KR20100137050A - Refrigeration and air conditioning system - Google Patents

Abstract

PURPOSE: A freezing and air-conditioning system is provided to enable the waste heat of a condenser to be used for heating an indoor load and for re-heating the dehumidified air. CONSTITUTION: A freezing and air-conditioning system comprises a compressor(1), a condenser(20), an expansion valve(70), an evaporator(30), a heat exchanger and a control unit. The compressor compresses the refrigerant gas to have a high-pressure and high-temperature state. The condenser condenses the compressed refrigerant to the liquid. The expansion valve expands the condensed liquid refrigerant to the low-pressure liquid refrigerant. The evaporator evaporates the expanded refrigerant and returns the low-pressure and low-temperature refrigerant gas to the compressor. If a heat exchanger system, which consists of an outdoor condenser, an indoor condenser, an outdoor receiver and an indoor receiver, requires a combined operation, the heat exchanger selectively performs it. The control unit consists of an outdoor-condenser bypassing control valve, an outdoor-condenser selecting control valve, an indoor-condenser selecting control valve and an indoor condenser bypassing control valve.

Description

Refrigeration and Air Conditioning System {REFRIGERATION AND AIR CONDITIONING SYSTEM}

The present invention is an application of a refrigeration air conditioning system, and more specifically, energy-saving type, such as a constant temperature and humidity device system for constantly adjusting the temperature and humidity of a computer room in which a computer or an electronic device is installed, and a cooling dehumidification system for cold air drying of agricultural and marine products. The system relates to the use of 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 for the dehumidifying air, which performs the constant temperature and humidity function without supplying additional energy. By reheating the air coming out, the relative humidity is lowered to allow continuous dehumidification.

Conventional constant temperature and humidity systems and cold air drying systems include the following.

<Example 1>

 9 is a constant temperature / humidity system composed of a compressor 1, a condenser 20, an expansion valve 70, an evaporator 30 and an electric heating coil 25, which is operated by a general refrigeration cycle during cooling, heating and room temperature. At the time of adjustment, it is a cycle operated by operating the electric heating coil 25.

However, in the conventional cycle, the energy consumption rate is high by using the electric coil 25 as the heating heat source, and during the room temperature constant temperature control, the refrigerating cycle and the electric heater are operated at the same time, resulting in high power consumption and an increase in the outside air temperature in summer. This condensation pressure rise has a disadvantage in that the power consumption of the compressor is increased.

 <Example 2>

 10 is disclosed in Korean Patent Application No. 10-2001-0032629 as a conventional constant temperature and humidity system.

10 is a system configuration diagram showing a conventional constant temperature and humidity cycle disclosed in the above publication.

This cycle controls the basic cycle with the compressor 101, the outdoor condenser 110, the indoor condenser 170, the evaporator 160 and the control valves 190, 201.

First, the cooling cycle is a general refrigeration cycle operated by the compressor 101, the outdoor condenser 110 and the evaporator 160, and the heating cycle is the compressor 101, the indoor condenser 170, the outdoor condenser 110 and the evaporator. As a cycle being operated at 160, the main principle is that by heating the hot gas into the indoor condenser 330 during heating can be heated without a separate heat source.

However, in the above conventional cycle, the refrigerant liquid at the outlet of the indoor condenser 170 is overcooled at the outdoor condenser 110 during the winter heating operation so that the amount of heat of cooling at the evaporator 160 increases, resulting in a decrease in the amount of heating heat. During the summer heating and dehumidification operation, the refrigerant liquid at the outlet of the indoor condenser 170 is heated by heat exchange with the external hot air in the outdoor condenser 110, so that flash gas may be generated, and thus the cooling capacity of the evaporator 160 may be reduced. And, the power of the compressor is increased by increasing the pressure drop when passing through the indoor condenser 170 and the outdoor condenser 110, there is a disadvantage that the system efficiency is lowered because the indoor condenser 170 is not used during the dehumidification and cooling operation.

<Example 3>

        11 is disclosed in the Republic of Korea Patent Publication No. 202-0024692 in a conventional drying system.

11 is a system configuration diagram showing only a refrigeration cycle portion of the conventional drying system disclosed in the above publication, which includes a compressor 1, an outdoor condenser 20, an indoor condenser 21, an evaporator 30, and a control valve 50, 51. ), And the basic drying cycle is operated by the compressor (1), the indoor condenser (21), the expansion valve (70) and the evaporator (30), and the air cooled below the dew point temperature in the evaporator (30) is condensed. Moisture is removed and reheated in the indoor condenser 21 and continuously introduced into the drying chamber at a low relative humidity, and the outdoor condenser (only when the temperature of the drying chamber is high or the pressure of the condenser 21 is high during operation) 20) It is a system that works.

However, in the conventional cycle, there is a risk of burnout of the compressor 1 due to the rapid change of the high and low pressure during cycle change during operation, and the increase of the liquid compression and superheat on the suction side of the compressor 1, and the outdoor condenser 20 ) Since the indoor condenser 21 is not used during operation, there is a disadvantage in that the water removal ability is lowered because the overcooling operation is not performed.

The present invention relates to a refrigeration air conditioning system, and relates to an energy-saving system such as a constant temperature and humidity device system and a cooling dehumidification system, wherein waste heat of a condenser is used for heating an indoor load and reheating heat source of dehumidified air during a refrigeration cycle. It performs constant temperature and humidity function without supplying additional energy.In the drying system, it is possible to continuously dehumidify by lowering the relative humidity by reheating the air that is cooled and dehumidified below the dew point temperature, and for stable operation of the cycle. It can be operated in cooling mode, maximum dehumidification and constant temperature mode, and each mode is controlled in multiple stages for temperature and humidity control, and it can be used as condenser function of indoor condenser, supercooling of refrigerant and reheater of cooling air. I improved the dehumidification ability To provide a cycle.

In addition, to prevent the rise of the condensation pressure during operation and the liquid compression of the refrigerant at the compressor inlet to improve the performance and to prevent the burner of the compressor, to provide a system that reduces the power required of the system.

The present invention is an outdoor condenser 20, the indoor condenser 21, the control valve (50, 51, 52, 53), the outdoor receiver 40 and the indoor receiver 41 is a conventional refrigeration air conditioning cycle compressor (1) ), Which is attached to the expansion valve 70 and the evaporator 30, by introducing waste heat of the outdoor condenser 20 into the indoor condenser 21 by controlling the control valves 50, 51, 52, and 53. By using it as a heat source for heating the room load and reheating the dehumidifying air, it performs the constant temperature and humidity function without supplying additional energy, and when the indoor condenser 21 is used as the supercooling function to improve the cooling dehumidification capacity, The dehumidification amount is increased by the improvement, and the condensation pressure is increased during operation and the liquid compression of the refrigerant at the compressor inlet is prevented, thereby improving the performance and preventing the compressor from being burned, and reducing the power consumption of the system.

The present invention relates to a system using a heat pump cycle in a refrigeration air conditioning system, and relates to an energy-saving system such as a constant temperature / humidity device system and a cooling dehumidification system. By using it as a heating heat source, it performs constant temperature and humidity function without supplying additional energy, and in the drying system, it is possible to continuously dehumidify by lowering the relative humidity by reheating the air that is cooled and dehumidified below the dew point temperature. It can be operated in cooling mode, maximum dehumidification and constant temperature mode for normal operation, and each mode is controlled in multiple stages for temperature and humidity control, and it can be used as condenser function of indoor condenser or as reheater of refrigerant supercooling and cooling air. Improves cooling ability and dehumidification ability, It prevents the increase of condensation pressure and the liquid compression of refrigerant at the compressor inlet during operation, thereby improving the performance and preventing the compressor from being burned, and reducing the power consumption of the system.

In order to achieve the above object, the refrigeration air conditioning system according to the present invention, a compressor for compressing and discharging the refrigerant gas in a state of high temperature and high pressure, a condenser for condensing the refrigerant compressed in the compressor in the liquid phase, condensed in the condenser An expansion valve for expanding a liquid refrigerant in a high temperature and high pressure state into a liquid refrigerant in a low pressure state, and using a latent heat of evaporation of the refrigerant while evaporating the refrigerant expanded in the expansion valve to achieve a freezing effect by heat exchange with the object to be cooled. In the refrigeration air conditioning system comprising an evaporator for returning a low-temperature, low-pressure gaseous refrigerant gas to the compressor,

A heat exchanger unit in which a combined operation is optionally performed in a heat exchanger system including an outdoor condenser 20, an indoor condenser 21, and a receiver 40, 41 between the compressor 1 and the expansion valve 70;

The outdoor condenser 20 and the indoor condenser 21 is characterized in that the refrigerant control unit consisting of control sides (50, 51, 52, 53) for controlling the flow of the refrigerant for the selective combination operation.

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, terms or words used in the present specification and claims should not be construed as being limited to the common 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.

Hereinafter, an embodiment of a heat pump according to the present invention will be described with reference to the accompanying drawings.

1 is a cycle diagram showing a schematic diagram of a refrigeration air conditioning system (constant temperature humidity or dehumidification system, etc.) according to the present invention.

Reference numeral 1 denotes a compressor, which is used to inhale refrigerant gas, compress it at high temperature and high pressure, and discharge it, and various forms such as reciprocating type, crank type, swash plate type, wobble plate type, rotary type, and scroll type depending on the purpose of use. Compressor can be applied.

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 shown in detail here, the condenser 20 and 21 may include a plurality of tubes forming a predetermined flow path by connecting the inlet header, the outlet header and the inlet / outlet headers so as to communicate with each other, and between the tubes. Conventional forms with corgate-type heat transfer fins laminated to can 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 condenser 20 and 21 is deprived of heat to the blowing air, thereby performing the condensation of the refrigerant.

On the other hand, the inlet line side of the compressor (1) by evaporating the refrigerant flowing from the expansion valve 70 to be described later by using the latent heat of evaporation heat exchanged between the object and the refrigerant to be cooled by the evaporator (30) Is connected. 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 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 70 for supplying the liquid refrigerant in the high temperature and high pressure state to the refrigerant in the low pressure state by the throttling action to supply the evaporator 30 to the evaporator 30 is easily performed. Is installed. Although not shown in detail here, the expansion valve 70 has an internal pressure equalizing, capillary tube for controlling 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 thermostat chamber. The thermostatic expansion valve, generally called TEV, can be used in various forms, such as external pressure regulation to control the trajectory of the high-pressure refrigerant flow path by the expansion displacement of the diaphragm.

Hereinafter, the configuration of the system of the present invention will be described with reference to the drawings.

In FIG. 1, there is an outdoor condenser selection control valve 51 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 outdoor receiver 40. The outlet of the outdoor liquid storage tank 40 is connected to the indoor condenser 21 and the control valve on the bypass pipe connecting the outdoor receiver 40 between the compressor 1 and the control valve 51. There is a control valve (52) on the pipe connecting the indoor condenser (21) at the rear end of the confluence of the control valve (50) and the pipe of the outlet of the outdoor receiver 40, the control valve (50) There is a control valve 53 on the bypass piping that joins the rear end of the indoor condenser 21 between the confluence point 52 and the rear end of the pipe at the outlet of the outdoor receiver 40 and the outdoor condenser 21, and the indoor condenser 21. The conduit of the outlet pipe of the outlet and the control valve 53 is connected to the indoor receiver 41, and the outlet of the indoor receiver 41 is connected to the expansion valve 70. In the system in which the outlet of the expansion valve 70 is connected to the evaporator 30, the outlet of the evaporator 30 is connected to the suction side of the compressor 1, the outdoor condenser 20 has a condenser fan ( 60), the indoor unit fan 61 is attached to the evaporator 30 and the indoor condenser 21.

Referring to the operation of the present invention, when classified according to the operating combination type of the outdoor condenser 20 and the indoor condenser 21, it can be largely classified into 1) cooling mode, 2) maximum dehumidification mode and 3) constant temperature mode.

First, in the cooling mode, the refrigerant of the high temperature and high pressure of the compressor 1 is opened in the open condenser selection valve 51 to open the condenser selection valve 51. The refrigerant at the outlet of the outdoor condenser 20 is bypassed to the indoor condenser 21 by the OPEN operation of the indoor condenser bypass valve 53 through the outdoor receiver 40 and the expansion valve 70. After depressurizing and passing through the indoor air in the evaporator 30, the liquid is converted into the gas phase and sucked into the compressor 1, and the outdoor condenser bypass control valve 50 and the indoor condenser selection control valve 52 are closed. In the CLOSE operation, the refrigerant is not introduced into the indoor condenser 21.

In this mode, the outdoor receiver 40 and the indoor receiver 41 function to prevent mixing of the uncondensed gas into the expansion valve 70 mixed in the refrigerant at the outlet of the outdoor condenser 20.

At this time, the indoor air is heat-exchanged with the refrigerant inside the heat exchanger tube of the evaporator 30 to be supplied to the room in a low temperature and high humidity state, which is operated in the maximum cooling capacity of the operating mode of the present invention.

Next, 2) the maximum dehumidification mode is a cycle for dehumidifying the indoor humidity in a cycle for dehumidifying operation at a high or low temperature in the room. In this mode, the indoor condenser selection control valve 51 is open and the indoor unit bypass. The control valve 53 is operated in the form of closed (close), the dehumidification heating operation in the form of the control valve 50 open and the control valve 51 (Close) when the room temperature is low temperature and high humidity. When the room temperature is high temperature and high humidity, the control valve 51 is opened and the control valve 51 is closed.

 First, in the dehumidification heating operation, the refrigerant gas of the high temperature and high pressure at the outlet of the compressor 1 is opened in the open condenser 20 bypass control valve 50 to operate the evaporator in the gas state of the high temperature and high pressure in the indoor condenser 21. 30) Condensation and subcooling with liquid refrigerant after heat exchange with the low temperature air at the outlet, decompression as it passes through the expansion valve 70, and after being heat exchanged with indoor air in the evaporator 30, the liquid phase is converted into gas phase by the compressor (1). Sucked into the outdoor condenser 20, the selection control valve 51 and the indoor condenser 21 bypass control valve 53 is operated in a closed state (CLOSE), the outdoor receiver 40 is not used, The indoor receiver 41 has a function of preventing mixing of the uncondensed gas into the expansion valve 70 mixed in the refrigerant at the outlet of the indoor condenser 20.

At this time, the indoor air is cooled below the dew point temperature in the evaporator 30, cooled and dehumidified by condensation on the surface of the heat exchanger of water vapor in the air, and then reheated in the indoor condenser 21 in a humid state of low temperature.

Since the indoor condenser 21 cools and condenses the high temperature and high pressure gas at the outlet of the compressor 1, the low temperature and humid air at the outlet of the evaporator 30 is heated and discharged into the room by the blower 61. This cycle dehumidifies the indoor air. In the heating operation, for example, if the cooling dehumidification is continuously operated in a low temperature and high humidity condition of an underground structure, the indoor temperature gradually decreases, and thus the condition that the electric heater, etc. should be operated to prevent this is used. Form.

Next, in the dehumidification cooling operation, the refrigerant gas of the high temperature and high pressure of the compressor 1 is opened (OPEN) operation of the outdoor condenser selection control valve 51 to open the liquid in the liquid state after heat exchange with the outdoor air in the gas state in the outdoor condenser 20. The refrigerant condensed, and the refrigerant at the outlet of the outdoor condenser 20 passes through the outdoor receiver 40 to open OPEN of the indoor condenser selection control valve 52, and the indoor condenser 21 is the outdoor condenser 20. The refrigerant at the outlet of the evaporator 30 is supercooled by heat exchange with the low temperature air at the outlet, and the supercooled refrigerant at the outlet of the indoor condenser 21 is decompressed while passing through the expansion valve 70 through the indoor receiver 41 and the evaporator. After the heat exchange with the indoor air at 30, the liquid phase is converted into the gas phase and sucked into the compressor 1, and the outdoor condenser bypass control valve 50 and the indoor condenser 21 bypass control valve 53 are closed (CLOSE). ) And the outdoor receiver ( 40 and the indoor receiver 41 prevent the incorporation of the non-condensing gas into the expansion valve 70 mixed in the refrigerant at the outlet of the indoor condenser 20 and the refrigerant storage function.

At this time, the indoor air is cooled below the dew point temperature in the evaporator 30, cooled and dehumidified by condensation on the surface of the heat exchanger of water vapor in the air, and then reheated in the indoor condenser 21 in a humid state of low temperature.

Since the indoor condenser 21 supercools the refrigerant at the outlet of the indoor condenser 20, the liquid refrigerant is cooled instead of condensing (latently) the high-temperature and high-pressure refrigerant gas at the outlet of the compressor 1 as in the dehumidification heating operation. Because of the sensible heat load type, the heating calorific value of the low temperature and humid air at the outlet of the evaporator 30 is a cycle for simultaneously performing dehumidification and cooling operation of the indoor air of a mode that is not very large.

For example, in the case where the cooling operation and the dehumidification operation should be performed simultaneously under the high temperature and high humidity conditions in summer, more indoor air is increased due to an increase in the cooling capacity of the indoor evaporator 30 due to the liquid refrigerant supercooling of the indoor condenser 21. Water vapor in the air may be removed by cooling the evaporator 30 below the dew point temperature.

Next, 3) constant temperature mode is a combination of 1) cooling mode, 2) maximum dehumidification mode, and hot gas bypass mode, which is operated as a constant temperature and humidity device that maintains a constant temperature and humidity. If the room temperature is high, operate in cooling mode. If the room temperature is low and humidity is high, open the control valves (50, 52) and close the control valves (51, 53) in the maximum dehumidification mode. Dehumidification heating operation, and when the room temperature and humidity conditions are high temperature and high humidity, the dehumidification cooling operation of the control valves 51 and 52 of the maximum dehumidification mode and the control sides 50 and 53 are closed. When the indoor temperature is low and low, the hot gas bypass operation, which is a simple heating operation of the control valves 50 and 53, and the control valves 51 and 52, is closed.

In the above operation mode, since 1) cooling mode and 2) maximum dehumidification mode have been described in the corresponding mode, only the hot gas bypass mode will be described.

The high-pressure and high-pressure refrigerant gas at the outlet of the compressor (1) is opened by the OPEN operation of the bypass control valve (53) of the outdoor condenser (20) and the bypass control valve (53) of the indoor condenser (21). While passing through the air, it is reduced in pressure and enters the compressor 1 by converting from superheated steam state to saturated steam state by heat exchange with indoor air in the evaporator 30, and the indoor air is heated without cooling process. ) Is operated in the closed state.

For example, in the case where the heating operation is to be carried out simply under a low temperature dry air condition in winter, the evaporator 30 is used as a condenser.

As described above, the cooling mode, the maximum dehumidification, and the constant temperature mode are used in each single mode operation or combined operation, and for the constant temperature and humidity of the room, the continuous heating, cooling, and dehumidification must be performed, and the operation must be performed in a combined cycle. The system also needs to be reheated after cooling and dehumidifying in the evaporator 30, so it is operated in the maximum dehumidification mode, and must be operated in a combined cycle for constant temperature and humidity.

2, 3, 4, 5, and 12 are views showing still another embodiment of the present invention, which is a system applying the basic cycle of the present invention of FIG.

First, FIG. 2 is a system in which the control valves 50, 51, 52, and 53 of FIG. 1 are changed to three-way valves 80 and 81. The control valves 50, 51, or control valve of FIG. Only one of 52 and 53 can be changed to a three-way valve, and the driving mode is the same as that of the present invention of FIG.

Next, FIG. 3 is a system in which the control valves 50 and 51 of FIG. 1 are changed to three-way valves 80, and the control valve 52 is omitted. WAY VALVE (80) can be changed to the control valve (50, 51), the operation mode is the bypass control valve by omitting the selection control valve 52 of the indoor condenser 21 in the operation mode of the present invention of FIG. It is the same as the form of controlling 53 independently.

Next, FIG. 4 is a system omitting the control valves 52 and 53 of FIG. 1, and the control valves 50 and 51 can be changed to three-way valves. In the operation mode of the present invention, the selection control valves 52 and 53 of the indoor condenser 21 are omitted.

Next, FIG. 12 is a system in which the control valve 51 of FIG. 4 is omitted, and the driving mode is a mode in which the selection control valves 52 and 53 of the indoor condenser 21 are omitted in the operating mode of the present invention of FIG. Is the same as

Finally, FIG. 5 is a view in which the evaporator 30 of FIG. 1 is divided into an evaporator 31 and an evaporator 32. The indoor condenser 21 is a system located between the evaporators 31 and 32. It can be changed to a system such as 3, 4, the order of introduction of the refrigerant of the evaporator (31, 32) can be first introduced into the evaporator (31) or the evaporator (32) based on the expansion valve 70, the evaporator (31) , 32) and the indoor condenser 21 may be configured in an integrated or independent form.

The driving mode will be described with reference to FIG. 5 because it is the same as the driving mode of the present invention of FIG. 1, but the dehumidification heating operation in the maximum dehumidification mode is different.

The dehumidification heating operation in the maximum dehumidification mode is performed by the high temperature and high pressure refrigerant gas at the outlet of the compressor 1 in the operation of the control valves 50 and 52 open and the control valves 51 and 53 closed. 20) The heat condenser 21 is condensed and subcooled with a refrigerant in a liquid state after heat exchange with the low temperature air at the outlet of the evaporator 32 in a gas of high temperature and high pressure in the indoor condenser 21 by OPEN operation of the bypass control valve 50. After depressurizing while passing through the expansion valve (70), after exchanged with the air of the outlet of the indoor condenser (21) in the evaporator (31), after being exchanged with the indoor air in the evaporator (32), the liquid is converted into a gas phase and sucked into the compressor (1). , The indoor air is cooled to below the dew point temperature in the evaporator 32, cooled and dehumidified by condensation on the surface of the heat exchanger of water vapor in the air, and then reheated in the indoor condenser 21 in a humid state of low temperature, and then evaporator 31. Cooled to below the dew point temperature After cooling and dehumidifying by condensation on the surface of the heat exchanger of water vapor in the air, it is supplied to the room in a low temperature and humid condition.

In the present embodiment, the indoor air at the outlet of the evaporator 32 is a low temperature and high humidity state in the summer high temperature and humid outdoor air condition, and a water film is formed on the surface of the heat exchanger of the evaporator 32 by condensation to exchange heat between the indoor air and the heat exchanger. In order to prevent this, the cooling condensation dehumidification performance is abruptly lowered, so in order to prevent this, the cold dehumidified low temperature and humid air of the evaporator 32 is reheated in the indoor condenser 21, and then the heat exchanger during the cooling dehumidification operation in the evaporator 31. By preventing the formation of a water film on the surface it can prevent the performance degradation.

On the other hand, in the present invention of Figures 1, 2, 3, 4, 5, the receiver 40, 41 may optionally be omitted one or both as needed.

         6 is a diagram Pi showing the cycle of the refrigeration air conditioning system according to the present invention, the conventional refrigeration air conditioning cycle (i1 ', i2', i3) is operated at a high pressure (P2 ') and low pressure (P1'), In the cycles i1, i2, i3 of the invention, in the system operating at high pressure (P2) and low pressure (P1), the discharge temperature is i2 'is higher than i2, so i2' becomes high temperature, and the amount (i2'-i1 ') Since it is larger than this amount (i2-i1), the conventional refrigeration air conditioning system causes damage due to the overload of the compressor (1) with more amount and higher discharge temperature, and the unit cooling capacity (i1-i3) is (i1). greater than '-i3', the air at the outlet of the evaporator 20 is cooled to a low temperature and has a moisture dehumidification capability.

7 and 8 are time-pressure diagram and pressure-power diagram when operated with a cold air dryer (cooling dehumidifier) of a refrigeration air conditioning system according to the present invention. > P2), the cycle of the present invention (ABC) is a high pressure (P1), the power consumption at this time consumes W1 at P1, W2 at P2, so W2> W1, the cycle of the present invention is conventional cold air drying (Cooling dehumidifier) A higher efficiency cycle with lower energy consumption than the system.

1 is a diagram illustrating a system diagram of a refrigeration air conditioning system according to the present invention.

Figure 2 is a schematic diagram of another embodiment of a refrigeration air conditioning system according to the present invention

Figure 3 is a schematic diagram of another embodiment of a refrigeration air conditioning system according to the present invention

Figure 4 is a schematic diagram of another embodiment of a refrigeration air conditioning system according to the present invention

5 is a schematic diagram of another embodiment of a refrigeration air conditioning system according to the present invention;

6 is a view showing a cycle diagram of a refrigeration air conditioning system according to the present invention

7 is a view showing a time-pressure diagram of a refrigeration air conditioning system according to the present invention;

8 is a view showing the pressure-consumption power of the refrigeration air conditioning system according to the present invention

9 is a schematic diagram of an example (1) of a conventional system.

10 is a schematic diagram of an example (2) of a conventional system.

11 is a schematic diagram of an example 3 of a conventional system.

12 is a schematic diagram of another embodiment of a refrigeration air conditioning system according to the present invention;

Claims (8)

A compressor for compressing and discharging the refrigerant gas to a high temperature and high pressure state, a condenser for condensing the refrigerant compressed in the compressor to a liquid phase, and an expansion for expanding a high temperature and high pressure liquid refrigerant condensed in the condenser into a low pressure liquid refrigerant A valve and an evaporator which evaporates the refrigerant gas of low temperature and low pressure to return to the compressor while achieving a refrigeration effect by heat exchange with the object to be cooled using the latent heat of evaporation while evaporating the refrigerant expanded by the expansion valve. In the refrigeration air conditioning system, A heat exchanger unit configured to selectively perform combination operation when necessary in a heat exchanger system including an outdoor condenser, an indoor condenser, an outdoor receiver, and an indoor receiver between the compressor and the expansion valve; The control unit comprises an outdoor condenser bypass control valve, an outdoor condenser selection control valve, an indoor condenser selection control valve, and an indoor condenser bypass control valve for controlling the flow of the refrigerant for selective combination operation of the outdoor condenser and the indoor condenser. Refrigeration and air conditioning system. The heat exchanger of claim 1, wherein the outdoor condenser is heat exchanged with an outdoor heat source (air or water), the indoor condenser is arranged in the order of the evaporator and the indoor condenser in the direction of the flow of indoor air, and the indoor condenser passes through the evaporator. It is a structure that exchanges heat with a low temperature air, the indoor condenser is a form of reheating the cooling air as a refrigerant condenser or a subcooler of the refrigerant according to the operation type, the evaporator and the indoor condenser is characterized in that it is composed of an integral or independent form System. The evaporator of claim 2, wherein the evaporator of the heat exchanger is divided into one or two, in which the evaporator is separated into two, and an indoor condenser is disposed between the evaporators 31 and 32, and the evaporator 31, the indoor condenser and the evaporator 32 ) Is a system characterized in that it is configured in one-piece or independent form of integral or selective combination. The outdoor receiver of claim 1, wherein the outdoor receiver is attached to the rear end of the outdoor condenser, the indoor receiver is attached between the expansion valve and the indoor condenser, and the outdoor receiver and the indoor receiver are optionally omitted. System characterized by consisting of one form. The refrigerant control valve of claim 1, wherein the refrigerant control valve of the control unit has an outdoor condenser selection control valve and a bypass control valve attached to the outdoor condenser to control the introduction of refrigerant into the outdoor condenser, and the indoor condenser is connected to the indoor condenser inlet side. A system comprising an indoor condenser selection control valve and an indoor condenser bypass control valve for the purpose of controlling the introduction of refrigerant into the interior. The system as claimed in claim 5, wherein the control side of the control unit is configured to be selectively manufactured by a 2-way valve or a 3-way valve. The method according to claim 5, wherein one or both of the indoor condenser selection control valve and the indoor condenser bypass control valve for the purpose of controlling the introduction of the refrigerant into the indoor condenser from the indoor condenser inlet side of the control unit are selectively omitted. In the form in which the indoor condenser bypass control valve is omitted, the system is configured to connect the pipe of the outdoor receiver outlet to the indoor condenser. The method according to claim 5, wherein the indoor condenser selection control valve and the indoor condenser bypass control valve of the indoor condenser of the controller are omitted. System characterized in that.

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