged with the cooler 18a of -15o0 or less, and the moisture becomes frost and adheres to the surface of the cooler IQa. The dehumidified air is further transferred to a second heat exchanger lb adjacent to the lotus passage 3.
Here, it is further cooled by the cooler amount ob of -1500 or less to approximately -15o0, and then it passes through the dry air pipe 32 from the switching valve 6b to the primary heat exchanger? passes through the coil 8 of
The high-temperature, high-pressure compressed air introduced into the primary heat exchanger 71 is subcooled and taken out from the dehumidified air outlet 33. The evaporation temperature of the temporary cut is about -18oo, and the dry air is -15qo, 8k9/
If the dry air is near that fog point, the atmospheric pressure dew point is -38
℃. The moisture content in the air at this time is 0.210 g/me. When producing dry air in this way, most of the moisture in the air freezes in the cooler 10a at an evaporation temperature of -1500 or less in the first heat exchanger la, reducing the evaporation capacity and freezing. This narrows the gap between the coils of the cooler 10a, making it difficult for air to circulate. Therefore, a pressure difference occurs between the air introduction side and the air outlet side of the first heat exchanger la. This pressure difference is detected by the differential pressure detection device 26a, the solenoid valve 17a is closed, and the sending of cold soot to the cooler 10a in the first heat exchanger la is stopped, causing evaporation of the first cooler 10a. Ability stops. At this time, high-temperature air continues to be sent from the overflow air pipe 31 to the first cooler 10a, so this air is cooled by exchanging heat with the frost that has formed on the surface of the cooler 10a, and is cooled by the second heat exchanger. It is introduced into vessel lb.
The cold heat sources at this time are the sensible heat of melting until the frost below -1500 becomes 0°C, and the latent heat until the frost at 0°C becomes water at 0°C. Since most of the moisture in the first heat exchanger la has been removed in the second heat exchanger lb, the ability of the -15°C second cooler 10b is not hindered by frost formation.
The air introduced at a cooling temperature of -15°C or lower is effectively cooled and is sent out from the dry air pipe 32 as dry air with a temperature of 8k9/hour and a pressure fog point of -1500°. Next, when all the frost in the first cooler 10a has melted, the switching valves 6a and 6b are switched from the solid line passage to the dotted line passage, and the humid air is transferred to the second heat exchanger l.
The flow direction is changed from b to the first heat exchanger la.

At the same time, the pressure difference in the first heat exchanger la becomes 0, so the solenoid valve 17a opens by the operation of the differential pressure detection device 26a, and the first
The refrigerant is again sent to the cooler 10a, and the cooling action below -15q0 starts. This effect allows the second heat exchanger l
At b, dehumidification is performed mainly by frosting of the cooler 10b,
In the first heat exchanger la, the cooler 10a is cooled with less frost, and 8 kg/dry air with a pressure dew point of -1530 is sent out from the dry air outlet 5a. In this way, the first and second heat exchangers la, lb are used alternately for dehumidification and cooling, and are continuously used for 8k9/c tiger, pressure fog point -15
00 dry air is obtained.

In addition, approximately 0 water flowing down from the coolers 10a and 10b enters the water droplet reservoir 9.
Since the cold water at ℃ is stored, the cold soot liquid is supercooled by the liquid supercooler 14 inserted here, and the cold soot liquid is supercooled to the expansion valve 18a. It is sent to coolers 10a and 10b via 18b to increase the cooling effect. Furthermore, excess cold water is passed through a float valve 22 to a cold water pipe 23.
It is added to the cooling water of the condenser 12 to promote the condensation effect. Next, the embodiment shown in FIG. 3 will be described.

In FIG. 3, the heat exchangers la and lb are each constituted by a separate vessel, and are connected through a passageway 3 made of a passage pipe. Also, water droplets 9a and 9 are located at the bottom of the heat exchangers la and lb, respectively.
b, liquid subcooler 1 umbrellas and 14b are inserted in the middle of branch liquid pipes 16a and 16b, respectively, and float valves 22a and 22b are inserted into respective water droplet reservoirs 9a and 9b.
Cold water pipes 23a and 23b are passed through the cooling water pipes 23a and 23b, respectively, and these are passed through the cold water pipe 23 to the water supply side of the cooling water pipe 24 of the condenser 12. In this example, the heat exchanger la
, 1b, and water droplet reservoirs 9a, 9b are formed separately from the embodiment shown in FIG. 2, but other configurations and operations are the same as the embodiment shown in FIG.

In the above embodiments, two heat exchangers la and lb were used, but two or more heat exchangers may be used if necessary.

According to the present invention, a plurality of heat exchangers each housing an evaporator and communicating with each other through a communication passage are formed with mutually switchable moist air inlets and dry air outlets. Humid air or humid gas is introduced into one heat exchanger to remove moisture, and the moisture removed is introduced into the other heat exchanger to further lower the temperature and frost the evaporator to remove moisture. This makes it possible to remove moisture at low temperatures and achieve a high dehumidification effect, and the dehumidified dry air can be led out from the dry air outlet.

Furthermore, by switching the humid air inlet and dry air outlet, humid air is first introduced into the heat exchanger where the evaporator has been frosted, and then the evaporator is frosted, and the heat exchanger which is not cooled is further cooled. By introducing previously dehumidified air or gas and further dehumidifying at a low temperature, it is possible to increase the dehumidifying effect and at the same time remove the frost from the evaporator. In addition, in front of the expansion valve that sends cold soot to each evaporator, the pressure difference generated in the heat exchanger by the mist of each evaporator is detected and activated to send or stop the lining medium. Since a solenoid valve is installed, if a certain amount of frost forms on the evaporator to which the soot is being sent, the solenoid valve will be switched and the refrigerant will stop being sent. It is possible to automatically switch the opening soot feed according to the amount of mist in the evaporator. Furthermore, since a liquid supercooler was inserted in the middle of the liquid pipe that sends the liquid to the evaporator to the water droplet reservoir carried at the bottom of the heat exchanger, the medium liquid sent to the evaporator is transferred to the evaporator. The frost is melted and the water is supercooled at approximately 0°C, thereby improving the cooling effect of the evaporator and further increasing the dehumidifying effect. Furthermore, since the liquid supercooler is directly inserted into the water droplet reservoir at the bottom of the heat exchanger for heat exchange, there is less heat loss and piping etc. can be simplified.

[Brief explanation of the drawing]

FIG. 1 is an explanatory diagram of a conventional dehumidifying device, and FIGS. 2 and 3 are explanatory diagrams of a dehumidifying device showing different embodiments of the present invention. Tortoise a, lb...Heat exchanger, 4a, 4b...Moist air inlet, 5a, 5b...Dry air outlet, 9,9a
, 9b... Water bottle reservoir, 10a, 10b... Cooler L 13... Liquid pipe, 14, 14a, 14b
．． ...Liquid supercooler, 17a, 17b...Solenoid valve 18a, 18b...Expansion valve 26a, 26b.
...Differential pressure detection device. Figure 2 Figure 7/Figure 0

Claims (1)

[Claims] 1. A plurality of heat exchangers each having a humid air inlet and a dry air outlet that are connected to each other through a communication passage and can be switched to each other, and a water droplet reservoir is connected to the bottom of the heat exchanger. an evaporator connected to a refrigerant liquid pipe having an expansion valve in the middle; a liquid supercooler inserted into the water droplet reservoir provided in the middle of the refrigerant liquid pipe before the expansion valve; An air or gas dehumidification device comprising: a solenoid valve that operates by detecting a differential pressure generated within the heat exchanger provided in the refrigerant liquid pipe.