KR100675900B1 - Refrigeration and air conditioning system - Google Patents

Abstract

The present invention is a system using a refrigeration air conditioning system, and in more detail, the constant temperature and humidity device system that constantly adjusts the temperature and humidity of the computer room in which the computer or electronic device is installed, and the energy of the cooling dehumidification system for cold air drying such as agricultural and marine products. It is a saving system, which uses the waste heat of the condenser during the refrigeration cycle as heating source for reheating the room load and reheating heat source of dehumidifying air to perform constant temperature and humidity function without additional energy supply. Reheat the air and lower the relative humidity to allow continuous dehumidification.

To this end, the indoor condenser 21, the subcooler 31, and the control valves 70, 71, 72, and 73 are replaced with conventional refrigeration air conditioning compressors (1), condensers (20), expansion valves (4) and evaporators ( It is attached in addition to 30).

This cycle is classified according to the operation type of the control valves 70, 71, 72, and 73 of the indoor condenser 21, the outdoor condenser 20, and the supercooler 31, and heating when the control valves 70, 72 are selected. Mode is operated, and when the control valves 71 and 72 are selected, the operation is performed in the maximum dehumidification and shift mode, and when the control valves 71 and 73 are selected, the operation is performed in the cooling and dehumidification mode.

In the present invention, the indoor condenser 21 is used not only as a condenser but also as a reheater of overcooling and cooling air of a refrigerant, and the compressor is burned out by controlling the heating and cooling operation of the system to which the conventional indoor condenser 21 is applied in multiple stages. There is a feature to prevent.

Description

Refrigeration and air conditioning system

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

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

Figure 3 shows a time-pressure diagram of the refrigeration air conditioning system according to the present invention

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

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

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

7 shows a schematic diagram of an example 3 of a conventional system.

<Description of the code | symbol about the principal part of drawing>

1-compressor 4-expansion valve

20-Outdoor Condenser 21-Indoor Condenser

30-Evaporator 31-Supercooler

70-Outdoor Condenser Bypass Valve 71-Outdoor Condenser Select Valve

72-Indoor Condenser Select Valve 73-Indoor Condenser Bypass Valve

The present invention is a system applying a heat pump cycle in a refrigeration air conditioning system, and in more detail, the cooling and cooling for cold air drying of a constant temperature and humidity device system and agricultural products, such as constant control of temperature and humidity of a computer room equipped with a computer or an electronic device The present invention relates to an energy-saving system such as a dehumidification system, which uses the waste heat of a condenser during a refrigeration cycle as a heat source for heating an indoor load and a reheating heat source for dehumidifying air, and performs a constant temperature and humidity function without supplying additional energy. It is to reheat the air which is cooled and dehumidified below the temperature to lower the relative humidity for continuous dehumidification.

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

<Example 1>

5 is a constant temperature / humidity system composed of a compressor 1, a condenser 20, an expansion valve 4, an evaporator 30, and an electric heating coil 25, which is operated by a general refrigeration cycle during cooling, heating and room temperature. It is a cycle operated by operating the electric heating coil 25 at the time of adjustment.

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. When the condensation pressure rises, the power consumption of the compressor increases.

<Example 2>                         

Figure 6 is a conventional constant temperature and humidity system disclosed in the Republic of Korea Patent Application No. 10-2001-0032629.

6 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 a flash gas may be generated, thereby reducing the cooling capacity of the evaporator 160. The pressure of the compressor increases by increasing the pressure drop when passing through the indoor condenser 170 and the outdoor condenser 110, and the system efficiency is lowered because the indoor condenser 170 is not used during the dehumidification and cooling operation. .                         

<Example 3>

Figure 7 is disclosed in the Republic of Korea Patent Publication No. 202-0024692 in a conventional drying system.

7 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 70, 71. ) The basic cycle, the drying basic cycle is operated by the compressor (1), the indoor condenser (21), the expansion valve (4) and the evaporator (30), the air cooled below the dew point temperature in the evaporator (30) condensation 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 the 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 drying system, it can reheat the air dehumidified below the dew point temperature to lower the relative humidity to perform continuous dehumidification and to cool the cycle for stable operation. And dehumidification mode, maximum dehumidification and variation mode, each mode is controlled in multiple stages for temperature and humidity control, cooling capacity by using as a condenser function of indoor condenser, supercooling of refrigerant and reheater of cooling air And improved 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.

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 composed of an outdoor condenser 20, an indoor condenser 21, and a cooler 31 between the compressor 1 and the expansion valve 4;

The outdoor condenser 20 and the indoor condenser 21 is characterized in that the refrigerant control unit for controlling the flow of the refrigerant into the heat exchanger in the control unit (70, 71, 72, 73) during 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) is a compressor, which sucks refrigerant gas and compresses it at high temperature and high pressure and discharges it, and according to the purpose of use, various forms such as reciprocating type, crank type, swash plate type, wobble plate type, rotary type, and spin roll type 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 heating the refrigerant gas discharged from the compressor (1) It is. Although not shown in detail, 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 and outlet header so that they pass through each other, and between the tubes. Conventional forms with corrugated heat transfer fins stacked 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 condenser 20 and 21 is deprived of heat to the blower air to condense the refrigerant.

On the other hand, the inlet line side of the compressor (1) by evaporating the refrigerant flowing from the expansion valve (4), which will be described later by using the latent heat of evaporation at this time evaporator (30) to heat exchange the object to be cooled and the refrigerant to achieve a freezing effect ) Is connected. The evaporator 30 has a plurality of tubes forming a predetermined flow path by connecting an inlet header and an outlet header, the inlet outlet headers to communicate with each other, and a corgate type heat transfer fin stacked between the tubes. 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 detail, the expansion valve (4) 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, an embodiment of a heat pump according to the present invention will be described with reference to the accompanying drawings.

In FIG. 1, there is an outdoor condenser selection valve 71 on a refrigerant pipe circuit connecting the outlet of the compressor 1 and the outdoor condenser 20, and the refrigerant connecting the outlet side of the outdoor condenser 20 and the indoor condenser 21. There is an indoor condenser select valve 72 on the piping circuit, and an outdoor condenser bypass valve 70 on the bypass refrigerant piping circuit connecting the outlet side of the outdoor condenser 20 at the front of the outdoor condenser select valve 71. There is an indoor condenser bypass valve 73 on the bypass refrigerant piping circuit connecting the outlet side of the indoor condenser 21 at the front of the indoor condenser selection valve 72, and the refrigerant pipe at the outlet of the indoor condenser 21. Is connected to the supercooler (31), the outlet side of the supercooler (31) is connected to the expansion valve (4), the outlet side of the expansion valve (4) is connected to the evaporator (30), and the outlet side of the evaporator (30) is a compressor ( 1) It is a structure that is connected to the inlet side.

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 classified into cooling and dehumidification mode, the maximum dehumidification and transition mode and heating mode.

First, in the cooling and dehumidifying mode, the refrigerant gas of the high temperature and high pressure of the compressor 1 is opened (OPEN) of the outdoor condenser selector valve 71, and the liquid refrigerant after the heat exchange with the outdoor air in the gas state in the outdoor condenser 20 is performed. The refrigerant at the outlet of the outdoor condenser 20 is subcooled with the low temperature refrigerant liquid after heat exchange with the low temperature air at the evaporator outlet in the supercooler 31 by the OPEN operation of the indoor condenser bypass valve 73. After being decompressed while passing through the expansion valve 4 and being exchanged with 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 valve 70 and the indoor condenser selection valve ( 72 is a close (CLOSE) operation of the refrigerant is not drawn into the indoor condenser 21.

At this time, the indoor air is cooled to 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 super cooler 31 in a humid state of low temperature.

Since the cooler 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 through the room 60 to obtain the maximum cooling capacity during this cycle.

Next, the maximum dehumidification and transition mode is a liquid state after heat-exchanging with outdoor air in a gas state in the outdoor condenser 20 by opening the high temperature and high pressure refrigerant gas of the compressor 1 in the open (OPEN) operation of the outdoor condenser selector valve 71. The refrigerant at the outlet of the outdoor condenser 20 is supercooled after exchanging heat with the low temperature air at the outlet of the overcooler 31 in the indoor condenser 21 by the OPEN operation of the indoor condenser selector valve 72. The refrigerant liquid at the outlet of the indoor condenser 21 is further cooled after exchanging heat with the low temperature air at the outlet of the supercooler 31 or the evaporator 30, and is decompressed while passing through the expansion valve 4 and the indoor air at the evaporator 30. After the heat exchange with the liquid is converted into the gas phase is sucked into the compressor (1), the outdoor condenser bypass valve 70 and the indoor condenser bypass valve 73 is operated in a closed state (CLOSE).

At this time, the indoor air is cooled to 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 supercooler 31 and the indoor condenser 21 in a humid state of low temperature. Lose.

Since the indoor condenser 21 has a large heat transfer area, the refrigerant at the outlet of the outdoor condenser 20 is cooled to a low temperature, and the heating capacity of the air is greater than that of the overcooler 31, thereby reheating the low temperature air to an appropriate temperature. The air is discharged to the room through the blower 60 in a state in which water droplets of air in the air are sufficiently removed, and the cycle is operated with maximum dehumidification capacity, and the cooling and dehumidifying mode is changed from heating mode to heating mode or cooling mode to dehumidifying mode. It is also used as an intermediate transition mode in order to prevent the compressor 1 from being burned out by the liquid compression of the refrigerant due to the rapid transition of the high pressure and the refrigerant flow rate during the conversion operation and the excessive superheat.

In the cycle, since the refrigerant liquid at the outlet of the outdoor condenser 20 is cooled to low temperature in the indoor condenser 21 and the supercooler 31, the cooling capacity of the evaporator 4 is increased, thereby cooling the temperature of the air at the outlet of the evaporator 30. And it is operated with high dehumidification ability by keeping it lower than dehumidification mode.

Finally, the heating mode is a high temperature and high pressure refrigerant gas of the compressor (1) by the open (OPEN) operation of the outdoor condenser bypass valve 70 in the gas state in the indoor condenser 21 and the low-temperature air of the evaporator 30 exit After heat exchange, the liquid is condensed into the refrigerant of the ecology, and the refrigerant at the outlet of the indoor condenser 21 is supercooled after exchanging heat with the low temperature air at the outlet of the evaporator 30 in the supercooler 31, and is decompressed while passing through the expansion valve 4. After the heat exchange with the indoor air in the evaporator 30 is converted into a gas phase in the liquid phase is sucked into the compressor (1), the outdoor condenser select valve 71 and the indoor condenser bypass valve 73 is operated in a closed state (CLOSE) .

At this time, the indoor air is cooled to 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 supercooler 31 and the indoor condenser 21 in a humid state of low temperature. Lose.

Since the indoor condenser 21 cools and condenses the high temperature and high pressure gas at the outlet of the compressor 1, the indoor condenser 21 passes the blower 60 in a high temperature dry state by heating the low temperature and humid air at the outlet of the evaporator 30 and the supercooler 21. This cycle is used as a heating operation state of indoor air.

In the cycle, the temperature of the air at the outlet of the cooler 31 due to the condensation of the high-temperature and high-pressure refrigerant gas inside the indoor condenser 21 is heated to a high temperature, so that the state of the air at the outlet is dried at a high temperature (low relative humidity). It is driven.

As described above, the cooling and dehumidification mode, the maximum dehumidification and variation mode, and the heating mode are used in each single mode operation or combined operation, and the operation is performed in a combined cycle because continuous heating, cooling, and dehumidification must be performed for the constant temperature and humidity of the room. In the cold air drying system, reheating is required after cooling and dehumidification in the evaporator 30, but the heating mode is abnormal. However, the heating mode alone operation causes the temperature inside the drying chamber to be excessively increased, resulting in an overload of the compressor 1. It should be operated in the above combined cycle because it may cause damage by the high temperature of agricultural and marine products inside the drying chamber.

And the control valve 70, 71, 72, 73 of this cycle can be changed to a three-way valve (3-way valve).

2 is a diagram Pi illustrating a cycle of the refrigeration air conditioning system according to the present invention, wherein the conventional refrigeration air conditioning cycles i1 ′, i2 ′, i3 operate at 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 ') Is larger than the amount (i2-i1), the conventional refrigeration air conditioning system causes damage due to the overload of the compressor (1) with more work and a higher discharge temperature, unit cooling capacity (i1-i3) is (i1 greater than '-i3', the air at the outlet of the evaporator 1 is cooled to low temperatures and has a high moisture dehumidification capability.

3 and 4 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, the conventional refrigeration air conditioning cycle (AB-C ') is a high pressure (P1- > P2), and the cycle ABC of the present invention is high pressure P1, and the power consumption at this time consumes W1 at P1 and W2 at P2, so W2> W1, so that the cycle of the present invention is conventional cold air drying. (Cooling dehumidifier) A higher efficiency cycle with lower energy consumption than the system.                     

In addition, in the form of the super cooler 31 may be configured in the form of an integral or independent form with the evaporator 30 or the indoor condenser 21.

As will be apparent from the above description, 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. It is used for heating the load and reheating the dehumidifying air to perform constant temperature and humidity function without supplying additional energy.In the drying system, continuous dehumidification is achieved by lowering the relative humidity by reheating the air dehumidified below the dew point temperature. It can be operated in cooling and dehumidification mode, maximum dehumidification and transition mode and heating mode for stable operation of the cycle, and each mode is controlled in multiple stages for temperature and humidity control and condensation of the indoor condenser Function or ash of the refrigerant and cooling and cooling air Improved cooling and dehumidification by use of heat, prevents increase of condensation pressure and liquid compression of refrigerant at compressor inlet during operation, improves performance and prevents damage of compressor, and reduces power consumption of system There is.

Claims (3)

A compressor for compressing and discharging the refrigerant gas at a high temperature and high pressure state, an indoor and an outdoor condenser for condensing the refrigerant compressed in the compressor into a liquid phase, and a liquid refrigerant having a high temperature and high pressure condensed in the condenser as a low pressure liquid refrigerant. An expansion valve for expanding and evaporating the refrigerant expanded by the expansion valve and using the latent heat of evaporation of the refrigerant to evaporate while achieving a freezing effect by heat exchange with the object to be cooled to return the refrigerant gas of low temperature and low pressure to the compressor In the refrigeration air conditioning system comprising an evaporator, In the heat exchanger system consisting of the outdoor condenser 20, the indoor condenser 21 and the supercooler 31 A heat exchanger unit selectively driving the heat exchangers 20, 21, and 31 in combination; The outdoor condenser bypass valve 70, the outdoor condenser select valve 71, the indoor condenser select valve 72, and the indoor condenser bypass valve for controlling the flow of the refrigerant in the outdoor condenser 20 and the indoor condenser 21. Refrigeration and air conditioning system characterized by a control unit consisting of (73). The method of claim 1, wherein the heat exchange unit is a form in which the outdoor condenser 20 heat exchanges with an outdoor heat source (air or water), the indoor condenser 21 is the evaporator 30, the cooler 31 in the direction of the flow of indoor air ) And the indoor condenser 21, the indoor condenser 21 is configured to exchange heat with the low-temperature air passing through the evaporator 30 or the super cooler 31, and the super cooler 31 is the evaporator 30. The heat exchanger is configured to exchange heat with air at an outlet, and is arranged between the indoor condenser 21 and the expansion valve 4, and the indoor condenser 21 is controlled according to the control form of the refrigerant control valves 70, 71, 72, and 73 of the control unit. Refrigerant condenser or supercooling of the refrigerant and the form of reheating the cooling air, the supercooler (31) is characterized in that it is configured integrally or independent of the evaporator (30) or the interior condenser (21). The refrigerant control valve (70, 71, 72, 73) of the control unit has an outdoor condenser select valve (71) on the refrigerant piping circuit connecting the outlet of the compressor (1) and the outdoor condenser (20). On the refrigerant pipe circuit connecting the outlet side of the outdoor condenser 20 and the indoor condenser 21, there is an indoor condenser selection valve 72, and the outlet side of the outdoor condenser 20 at the front end of the outdoor condenser selection valve 71. There is an outdoor condenser bypass valve 70 on the bypass refrigerant piping circuit for connecting the condenser, and the indoor condenser on the bypass refrigerant piping circuit connecting the outlet side of the indoor condenser 21 in front of the indoor condenser selection valve 72. There is a bypass valve 73, and the refrigerant pipe at the outlet of the indoor condenser 21 is connected to the cooler 31. The refrigerant control valves 70, 71, 72, and 73 are optional for cooling, dehumidification, or heating. Control system in the system (70, 71, 72, 73) for the bangbyeon (2-way valve) or a three-way side (3-way valve), Refrigeration and Air Conditioning system, characterized in that use.

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