KR101224157B1 - Heatpump type dehumidifier apparatus - Google Patents

Abstract

PURPOSE: A heat pump type drying machine is provided to improve the quality of dried articles by individually controlling the temperature and humidity of each drying process. CONSTITUTION: A heat pump type drying machine is composed of a refrigeration cycle system and an air control system. The refrigeration cycle system comprises a compressor(1), outdoor and indoor condensers(20,21), a super cooler(31), an expansion valve(4), an evaporator(30), and a hot gas control valve(73). The outdoor and indoor condensers condense refrigerants compressed in the compressor. The super cooler cools the condensed refrigerants. The evaporator evaporates the refrigerants. The hot gas control valve controls the dehumidification function of the evaporator. The air control system comprises an air inlet, an air outlet, a suction chamber, a middle chamber, a circulation chamber, a fan chamber, an external air inflow chamber, an exhaust chamber, an air damper, and an exhaust fan. The suction chamber inhales humid air. The fan chamber supplies high-temperature air to objects. The exhaust chamber exhausts external air passing through the condenser.

Description

Heat Pump Type Dryer {HEATPUMP TYPE DEHUMIDIFIER APPARATUS}

The present invention relates to an agricultural and aquatic product drying apparatus applying a refrigeration air conditioning and drying system, and more particularly, by heating the low-temperature and humid air by the condensation heat of the condenser at the same time as the cooling and dehumidification, supplying the high-temperature dry air to the agricultural and aquatic products to dry the temperature and humidity It relates to a heat pump type dryer for controlling independently.

Drying systems using conventional methods for drying agricultural and marine products and refrigeration cycles are divided into solar drying and wind drying methods and hot air drying methods using electricity and fossil fuels (petroleum and coal), which are widely used in the past. However, due to the low production volume, it is used only for small scale drying.In the hot air drying method, a heater and a burner using electricity or fossil fuel are operated to heat low-temperature air to lower relative humidity, and forcibly blow dry water to dry matter. It is a system in which energy consumption is large in the form of being taken away and released into the air at a high temperature and high humidity, and if the humidity of the outside air is high, the efficiency of the drying process is rapidly reduced. In addition, the drying process is high, the color of the dried product is decolorized and deformed to deteriorate the quality of the product, the high temperature and humid air is discharged into the air without recycling, it is a drying process that consumes enormous energy in winter.

On the other hand, Republic of Korea Patent No. 10-0675900 (2007.01.23) discloses a cold air drying method such as agricultural and marine products, Figure 1 is a system configuration diagram showing a cold air drying method of conventional agricultural and marine products disclosed in the patent.

In the prior art system, referring to FIG. 1, the compressor 1, the outdoor condenser 20, the indoor condenser 21, the selection valves 70, 71, 72, 73, the cooler 31, and the expansion valve 4 are described. ), The evaporator 30, and the fans 60 and 61.

Referring to the operation of the conventional refrigeration cycle, when classified according to the operation combination type of the outdoor condenser 20 and the indoor condenser 21, it can be divided into cooling and dehumidification mode, the maximum dehumidification and transition mode and heating mode.

First, the cooling and dehumidifying mode uses the outdoor condenser 20, does not use the indoor condenser 21, the control valves 71 and 73 operate in the open operation, and the control valves 70 and 72 operate in the closed operation. After the heat exchange with the low-temperature air of the evaporator outlet in the supercooler (31), it is subcooled with the low-temperature refrigerant liquid, decompressed while passing through the expansion valve (4), and after the heat exchange with the indoor air in the evaporator (30) from the liquid phase to the gas phase After conversion, the compressor is sucked into the compressor 1, and the outdoor condenser bypass valve 70 and the indoor condenser selection valve 72 do not introduce refrigerant into the indoor condenser 21 by a CLOSE operation.

At this time, the indoor air is cooled to below the dew point temperature in the evaporator 30, and then reheated in the supercooler 31 in a humid state of low temperature after cooling and dehumidification by condensation on the surface of the heat exchanger of water vapor in the air.

Since the supercooler 31 has a smaller heat transfer area than the evaporator 30 and the outdoor and indoor condensers 20 and 21, the heating capacity of the air is not large, so the air at the outlet of the evaporator 30 is at a low temperature. It is discharged to the room after 60, and the maximum cooling capacity can be obtained during this cycle.

Next, the maximum dehumidification and transition mode opens the control valves 71 and 72 of the cooling and dehumidification mode, and closes the control valves 70 and 73 to the CLOSE operation. By using it constitutes a cycle of maximum dehumidification capacity.

Finally, in the heating mode, the control valves 70 and 72 of the dehumidification mode are opened, and the control valves 71 and 73 are closed. The indoor condenser 20 is used without using the outdoor condenser 20. By using 21), a maximum heating mode is formed.

However, in the conventional cycle, although the dehumidification amount and the heating capacity can be varied in the cooling and dehumidifying mode, the maximum dehumidification and the variation mode, and the heating mode, the variable humidity control is required in the agricultural and aquatic product drying process such as seaweed and anchovy. The time control range is too narrow to control with proper humidity, and the temperature control to the outdoor unit also increases the heat dissipation capacity of the outdoor unit to 1.25 to 1.5 times the evaporator heat capacity in the entire cycle, causing excessive cost increase, and individual independent control of temperature and humidity. Since it is not possible to precisely control the required humidity and temperature for drying according to the type of agricultural and marine products, deterioration of the drying efficiency of agricultural products may cause decay and discoloration of agricultural products by prolonged drying operation. There is a problem such as consuming.

1. Republic of Korea Patent No. 10-0675900 (2007.01.23)

The present invention has been made to solve the above problems of the prior art, and relates to a heat pump type dryer that can save the best quality and energy by individually controlling the temperature and humidity for cold and hot air drying of agricultural and marine products, The heat pump type dryer according to the present invention uses the waste heat of the condenser during the refrigeration cycle as a heat source for heating the room load and as a reheating heat source of the dehumidifying air, thereby drying the hot air without supplying additional energy, and evaporating the humid air introduced into the drying system. Can be dehumidified below the dew point temperature, reheat the air at the outlet of the evaporator to lower the relative humidity for continuous dehumidification.Independent control of the heat of condenser heating and the cooling dehumidification capacity of the evaporator allows the temperature and humidity to be controlled independently. Control the temperature and humidity of each drying process Apply to the drying process of agricultural products such as anchovy and seaweed (Haitai) that can improve the quality of the dried product by controlling it. Characterized in that can be saved.

Therefore, an object of the present invention is to independently control the temperature and humidity of the heat pump type dryer applying the refrigeration air conditioning system, and to selectively control the temperature and humidity of the cold air and hot air drying room of the agricultural and marine products according to the drying process and the dry matter To provide a heat pump type dryer that can save quality and energy.

The object of the present invention is a dehumidification system for cooling and dehumidifying the wet incoming air at the inlet of the drying system to below the dew point temperature in the evaporator; A heat pump cycle using waste heat from the condenser during the refrigeration cycle as a reheating heat source of dehumidifying air; Refrigerant cycle system consisting of a dehumidification capacity control system consisting of a hot gas control valve for controlling the high temperature and high pressure gas at the compressor outlet to the evaporator to control the cooling dehumidification capacity of the evaporator; and the temperature of the air at the outlet of the heat pump type dryer. It can be achieved by a high-quality and high-efficiency heat pump type drying system consisting of an air control damper system for the purpose of controlling the incoming air temperature of the drying chamber by controlling; and an air control system for individually controlling the temperature and humidity.

According to the present invention, the best quality and energy saving can be achieved by controlling the temperature and humidity separately for the cold and hot air drying of agricultural and marine products, and the waste heat of the condenser during the refrigeration cycle is used for heating the indoor load and as the reheating heat source of the dehumidifying air. By drying the hot air without supplying additional energy, it is applied to agricultural product drying processes such as anchovy and seaweed (Haitae), which can improve the quality of dried products by controlling temperature and humidity differently for each drying process. There is a variety of effects, such as the best to dry the taste and color of the dried product, and to save the energy input to the drying process.

1 shows a system diagram of an example of a drying system according to the prior art.
2 is a view showing a refrigerant system diagram of a heat pump type dryer according to the present invention.
3 is a front view of a heat pump type dryer according to the present invention;
4 is a cross-sectional view taken along line AA ′ of FIG. 3.
5 is a cross-sectional view taken along line BB ′ of FIG. 3.
6 is a cross-sectional view taken along line BB ′ of FIG. 3.
7 is a cross-sectional view taken along line CC ′ of FIG. 3.
8 is a cross-sectional view taken along line CC ′ of FIG. 3.
9 is a view showing a refrigerant system diagram of another embodiment of the heat pump type dryer according to the present invention.
10 is a diagram showing a humid air diagram of a standard cycle of a heat pump type dryer according to the present invention.
11 is a view showing a humid air diagram of the heat cycle of the heat pump type dryer according to the present invention.
12 is a view showing a humid air diagram of a variable dehumidification cycle of the heat pump type dryer according to the present invention.
13 is a diagram showing a humid air diagram of a variable dehumidification and arrangement cycle of the heat pump type dryer according to the present invention.
14 is a view showing an operation example of a conventional drying system.
15 is a view showing an operation example of a heat pump type dryer according to the present invention.

In one aspect, the present invention,

A compressor (1) for compressing and discharging the refrigerant gas at a state of high temperature and high pressure;

Outdoor and indoor condensers (20, 21) for condensing the refrigerant compressed by the compressor (1) into a liquid phase;

A super cooler (31) for cooling the high temperature refrigerant liquid condensed into the liquid phase in the condenser (20, 21) to a low temperature;

An expansion valve (4) for expanding the liquid refrigerant in the high pressure state cooled in the super cooler (31) into the liquid refrigerant in the low pressure state;

An evaporator (30) for evaporating the refrigerant expanded in the expansion valve (4) to return the refrigerant gas of low temperature and low pressure to the compressor while achieving a freezing effect by heat exchange with the object to be cooled using the latent heat of evaporation of the refrigerant; And

A refrigerant cycle system comprising a hot gas control valve (73) for controlling the dehumidification capacity of the evaporator (30);

An air inlet 501 and an air outlet 502;

A suction chamber 510 for introducing humid air;

An intermediate chamber 511 between the evaporator and the condenser;

A circulation chamber 512 after the condenser;

A fan chamber 514 for supplying hot dry air to the object to be dried by a circulation fan;

An outside air inlet chamber 515 for introducing outside air between the evaporator and the condenser;

An exhaust chamber 516 which exhausts outside air after passing through the condenser;

Air dampers M1 521, M2 522, M3 523, and M4 524; And

An air control system comprising an exhaust fan 62;

There is an outdoor condenser selection control valve 71 on the refrigerant pipe circuit connecting the outlet of the compressor 1 and the outdoor condenser 20, and the outlet of the outdoor condenser 20 is connected to the outlet of the indoor condenser 21. , The control valve 70 is connected on the refrigerant condenser 21 and the refrigerant condenser piping circuit, and the outlet of the indoor condenser 21 joins the pipe of the outlet of the outdoor condenser 20 so as to overcool 31. Inlet, the outlet of the supercooler 31 is connected to the expansion valve 4, the outlet of the expansion valve 4 is connected to the evaporator 30, the outlet of the evaporator 30 is connected to the compressor 1 In the piping bypassed from the outlet of the compressor 1 to the expansion valve outlet, there is a hot gas control valve 73, the outdoor condenser 20 has a condenser fan 61, an evaporator 30 and an indoor condenser 21. It provides a heat pump type dryer characterized in that the indoor unit fan 60 is attached.

The features and advantages of the present invention will become more apparent from the detailed description of the preferred embodiments based on the accompanying drawings. Prior to this, the terms or words used in this specification and claims should not be construed as being limited to the ordinary or dictionary meanings, and the inventors may properly interpret the concept of terms in order to best explain their own invention. Based on the principle that can be defined, it should be interpreted as meaning and concept corresponding to the technical idea of the present invention.

EMBODIMENT OF THE INVENTION Hereinafter, with reference to an accompanying drawing, 1st Embodiment of the heat pump type dryer by this invention is described concretely with respect to a refrigerant | coolant cycle system, an air control system, and a humidity control system.

First, the refrigerant cycle system of the heat pump type dryer according to the present invention has a refrigerant cycle system configuration as shown in FIG.

Reference numeral (1) is a compressor, which is used for the function of sucking the refrigerant gas and compressing and discharging it at high temperature and high pressure, and according to the purpose of use, reciprocating, crank, swash plate, wobble plate, rotary, scroll Various types of compressors can be applied, for example.

The discharge line of the compressor (1) is connected to the condenser (20, 21), the condenser (20, 21) is condensed into a liquid refrigerant of high temperature and high pressure by radiating the refrigerant gas discharged from the compressor (1) It is. Although not specifically illustrated in the drawings, the condenser 20 and 21 may include a plurality of tubes forming a predetermined flow path by connecting the inlet header and the outlet header and the inlet / outlet headers so as to communicate with each other, and the tubes. Conventional forms with corrugated heating fins stacked in between may be applied. Therefore, the air blown by the cooling fan passes through the heat transfer fins between the tubes, and in this process, the refrigerant flowing inside the condenser 20 and 21 is deprived of heat to the blown air to condense the refrigerant, and the condenser 20 ) Is a fluid (water, brine, etc.) heat exchanger in the form of a plate heat exchanger, a cell-and-tube heat exchanger, a spiral tube and a double tube heat exchanger in the form of heat loss to the fluid inside the heat exchanger to lose heat and condensation of the refrigerant is performed.

On the other hand, the inlet line side of the compressor 1 evaporates the refrigerant flowing from the expansion valve 4 (hereinafter referred to as "expansion valve"), which will be described later, to exchange heat between the cooled object and the refrigerant by using latent heat of evaporation. An evaporator 30 is connected to achieve the freezing effect. The evaporator 30 includes a plurality of tubes forming a predetermined flow path by connecting an inlet header and an outlet header and the inlet / outlet headers so as to communicate with each other, and a corgate type heat transfer fin stacked between the tubes. With conventional forms may be applied. Therefore, the air blown by the cooling fan passes through the heat transfer fins between the tubes, and in this process, the refrigerant flowing in the evaporator 30 takes the temperature (heat amount) of the blowing air, and thus the refrigerant evaporates.

At the inlet end of the evaporator 30, an expansion valve 4 for supplying the liquid refrigerant in the high temperature and high pressure state to the low pressure state refrigerant by the throttling action to supply the evaporator 30 to the evaporator 30 is easily performed. Is installed. Although not shown in the drawings, the expansion valve (4) is an internal pressure equalizing, capillary tube for adjusting the trajectory of the high-pressure refrigerant flow path through the pressure transfer rod by the expansion displacement of the diaphragm according to the temperature inside the temperature reduction chamber. By using the expansion pressure of the diaphragm through the external pressure control to adjust the trajectory of the high-pressure refrigerant flow path, generally using a thermostatic expansion valve, such as TEV, capillary and electronic expansion valve, and various types can be used.

Hereinafter, the refrigerant cycle system of the system of the present invention will be described in more detail with reference to the accompanying drawings.

In FIG. 2, there is an outdoor condenser selection control valve 71 on the refrigerant pipe circuit connecting the outlet of the compressor 1 and the outdoor condenser 20, and the outlet of the outdoor condenser 20 is connected to the outlet of the indoor condenser 21. The control valve 70 is connected to the refrigerant condenser piping circuit connected to the indoor condenser 21 and the compressor 1, and the outlet of the indoor condenser 21 joins the pipe of the outlet of the outdoor condenser 20 so that the super cooler ( 31, the outlet of the supercooler 31 is connected to the expansion valve 4, the outlet of the expansion valve 4 is connected to the evaporator 30, and the outlet of the evaporator 30 is connected to the compressor 1. And a hot gas bypass control valve 73 in the piping bypassed from the outlet of the compressor 1 to the expansion valve outlet, the outdoor condenser 20 has a condenser fan 61, an evaporator 30 and an indoor condenser. 21, the indoor unit fan 60 is attached.

In the above structure, the super cooler 31 may be integrally manufactured at the rear end of the evaporator 30, or the super cooler 31 may be integrally manufactured at the front end of the indoor condenser 21, or the super cooler 31 may be manufactured alone. Can be.

In addition, the control valve 70 may be manufactured in a structure in which the compressor 1 and the indoor condenser 21 are directly connected by a refrigerant pipe in a omitted form.

Second, the temperature control system of the heat pump type dryer according to the present invention has a configuration as shown in Figs.

Figure 3 is a front view of the heat pump type dryer of the present invention in general, it is obvious that it can be designed in various forms in addition to the cuboid structure.

FIG. 4 is a sectional view taken along line AA ′ of FIG. 3, FIG. 5 is a sectional view taken along line BB ′ of FIG. 3, FIG. 6 is a sectional view taken along line BB ′ of FIG. 3, FIG. 7 is a sectional view taken along line CC ′ of FIG. 3, and FIG. CC 'is a cross-sectional view.

In FIG. 3, the air inlet 501 is located at the top and the air outlet 502 is located at the bottom. In FIG. 7, the air inlet 501 is connected to the intake chamber 510, and the intake chamber 510 has an evaporator ( 30 is separated from the intermediate chamber 511 and the outside air inlet chamber 515 by the partitions 533 and 534 and the air damper M1 521, and the intermediate chamber 511 is an evaporator 30 and a condenser 21. Between the air inlet chamber 515 and the partition 531 of the outside air inlet chamber 515 is a wall that closes between the evaporator 30 and the condenser 21, or is completely sealed. It is a part opening and closing structure, the circulation chamber 512 is between the condenser 21, the fan chamber 514 and the exhaust chamber 516, the intermediate chamber 511 and the condenser 21 and partition 535 partitioned The exhaust chamber 516 is divided into a partition 532, and the circulation chamber 512 is a fan chamber 514 and has an open structure as shown in FIG. 4, and an outside air inlet chamber 515. Silver Evaporator (30) The space between the condenser 21 is divided into the intermediate chamber 511 and the outdoor air inlet chamber 515 is formed by the air dampers M1 521, M2 522 and the partitions 531, 534, and 536 as shown in FIG. 7. When the air damper M1 521 is attached to an opposite position as shown in FIG. 8, the air damper M1 521 is partitioned from the suction chamber by the partition 534, and the exhaust chamber 516 is circulated to the rear end of the outside air chamber 515. And a fan chamber 514, a fan chamber 514 and an air damper M3 523, a circulation chamber 512 and a partition 532, and an air damper M4 524. The exhaust fan 62 which is divided into the outside air and discharges the air of the exhaust chamber 516 is configured on the inner side or the outer side (not shown) of the air damper M4 524 as shown in FIG. Although not shown in the drawing, the air damper M3 523 is attached to the partition 532. At this time, the air damper M3 523 is structured to be blocked by a partition at the position of the air damper M3 523 of FIG. The fur M3 523 may be configured on both sides, and the air damper M3 523 of FIG. 5 may be configured to be attached to the partition 532. In FIG. 4, the fan chamber 514 may include a circulation chamber ( Located in the lower part of the 512, and there is no device between the fan chamber 514 and the circulation chamber 512, the air damper M3 (523) is opened and closed between the fan chamber 514 and the exhaust chamber 516. It is a structure to be partitioned.

The air dampers M1, M2, M3, and M4 (521, 522, 523, 524) are generally formed of an air damper and an electric motor, and are in a general form of ON-OFF control or proportional control according to a control signal. In the present specification, it is referred to as an air damper, and the air damper is configured in various forms such as a circle or a square, and the air dampers M1, M2, M3, and M4 (521, 522, 523, 524) are electrically or manually mixed. Applicable

An air damper M1 521 for bypassing air from the suction chamber 510 to the outside air inlet chamber 515 may be installed in the partition 533 between the suction chamber 510 and the intermediate chamber 511 as shown in FIG. 8. Although not shown, the air damper M1 521 may be installed at both positions as shown in FIGS. 7 and 8, and although not shown, the fan damper 514 may include the suction chamber 510 and the intermediate chamber ( 511, the circulation chamber 512, the outside air chamber 515, and the exhaust chamber 516, and the air inlet 501 is located at the bottom, the air outlet 502 is located at the top, or the fan chamber ( 514, the suction chamber 510, the intermediate chamber 511, the circulation chamber 512, the outside air chamber 515, and the exhaust chamber 516 are not shown in the drawing, but are designed in the same plane or in a complex configuration. can do.

Referring to the operation of the heat pump dryer of the present invention, classified according to the type of operation, 1) dehumidification and heating mode, 2) dehumidification and arrangement mode, 3) controlled dehumidification and heating mode, 4) controlled dehumidification and arrangement mode, 5 6) It can be classified into control arrangement mode, and 6) air inlet mode.

First, in the refrigerant cycle of the dehumidification and heating mode, the refrigerant gas of the high temperature and high pressure of the compressor 1 is operated by the CLOSE operation of the outdoor condenser control valve 71 as shown in FIG. Instead, the indoor condenser 21 is operated by the opening of the control valve 70 to be condensed into a liquid refrigerant in a gaseous state after heat exchange with air at the outlet of the supercooler 31, and then to the supercooler 31. After being cooled by the refrigerant liquid having a low temperature and high pressure and then passed through the expansion valve 4, the pressure is reduced and the outdoor condenser 20 is converted into the gas phase after being exchanged with the indoor air in the evaporator 30 and sucked into the compressor 1. ) Is operated in such a way that no refrigerant is introduced.

At this time, the intake air is cooled and dehumidified by heat exchange with the refrigerant inside the heat transfer tube of the evaporator 30, and is sequentially supplied from the supercooler 31 and the indoor condenser 21 to the fan 60 after being heated.

In the air control system of the dehumidification and heating mode, as shown in FIGS. 5 and 7, the humid air introduced at the intake port 501 is cooled to below the dew point temperature in the evaporator 30 to be dehumidified, and the super cooler 31. ) And the evaporator 30 are heated in the supercooler 31 and drawn into the intermediate chamber 511 and then heated in the condenser 21 and drawn into the fan chamber 514 in a hot dry air state. In the integral type of the 31 and the condenser 21, the air at the outlet of the evaporator 30 passes through the intermediate chamber 511 and is heated in the cooler 31 and the condenser 21, and the fan chamber 514 in a high temperature dry air state. Air introduced into the air chamber 515 through the evaporator 30 in the suction chamber 510 passes through the condenser 21 and passes through the opening of the fan damper M3 523. 514 is introduced, at which time the air dampers M2 522 and M4 524 operate CLOSE.

The operation form is a form of maximum dehumidification and maximum heating operation, and the air damper M1 521 is configured to determine an optimal air cooling flow rate when the incoming air is cooled below the dew point temperature and dehumidified during the cooling dehumidification of the evaporator 30. When the air damper M1 521 is opened, the amount of air bypassing the evaporator 30 increases, so that the amount of air passing through the evaporator 30 decreases, so that the amount of dehumidification increases, and the air damper M1 521. When this is closed, there is no air volume bypassing the evaporator 30, and the amount of air passing through the evaporator 30 is large, so that the amount of dehumidification decreases, but the optimum air flow rate is reduced depending on the capacity of the evaporator 30 and the compressor 1. Therefore, proper control is possible.

Next, 2) the refrigerant cycle of the dehumidification and arrangement mode is a refrigerant gas of the high temperature and high pressure of the compressor 1 in FIG. 2 to the outdoor condenser 20 by the operation (OPEN) of the control valve 71 of the outdoor condenser 20. It is supplied and operated, the indoor condenser 21 is operated by the OPEN operation of the control valve 70, the outdoor condenser 20 is condensed with the refrigerant in the liquid state in the gas state after heat exchange with the outside air, the indoor condenser The high temperature and high pressure refrigerant gas introduced into the 21 is condensed into the refrigerant liquid by the air at the outlet of the overcooler 31 and the outside air of the outside air inlet chamber 515, and the outdoor condenser at the refrigerant pipe at the outlet of the indoor condenser 21. It is combined with the refrigerant liquid of (20) and introduced into the super cooler (31), cooled by a low temperature and high pressure refrigerant liquid, and then decompressed while passing through the expansion valve (4). Converted to suction by the compressor (1) .

At this time, the intake air is cooled and dehumidified by heat exchange with the refrigerant inside the heat transfer tube of the evaporator 30, heated in the super cooler 31, and then supplied to the dry object by the fan 60.

In the air control system in the dehumidification and arrangement mode, the humid air introduced into the inlet 501 in FIGS. 6 and 7 is cooled and dehumidified in the evaporator 30 to below the dew point temperature, and the super cooler 31 and the evaporator. In the integrated type of (30), it is heated in the supercooler (31), drawn into the intermediate chamber (511) and then introduced into the fan chamber (514) through the indoor condenser (21), and of the supercooler (31) and the condenser (21) In the integrated type, the air at the outlet of the evaporator 30 is heated in the intermediate chamber 511 and heated in the cooler 31 to be introduced into the fan chamber 514 in a state of high temperature dry air, and the air damper M2 522 is opened. The outside air is introduced into the outside air inlet chamber 515, and the outside air of the outside air intake chamber 515 cools and condenses the high temperature and high pressure refrigerant gas inside the condenser 21, and the outside air is heated and exhausted. The fan 62 is discharged outward through the air damper 524 in the open state, and the air damper M3 523 performs a CLOSE operation.

Therefore, a small amount of air is drawn from the evaporator 30 to the outside air inlet chamber 515 and the middle chamber 511 in the outside air inlet chamber 515 through the partition 531 of the outside air inlet chamber 515 and the middle chamber 511. The pressure distribution is Pm (intermediate chamber) <Po (outer air inlet chamber) and moves from the high pressure air inlet chamber 515 to the middle chamber 511, and the partition 531 is inlet air inlet. In the structure in which the chamber 515 and the intermediate chamber 511 are completely enclosed, there is no air movement from the external air inlet chamber 515 to the intermediate chamber 511, and the air inlet chamber through the evaporator 30 in the suction chamber 510 ( 515) is also a small amount of air movement.

In the above driving mode, the air damper M1 is the same as the 1) operating mode of the dehumidification and heating mode.

In this mode, since the heat from the condenser 20 and 21 is discharged to the air damper M4 524 by the outdoor condenser 20 and the exhaust fan 62, temperature control is easy, and the capacity of the outdoor condenser 20 is minimized. Since it is possible to manufacture, the cost of the product is saved, and even when the outdoor condenser 20 is omitted as shown in FIG. 9, the air is supplied to the air damper M4 524 by the array fan 62 to the outside air through the air inlet chamber 515. By discharging the condensation heat of the indoor condenser 21 to the outside, it is possible to actively control the temperature of the object to be dried.

3) In the refrigerant cycle of the controlled dehumidification and heating mode, the refrigerant gas of the high temperature and high pressure of the compressor 1 of FIG. 2 is operated by the CLOSE operation of the control valve 71 of the outdoor condenser 20. ) Is not operated, and the indoor condenser 21 is operated by the OPEN operation of the control valve 70 to condense the liquid refrigerant in the gas state after heat exchange with the air at the outlet of the supercooler 31, and thus the supercooler. It is introduced into the (31) and cooled by the refrigerant liquid of low temperature and high pressure, and then depressurized while passing through the expansion valve (4), after being exchanged with the indoor air in the evaporator (30), the liquid is converted into the gas phase and sucked into the compressor (1). The outdoor condenser 20 draws hot gas of high temperature and high pressure at the outlet of the compressor 1 in the basic refrigeration cycle in which the refrigerant is not drawn into the rear end of the expansion valve 4 by opening the control valve 73. The pressure of the evaporator 30 is increased to control the amount of cooling dehumidification of the air drawn in from the suction chamber 510.

At this time, in order to control the cooling dehumidification amount of the evaporator 30 from 0% to 100% by the on-off operation or the proportional control operation of the control valve 73.

In the air control system in this mode, the humid air introduced into the inlet 501 in FIGS. 5 and 7 is cooled and dehumidified below the dew point temperature in the evaporator 30, and the super cooler 31 and the evaporator 30 are dehumidified. In the integral type of, it is heated in the supercooler 31, drawn into the intermediate chamber 511, and then heated in the condenser 21, drawn into the fan chamber 514 in a state of high temperature dry air, and the supercooler 31 and the condenser 21. ), The air at the outlet of the evaporator 30 is heated through the intermediate chamber 511 and heated in the cooler 31 and the condenser 21 to be introduced into the fan chamber 514 in a hot dry air state, and the suction chamber Air introduced into the outside air inlet chamber 515 through the evaporator 30 at 510 is introduced into the fan chamber 514 past the condenser 21 and through the air damper M3 523 open (OPEN) opening. The air dampers M2 522 and M4 524 operate CLOSE.

Next, as shown in FIG. 2, in the refrigerant cycle of the control dehumidification and arrangement mode, the high temperature and high pressure refrigerant gas of the compressor 1 is operated by the open operation of the control valves 70 and 71. And the condenser 21 are simultaneously supplied and operated, and the outdoor condenser 20 is condensed into a refrigerant in a liquid state in a gaseous state after heat exchange with the outside air, and the high temperature and high pressure refrigerant gas introduced into the indoor condenser 21 is The condenser is condensed into the refrigerant liquid by the air at the outlet of the cooler 31 and the outside air of the external air inlet chamber 515, and is combined with the refrigerant liquid of the outdoor condenser 20 at the refrigerant pipe at the outlet of the indoor condenser 21. After being cooled to the refrigerant liquid of low temperature and high pressure and then passed through the expansion valve (4), the pressure is reduced, and the heat is exchanged with the indoor air in the evaporator (30) and is operated in the form of being sucked into the compressor (1) by converting from the liquid phase into the gas phase.

At this time, the hot gas of the high temperature and high pressure at the outlet of the compressor 1 is introduced into the rear end of the expansion valve 4 by opening the control valve 73 to OPEN to increase the pressure of the evaporator 30 to increase the pressure in the suction chamber 510. It controls the amount of cooling dehumidification of the incoming air, and 3) controls the control valve 73 in the same manner as the control dehumidification and heating mode.

In the air control system in this mode, the humid air drawn in from the inlet 501 of FIG. 6 and FIG. 7 is cooled and dehumidified below the dew point temperature in the evaporator 30, and the supercooler 31 and the evaporator 30 In the integrated type, it is heated in the supercooler 31 and drawn into the intermediate chamber 511 and then passed through the indoor condenser 21 to the fan chamber 514. In the integrated type of the supercooler 31 and the condenser 21, the evaporator ( The air at the outlet of 30 is heated through the intermediate chamber 511 and heated in the cooler 31 and the indoor condenser 21 to be introduced into the fan chamber 514 in a hot dry air state, and the air damper M2 522 is opened. The outside air is introduced into the outside air inlet chamber 515, and the outside air of the outside air intake chamber 515 cools and condenses the high temperature and high pressure refrigerant gas inside the condenser 21, and the outside air is heated to exhaust. It is discharged out through the air damper 524 in the open state by the fan 62, and the air dam M3 (523) is a closed (CLOSE) operation.

Therefore, a small amount of air is drawn from the evaporator 30 to the outside air inlet chamber 515 and the middle chamber 511 in the outside air inlet chamber 515 through the partition 531 of the outside air inlet chamber 515 and the middle chamber 511. The pressure distribution is Pm (intermediate chamber) <Po (outer air inlet chamber) and moves from the high pressure air inlet chamber 515 to the middle chamber 511, and the partition 531 is inlet air inlet. In the structure in which the chamber 515 and the intermediate chamber 511 are completely enclosed, there is no air movement from the external air inlet chamber 515 to the intermediate chamber 511, and the air inlet chamber through the evaporator 30 in the suction chamber 510 ( 515) is also a small amount of air movement.

In the above driving mode, the air damper M1 is the same as the 1) operating mode of the dehumidification and heating mode.

In this mode, since the heat of the condenser 20, 21 is discharged to the air damper M4 524 by the outdoor condenser 20 and the array fan 62, temperature control is easy, and the capacity of the outdoor condenser 20 is the minimum capacity. The cost of the product can be saved because it can be manufactured, and the outdoor air through the air inlet chamber 515 to the air damper M4 524 by the array fan 62 even when the outdoor condenser 20 is omitted as shown in FIG. 9. By discharging the heat of condensation of the indoor condenser 21 to the outside, it is possible to actively control the temperature of the object to be dried.

Next, 5) the control arrangement mode can be applied to the dehumidification, the control dehumidification and the outdoor air inlet mode, the refrigerant cycle is a control valve 71 of the outdoor condenser 20 in the refrigerant gas of the high temperature and high pressure of the compressor 1 in FIG. It is supplied to the outdoor condenser 20 by the operation of OPEN, and the indoor condenser 21 is not operated by the CLOSE operation of the control valve 70, and the outdoor condenser 20 exchanges heat with outside air. After condensing into a refrigerant in a liquid state in the gas state, the indoor condenser 21 is a structure that only passes through the air of the outlet of the supercooler 31 without heating, the outdoor condenser in the refrigerant pipe of the outlet of the indoor condenser 21 It is combined with the refrigerant liquid of (20) and introduced into the super cooler (31), cooled by a low temperature and high pressure refrigerant liquid, and then decompressed while passing through the expansion valve (4). In the form of suction It is around.

In addition, in the air control system, the air damper M2 522 may be opened (OPEN) or open (OPEN) operation, and in the open (OPEN) operation of the air damper M2 522, the outside air is drawn into the outside room 515. The outside air of the outside chamber 515 is introduced into the fan chamber 514 through the air damper M3 523 without being heat exchanged with the condenser 21, and the air damper M4 524 is closed (CLOSE). Drive.

This mode is operated by the heating capacity between the array operation and the heating operation in a controlled arrangement method in which the temperature of the drying chamber is applied to a more precise control operation.

Next, 6) the air inlet mode It can be applied to 1) dehumidification and heating mode, 3) control dehumidification and heating mode and 5) control arrangement mode, and the refrigerant cycle can be applied to the same mode as above.

In addition, the air control system is the same type as all the above modes, the air damper M2 (522) is open (OPEN) to draw the outside air into the air inlet 515, the outside air of the air inlet 515 is a condenser Cooling and condensation of the refrigerant gas of the high temperature and high pressure in the inside of the 21, and the outside air is heated to enter the fan chamber 514 through the air damper M3 (523), the air damper M4 (524) is closed (CLOSE) operation Do it.

This mode is a type of operation to prevent fresh air by introducing fresh air into the drying chamber after a long period of drying operation due to the condensation gas and odor generated in the drying chamber adversely affects the quality of the product.

Although not shown in the drawings in the first embodiment, if the control valve 70 is omitted, 1) dehumidification and heating mode, 2) dehumidification and arrangement mode, 3) control dehumidification and heating mode, 4) control dehumidification and arrangement mode, and 6) The outside air inlet mode is operated in the same form, and 5) only the control arrangement mode operation form cannot be realized.

EMBODIMENT OF THE INVENTION Hereinafter, it demonstrates regarding 2nd Embodiment of the heat pump type dryer which concerns on this invention.

The second embodiment of the heat pump type dryer according to the present invention may be composed of a refrigerant cycle system, an air control system and a humidity control system, as shown in the accompanying drawings.

First, the refrigerant cycle system is connected to the refrigerant pipe between the compressor 1 and the indoor condenser 21, the outlet of the indoor condenser 21 is introduced into the super cooler 31, the outlet of the super cooler 31 is the expansion valve (4), the outlet of the expansion valve (4) is connected to the evaporator (30), the outlet of the evaporator (30) is connected to the compressor (1), and is bypassed from the outlet of the compressor (1) to the expansion valve outlet There is a hot gas bypass valve 73 in the losing pipe, and the indoor unit fan 60 is attached to the evaporator 30 and the indoor condenser 21.

In the above structure, the super cooler 31 is integrally manufactured at the rear end of the evaporator 30, or the super cooler 31 is integrally manufactured at the front end of the super condenser 21, or the cooler 31 is manufactured alone. Can lose.

Referring to the operation of the heat pump dryer according to the second aspect, according to the operation mode of the heat pump dryer, 1) dehumidification and heating mode, 2) dehumidification and arrangement mode, 3) controlled dehumidification and heating mode, 4) 5) Can be classified into controlled dehumidification and arrangement mode, 5) outside air inlet mode.

First, 1) in the refrigerant cycle of the dehumidification and heating mode, the refrigerant gas of the high temperature and high pressure of the compressor 1 in FIG. 9 is a liquid in the gas state after heat exchange with the air at the outlet of the overcooler 31 by operating the indoor condenser 21. After being condensed into the refrigerant in the state and introduced into the super cooler 31 and cooled by the low-temperature and high-pressure refrigerant liquid, it is decompressed while passing through the expansion valve 4, and is exchanged with the indoor air in the evaporator 30 to convert from the liquid phase to the gas phase. It is operated in the form of suction in (1).

The air control system in the dehumidification and heating modes is the same as in the first embodiment.

Next, 2) in the refrigerant cycle of the dehumidification and arrangement mode, the high temperature and high pressure refrigerant gas of the compressor 1 is supplied to the indoor condenser 21 in FIG. 9 and operated, and the high temperature and high pressure refrigerant introduced into the indoor condenser 21 is operated. The gas is condensed into the refrigerant liquid by the air at the outlet of the overcooler 31 and the outside air of the entrance chamber 515, which is the outside air, and enters the supercooler 31 through the outlet of the indoor condenser 21 to the refrigerant liquid of low temperature and high pressure. After cooling, the pressure is reduced while passing through the expansion valve (4), and the heat is exchanged with the indoor air in the evaporator (30), and then the liquid is converted into the gaseous phase and operated in the form of being sucked into the compressor (1).

The air control system in the dehumidification and arrangement modes is the same as in the first embodiment.

3) In the refrigerant cycle of the controlled dehumidification and heating mode, the refrigerant gas of the high temperature and high pressure of the compressor 1 in FIG. 9 is in a gas state after the heat exchange with the air at the outlet of the overcooler 31 by operating the indoor condenser 21. Condensed into a liquid refrigerant in the coolant (31), cooled to a low-temperature, high-pressure refrigerant liquid, and then depressurized while passing through the expansion valve (4). The control valve 73 opens the hot gas of the high temperature and high pressure at the outlet of the compressor 1 in the basic refrigeration cycle in which the refrigerant is introduced into the outdoor condenser 20 without the refrigerant flowing into the condenser 20. Opening the rear end of the expansion valve 4 to OPEN increases the pressure of the evaporator 30 to control the amount of cooling dehumidification of the air introduced from the suction chamber 510.

At this time, in the OPEN operation of the control valve 73, the amount of passing hot gas may be controlled according to the size of the connection pipe of the control valve 73 to control the cooling dehumidification capacity from 0 to 100%, which is the evaporator 30. If the amount of hot gas drawn into is large, the dehumidification is 0% because the incoming air cannot be cooled below the dew point temperature. If the amount of hot gas is small, the dehumidification capacity is 100%. It is decided.

The air control system in this mode is the same as in the first embodiment.

4) In the refrigerant cycle of the controlled dehumidification and arrangement mode, the high temperature and high pressure refrigerant gas of the compressor 1 is supplied to the indoor condenser 21 and operated in FIG. 9, and the high temperature and high pressure refrigerant introduced into the indoor condenser 21 is operated. The refrigerant gas is condensed into the refrigerant liquid by the air at the outlet of the overcooler 31 and the outside air of the entrance chamber 515, which is the outside air, and flows into the overcooler 31 at the refrigerant pipe at the outlet of the indoor condenser 21. After cooling with the refrigerant liquid, the pressure is reduced while passing through the expansion valve (4), and the heat is exchanged with the indoor air in the evaporator (30), and the liquid is converted into the gas phase and operated in the form of being sucked into the compressor (1).

At this time, the hot gas of the high temperature and high pressure at the outlet of the compressor 1 is introduced into the rear end of the expansion valve 4 with the control valve 73 opened to increase the pressure of the evaporator 30 to be drawn in the suction chamber 510. 3) Control the control valve 73 in the same manner as the control dehumidification and heating mode.

The air control system in this mode is the same as in the first embodiment.

Next, 5) The outdoor air drawing mode is the same as in the first embodiment.

10 is a representative graph of the characteristics of the standard cycle (dehumidification and heating mode) of the heat pump dryer according to the present invention in terms of temperature and absolute humidity, when comparing the change in the amount of air (temperature, absolute humidity) of the air inside the dryer , The air state change of the conventional dryer is air inlet (1)-> air outlet (2 ') of the evaporator (30)-> heating (3') of the condenser 21, the air state of the heat pump type dryer of the present invention When comparing the air inlet (1)-> air outlet (2)-> condenser (21) heating (3) of the outside air, the amount of dehumidification is the conventional form ΔX) 1-3 '= X1-X3' Since the dehumidification amount of the present invention is ΔX) 1-3 = X1-X3, the amount of dehumidification of the heat pump type dehumidifier of the present invention is ΔX) 1-3 '<ΔX) 1-3, and the heating capacity is ΔT) 3'-2 '= T2'-T3', and T) 3-2 = T3- T2 of the present invention, so that the heating capacity is large at ΔT) 3'-2 '<T) 3-2. , The heat pump dryer of the present invention has high dehumidification and high heating It is a more efficient heat pump dryer because of its ability.

11 is a graph showing the dehumidification and arrangement mode of the heat pump dryer according to the present invention, ΔT) 3-3 '= T3-T3' by the operation of the air dampers M2, M3, M4 and the exhaust fan 62; By arranging as much as possible, it is possible to control the temperature of the dried product, which is the drying of agricultural and marine products such as laver (Haitai) and laver, which require optimum conditions such as the color of the dried product and the deformation of the product when dried at an appropriate temperature in the drying process. It is an essential control item in the process.

12 is a graph showing the variable air dehumidification and heating mode of the heat pump dryer according to the present invention, the air state change in the dehumidification mode inlet (1)-> the air outlet of the evaporator (30)-> condenser ( 21) Change in air condition of heating (3) and variable dehumidification mode Induction of fresh air (1)-> air outlet (2 ') of evaporator (30)-> condenser (21) heating (3') ΔX) 1-3 '= X1-X3' and the standard dehumidification amount is △ X) 1-3 = X1-X3, so ΔX) 1-3 '<ΔX) 1-3, so the standard dehumidification mode The dehumidification capacity is reduced, which is essential control in the drying process of agricultural and marine products such as Kim (Haitai), which requires optimal conditions such as the color of the dried product and the deformation of the product when dried at an appropriate humidity. Item.

FIG. 13 is a graph showing the variable dehumidification and the arrangement of the humid air of the heat pump dryer according to the present invention, in which the operation of the air dampers M2, M3, M4 and the exhaust fan 62 is applied to ΔT) 3'-3 "= T3 '. -T3 "can be adjusted to adjust the temperature of the dried product, which is the agricultural and marine products such as Kim (Hai-tae), which requires the optimal conditions such as the color of the dried product and the deformation of the product when dried at an appropriate temperature in the processing of the dried product Essential control items for the drying process.

FIG. 14 is a view illustrating a laver (Haitai) dryer, which is one of the conventional agricultural and aquatic product drying forms. An upper part of the drying chamber 600 includes an exhaust fan 602 and a dry laver 607 and 608. 603, a heat source heater 605, an outside air inlet window 609, an upper chamber 610, a fan chamber 611, a lower chamber 612, and an outside chamber 614. , 608 is a structure that rotates, the air is supplied to the heater 605 by the circulation fan 603 and heated to dry the high temperature (55 ℃ ~ 65 ℃) dry (relative humidity: 25% ~ 35%) Air supplied to the 612 to dry the dried seaweed and the low temperature and humid air is partially discharged to the exhaust fan 602, the remainder is mixed with the fresh air introduced through the outside air inlet window 609 after the circulation fan 603 It is a type that is driven in and operated repeatedly.

The hot air drying method such as the electric heater method or the oil burner discharges the heated air to the outside by the exhaust fan, which causes high energy loss and the drying and drying at a high temperature, resulting in color and damage of the product. As a result, energy consumption is increased compared to high-efficiency heat pump method, which leads to a cost increase, thereby weakening the competitiveness of the steaming industry.

FIG. 15 is a view illustrating a laver (Haitai) dryer, which is one application type of the heat pump type dryer of the present invention, in which an exhaust fan 602 is provided on an upper part of a drying chamber 600, and laver (607, 608) to be dried. And, in the form of a heat pump dryer consisting of a circulation fan 603, an outside air inlet window 609, an upper chamber 610, a fan chamber 611, a lower chamber 612, an outside chamber 614, a steam 607. , 608 is a rotating structure, by supplying air of dry (relative humidity: 15% ~ 30%) of medium temperature (42 ℃ ~ 45 ℃) to the lower chamber 612 by the circulation fan 603 The dried and low temperature humid air is heated in a medium temperature (46 ° C. to 50 ° C.) through a heat pump dryer 500 (relative humidity: 5% to 18%) in the fan chamber 611 in the drying chamber upper chamber 610. After mixing with the air directly introduced into the) is introduced into the circulation fan 603 is repeatedly operated.

Since the hot air dehumidification drying method of the present invention does not discharge the heated air to the outside through the exhaust fan 602, there is little energy loss, and drying at medium temperature, there is no color and damage of the product, and the energy consumption is high because the high efficiency heat pump method is used. Reduced processing costs can contribute to strengthening the competitiveness of the laver industry and increasing income for fish farmers.

1: compressor 20: outdoor condenser
21: indoor condenser 30: evaporator
31: and cooler 60: indoor unit fan
500: heat pump dryer 501: air intake
502: air outlet 510: suction chamber
511: intermediate chamber 512: circulation chamber
514: fan room 515: outside room
516: ship cabin 521: air damper M1
522: air damper M2 523: air damper M3
524: Air Damper M4

Claims (12)

A compressor (1) for compressing and discharging the refrigerant gas at a state of high temperature and high pressure;
Outdoor and indoor condensers (20, 21) for condensing the refrigerant compressed by the compressor (1) into a liquid phase;
A super cooler (31) for cooling the high temperature refrigerant liquid condensed into the liquid phase in the condenser (20, 21) to a low temperature;
An expansion valve (4) for expanding the liquid refrigerant in the high pressure state cooled in the super cooler (31) into the liquid refrigerant in the low pressure state;
An evaporator (30) for evaporating the refrigerant expanded in the expansion valve (4) to return the refrigerant gas of low temperature and low pressure to the compressor while achieving a freezing effect by heat exchange with the object to be cooled using the latent heat of evaporation of the refrigerant; And
A refrigerant cycle system comprising a hot gas control valve (73) for controlling the dehumidification capacity of the evaporator (30);
An air inlet 501 and an air outlet 502;
A suction chamber 510 for introducing humid air;
An intermediate chamber 511 between the evaporator and the condenser;
A circulation chamber 512 after the condenser;
A fan chamber 514 for supplying hot dry air to the object to be dried by a circulation fan;
An outside air inlet chamber 515 for introducing outside air between the evaporator and the condenser;
An exhaust chamber 516 which exhausts outside air after passing through the condenser;
Air dampers M1 521, M2 522, M3 523, and M4 524; And
An air control system comprising an exhaust fan 62;
There is an outdoor condenser selection control valve 71 on the refrigerant pipe circuit connecting the outlet of the compressor 1 and the outdoor condenser 20, and the outlet of the outdoor condenser 20 is connected to the outlet of the indoor condenser 21. , The control valve 70 is connected on the refrigerant condenser 21 and the refrigerant condenser piping circuit, and the outlet of the indoor condenser 21 joins the pipe of the outlet of the outdoor condenser 20 so as to overcool 31. Inlet, the outlet of the supercooler 31 is connected to the expansion valve 4, the outlet of the expansion valve 4 is connected to the evaporator 30, the outlet of the evaporator 30 is connected to the compressor 1 In the piping bypassed from the outlet of the compressor 1 to the expansion valve outlet, there is a hot gas control valve 73, the outdoor condenser 20 has a condenser fan 61, an evaporator 30 and an indoor condenser 21. In the indoor unit fan 60 is attached,
The suction chamber 510 for introducing air of the air control system is located at the top of the heat pump type dryer, the air outlet 502 is located at the bottom of the heat pump type dryer, and the air inlet 501 is the suction chamber 510. In the suction chamber 510, the evaporator 30 is separated from the intermediate chamber 511 and the outside air inlet chamber 515 by partitions 533 and 534 and the air damper M1 521. 511 is in contact with the outside air inlet chamber 515 between the evaporator 30 and the condenser 21, the partition 531 of the outside air inlet chamber 515 is between the evaporator 30 and the condenser 21. Wall, which is completely enclosed or partially opened and closed, the circulation chamber 512 is between the condenser 21, the fan chamber 514 and the exhaust chamber 516, the intermediate chamber 511 and the condenser 21 and It is partitioned by the partition 535, and it is partitioned by the partition 532 with the exhaust chamber 516, and the circulation chamber 512 is open structure with the fan chamber 514. , The outside air chamber 515 is configured to divide the space between the evaporator 30 and the condenser 21 with the intermediate chamber 511, and the outdoor air inlet chamber 515 includes air dampers M1 521, M2 522, and Partitioned by partitions 531, 534, 536, and when air damper M1 521 is attached in the opposite position, it is interrupted by the partition 534 with the suction chamber, and exhaust chamber 516 to the rear end of the outside air chamber 515. It is in contact with the circulation chamber 512 and the fan chamber 514, the fan chamber 514 is separated by the air damper M3 (523), the circulation chamber 512 is separated by a partition 532, The air damper M4 524 is partitioned from the outside air, the exhaust fan 62 for discharging the air in the exhaust chamber 516 is configured in the form configured on the inner side or the outer side of the air damper M4 524, The air damper M3 523 is attached to the partition 532, and in this case, the air damper M3 523 is blocked by a partition at the position of the air damper M3 523, and the air damper M3 523 is formed on both sides. The structure of the damper M3 523 and the structure attached to the partition 532, the fan chamber 514 is located below the circulation chamber 512, the fan chamber 514 and the circulation chamber 512. An open structure without an apparatus therebetween, and between the fan chamber 514 and the exhaust chamber 516, an air damper M3 523 is partitioned into an open / close structure. The method of claim 1, wherein the outdoor condenser 20 of the refrigerant cycle system is in the form of heat exchange with the heat source including the air or water of the outside, the indoor condenser 21 is evaporator 30, in the flow direction of the indoor air, The supercooler 31 and the indoor condenser 21 are arranged in this order, and the indoor condenser 21 has a structure for exchanging heat with the low-temperature air passing through the evaporator 30 or the supercooler 31, and the supercooler 31. Is a structure for exchanging heat with air at the outlet of the evaporator 30, the outdoor condenser 20 is operated in accordance with the control form of the control valve 71, the indoor condenser 21 is a control form of the control valve 70 And the supercooler (31) is integrally formed with the evaporator (30) or with the indoor condenser (21) or integrally or independent of the heat pump type dryer. The heat pump type dryer according to claim 2, wherein the outdoor condenser (20), the control valve (71) and the condenser fan (61) are omitted. 3. The heat pump type dryer according to claim 2, wherein the control valve is omitted. The method of claim 1, wherein the hot gas of the high temperature and high pressure at the outlet of the compressor (1) is controlled to enter the rear end of the expansion valve (4) by controlling the control valve (73) to control the amount of cooling dehumidification of the evaporator (30), 30. A heat pump type dryer, characterized in that the variable dehumidification is performed by an on-off operation or a proportional control operation of the control valve 73 to control the amount of cooling dehumidification of 0 to 100%. delete The air damper M1 521 for bypassing air from the suction chamber 510 to the outside air inlet chamber 515 is provided in a partition 533 between the suction chamber 510 and the intermediate chamber 511. Heat pump type dryer, characterized in that installed in the partition or partition (533) and partition (534), respectively. The air conditioner of claim 1, wherein the fan chamber 514 comprises an upper structure of an intake chamber 510, an intermediate chamber 511, a circulation chamber 512, an outside air chamber 515, and an exhaust chamber 516. A heat pump type dryer, characterized in that the inlet portion 501 is located under the heat pump type dryer, and the air outlet 502 is located above the heat pump type dryer. 2. The air damper M3 523 is opened, the air dampers M2 522 and M4 524 are closed, and the outdoor condenser control valve 71 is closed. In operation, the outdoor condenser 20 is not operated, and the indoor condenser 21 is operated by the opening OPEN of the control valve 70 to exchange liquid with the air at the outlet of the supercooler 31. After being condensed into the supercooler (31) and cooled with a low temperature and high pressure refrigerant liquid, it is decompressed while passing through the expansion valve (4), and after being heat exchanged with the indoor air in the evaporator (30), is converted into a gas phase in the liquid phase (1) Heat pump type dryer, characterized in that configured to adjust the maximum dehumidification capacity by operating in a form that does not draw refrigerant into the outdoor condenser 20 in the form sucked in. The air dampers M2, M3, and M4 are selectively controlled in the heating mode, the array mode, and the air inlet mode, so that the air dampers M2 and M4 are closed in the heating mode, and the air dampers M3 are in the open operation. In the arrangement mode, the air dampers M2 and M4 operate in an open operation, the air dampers M3 operate in a closed operation, and in the external air inlet mode, the air dampers M2 open and operate, and the air dampers M3 and M4 operate in a closed operation, and the exhaust fan (62). ) Is configured to operate only in array mode. The exhaust fan 62 for discharging the air of the exhaust chamber 516 is configured in the inner side or the outer side of the air damper M4 524, the air damper M3 (523) A heat pump type dryer, characterized in that it is configured to be attached to the partition 532, attached to the lower part of the exhaust chamber, or both. According to claim 1, wherein the air dampers M1, M2, M3, M4 (521, 522, 523, 524) is composed of an air damper and an electric motor, in the form of on-off control or proportional control according to the control signal In the form of an air damper, it is configured in the form of a circular or square, the air dampers M1, M2, M3, M4 (521, 522, 523, 524) is characterized in that the electric or manual mixed application configured Pump dryer.

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