KR20180019041A - Multi heat pump Refrigeration system - Google Patents

Abstract

The present invention relates to a system using a heat pump system and, specifically, to a thermo-hygrostat system controlling the humidity and the temperature of a computer room in which a computer or an electronic device is installed, so that the humidity and the temperature of the computer are constant and an energy saving type system such as a cooling dehumidification system for drying an agricultural and marine product and the like with cold air. The system using the heat pump system can perform a thermo-hygrostat function without supplying additional energy by being used as a heat resource for heating an indoor thermal load and a heat source for reheating dehumidification air. The system using the heat pump system reheats the air which flows out after being cooled and dehumidified from a dry system at heating calories and a dew point temperature or less. So, the heat pump system lowers relative humidity and performs continuous dehumidification action. To achieve the same, the system applied with the heat pump system comprises a first refrigeration cycle, a second heat pump cycle, and an outdoor unit system. According to the present invention, the second heat pump cycle, which has the form of a heat pump, can selectively perform a heat recovery cycle and operation of the heat pump in accordance with an operation form.

Description

[0001] Multi heat pump refrigeration system [0002]

The present invention is applied to a heat pump system. More specifically, the present invention relates to a heat pump system for controlling the temperature and humidity of a computer room in which a computer or an electronic device is installed and a cooling and dehumidifying system for cold- The system uses the waste heat of the condenser during the heat pump cycle and the refrigeration cycle as the heat source for reheating the indoor load and the dehumidifying air to perform the constant temperature and humidity function without supplying additional energy. So that the dehumidification operation can be performed continuously by lowering the relative humidity by reheating the air that is cooled and dehumidified in the dehumidifier.

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

<Example 1>

 3 is a constant temperature and humidity system composed of a compressor 410, a condenser 420, an expansion valve 470, an evaporator 430 and an electric heating coil 425. In the cooling mode, the refrigerator is operated in a general refrigeration cycle, And the electric heating coil 425 is operated to operate.

However, in the conventional cycle, the energy consumption rate is high by using the electric coil 425 as the heat source of heat, and the refrigeration cycle and the electric heater are simultaneously operated at the room temperature constant temperature control, thereby consuming a lot of electric power, This increase in condensation pressure has a disadvantage in that the power consumption of the compressor increases.

 <Example 2>

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

4 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 sides 190 and 201.

First, the cooling cycle is a general refrigeration cycle operated by the compressor 101, the outdoor condenser 110 and the evaporator 160. The heating cycle includes a compressor 101, an indoor condenser 170, an outdoor condenser 110, (160). The main principle is that the hot gas can be drawn into the indoor condenser (330) at the time of heating and the heating can be performed without a separate heat source.

However, in the conventional cycle, the refrigerant at the outlet of the indoor condenser 170 is supercooled by the outdoor condenser 110 during the winter heating operation, so that the amount of cooling heat in the evaporator 160 is increased, The refrigerant liquid at the outlet of the indoor condenser 170 is heated by heat exchange with the hot air outside from the outdoor condenser 110 during the summer heating and dehumidifying operation so that the flash gas may be generated and the cooling ability of the evaporator 160 may be lowered The power of the compressor increases due to an increase in 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 utilized during the dehumidification and cooling operation.

<Example 3>

        5 is a conventional drying system as disclosed in Korean Patent Publication No. 10-067590, which relates to a heat recovery cycle and efficiency improvement.

5, a compressor 510, an outdoor condenser 520, an indoor condenser 521, an evaporator 531, and control sides 570, 571 and 574 are operated.

The main function of the patent is to save energy by using the indoor condenser 521 as a heat recovery cycle and utilizing the waste heat of the condenser of the refrigeration system without using a heater as an indoor heat source.

However, in the above-mentioned conventional cycle, since the heating load such as the winter system can not be covered, there is a drawback that an additional operation cost of the winter system is caused by using a heater.

The present invention relates to an energy saving system such as a constant temperature and humidity apparatus system and a cooling and dehumidifying system, which is applied to a heat pump system. In a combined form of a heat pump cycle and a refrigeration cycle, waste heat (heat recovery cycle) Is used as a reheating heat source for the heating of the room load and the dehumidifying air, so that it performs the constant temperature and humidity function without supplying any additional energy. In the drying system, the air cooled and dehumidified at the dew point temperature is reheated and the relative humidity Dehumidifying operation can be performed by lowering the temperature of the dehumidifier, and the cycle is characterized by high dehumidification and high efficiency operation by multi-stage cooling dehumidification and heating.

In addition, the heat pump cycle is to provide a system that reduces the operation power by 3 to 4 times as much as that of the electric heater by selectively operating the heat pump operation and the heat recovery operation (heat recovery) in one cycle.

The present invention relates to a combined heat pump type constant temperature and humidity system comprising a first refrigeration cycle 100 which is a conventional constant temperature and humidity system and a second heat pump cycle 200 and an outdoor unit 300, The first condenser 20 and the second condenser 21 improve the heating capacity and the outdoor unit 22 is selectively supplied to the condenser and the condenser. It can be used as an evaporator to control the room temperature and heat pump cycle. It increases the heating capacity by 3 ~ 4 times compared to existing thermo-hygrostat, which greatly reduces the operation cost and shortens the operating time of the thermo-hygrostat with high dehumidification performance. In order to provide a system that reduces the cost of the system.

The present invention relates to an energy saving system such as a constant temperature and humidity system, a cooling and dehumidifying system, and a high dehumidification function. The first refrigeration cycle (100) includes a condenser The second heat pump cycle 200 is used as the waste heat of the condenser and the evaporator of the outdoor unit 300. The second heat pump cycle 200 may be used as an evaporator of the outdoor unit 300, In the multi-stage dehumidification system of the first and second evaporators 30 and 31, the first evaporator 30 performs cooling and dehumidification below the dew point temperature and the second evaporator 31 The high temperature and high humidity air at the outlet of the first evaporator (30) can be cooled and dehumidified below the dew point and continuously operated at a multi-stage high dehumidification performance.

In addition, the heating capacity of the first condenser 20 and the second condenser 21 is improved, and the outdoor unit 22 is selectively used as a condenser and an evaporator, so that the room temperature control function and the heat pump cycle It greatly reduces the operation cost by increasing the heating capacity by 3 ~ 4 times, and reduces the operation time of the thermo-hygrostat with high dehumidification performance, thereby reducing the power required for the system.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a diagram showing a cooling mode diagram of a hybrid constant temperature /
2 is a view showing a heating mode diagram of a hybrid temperature and humidity control system according to the present invention;
3 is a schematic diagram of an example (1) of a conventional system;
4 is a diagram showing a schematic diagram of an example (2) of a conventional system
5 is a schematic diagram of an example (3) of a conventional system;
5 is a schematic diagram of an example (3) of a conventional system;
6 is a schematic diagram of a first embodiment of the present invention
7 is a schematic diagram of a fourth embodiment of the present invention

To achieve the above object, a refrigeration and air conditioning system according to the present invention comprises: a compressor for compressing and discharging refrigerant gas into a high-temperature and high-pressure state; a four-way valve for switching the direction of the refrigerant; An expansion valve for expanding the liquid refrigerant in the high-temperature and high-pressure state condensed in the condenser to low-pressure liquid refrigerant, and a condenser for evaporating the refrigerant expanded in the expansion valve, And an outdoor unit for evaporating the refrigerant gas while exchanging the refrigerant gas to evaporate the refrigerant gas and returning the refrigerant gas in a gaseous phase of low temperature and low pressure to the compressor, and a refrigerant air conditioning system,

A first refrigeration cycle unit including the compressor 10, the condenser 20, the expansion valve 50, and the evaporator 30;

And is composed of the compressor 11, the condenser 21, the expansion valves 51 and 52, the evaporator 31, the four sides 60, the outdoor unit 22, the control sides 70 and the fans 80 and 81, And a heat pump cycle unit constituted by a second heat pump cycle (200) for performing a combined operation and an outdoor unit (300).

The features and advantages of the present invention will become more apparent from the detailed description of preferred embodiments with reference to the accompanying drawings. Prior to this, terms and words used in the present specification and claims should not be construed as limited to ordinary or dictionary meanings, and the inventors should appropriately interpret the concepts of terms in order to describe their invention in the best way. It should be interpreted in accordance with the meaning and concept consistent with the technical idea of the present invention based on the principle that it can be defined.

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

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cycle diagram showing a system diagram of a refrigeration and air conditioning system (a constant temperature, humidity, or dehumidification system, etc.) according to the present invention;

Reference numerals 10 and 11 denote compressors for sucking a refrigerant gas and compressing the refrigerant gas at a high temperature and a high pressure and discharging the refrigerant gas by reciprocating type, crank type, swash plate type, wobble plate type, rotary type, Various types of compressors can be applied.

In the first refrigeration cycle, the discharge line of the compressor 10 is connected to the condenser 20. The condenser 20 condenses the refrigerant gas compressed and discharged in the compressor 10 into a liquid refrigerant of high temperature and high pressure by radiating heat . Although not shown in detail here, the condenser 20 includes an inlet header and an outlet header, a plurality of tubes connecting the inlet / outlet headers to each other to form a predetermined flow passage therethrough, and a plurality of tubes A conventional type having corrugated heat conductive fins may be applied. Accordingly, 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 loses heat to the blowing air to perform the condensing action of the refrigerant.

On the other hand, an evaporator 30 for evaporating the refrigerant flowing from the expansion valve 50 to be described later and performing a heat exchange between the object to be cooled and the refrigerant by using the latent heat of evaporation at the inlet line side of the compressor 10, Respectively. The evaporator 30 includes an inlet header and an outlet header, a plurality of tubes for connecting the inlet / outlet headers to each other to communicate with each other to form a predetermined flow path, and a corrugated heat transfer fin A conventional type having the same shape can be applied. Therefore, the air blown by the cooling fan passes through the heat transfer fins between the tubes. In this process, the refrigerant flowing in the evaporator 30 takes the temperature (heat amount) of the blowing air and evaporates the refrigerant.

And an expansion valve 50 for supplying the liquid refrigerant at the inlet end of the evaporator 30 to the evaporator 30 so as to expand the liquid refrigerant in a high-temperature and high-pressure state to a low-pressure refrigerant by an alternating action, Respectively. Although not specifically shown here, the expansion valve 50 is an internal pressure type that adjusts the trajectory of the high-pressure refrigerant passage through the pressure transmission rod on the expansion side of the diaphragm according to the temperature inside the pressure reducing chamber, and a capillary tube Pressure type refrigerant flow path by controlling the expansion or contraction of the high-pressure refrigerant flow path through the diaphragm through the diaphragm, and a variety of types can be used.

In the second heat pump cycle, the discharge line of the compressor 11 is at the four sides 60, the outlet side of the four sides 60 is connected to the outdoor unit 22, and the outdoor unit 22 is connected to the condenser and the evaporator The condenser 21, the outdoor unit 22, the expansion valves 51 and 52, and the compressor (not shown) in such a manner that the second condenser 21 and the control side 70 are additionally requested to be selectively operated. Is operated in the same manner as the principle of the first refrigeration cycle.

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

1, the first refrigeration cycle 100 includes an outlet of the compressor 10 and an outlet of the condenser 20. The first refrigeration cycle 100 includes a first refrigeration cycle 100, a second heat pump cycle 200, The outlet of the condenser 20 is connected to the expansion side 50 and the outlet of the expansion side 50 is connected to the evaporator 30 and the outlet of the evaporator 30 is connected to the compressor 1, As shown in FIG.

The outlet of the compressor 11 and the inlet side of the four sides 60-a of the second heat pump cycle 200 and the outdoor unit system 300 are connected by a refrigerant pipe and the connection of the four sides 60- 22 are connected by a refrigerant pipe and connected to the outdoor unit 22 and the third expansion unit 52 by a refrigerant pipe and the third expansion unit 52 is connected to the second condenser 21 and the second expansion unit 51 The second expansion valve 51 and the second evaporator 31 are connected to the refrigerant pipe and the second evaporator 31 and the four sides 60-c are connected to the refrigerant pipe, The control side 70 is attached on the connecting refrigerant pipe of the second condenser 21 by branching from the outlet of the compressor 11 on the connecting refrigerant pipe of the four sides 60- And the suction side of the compressor 11 are connected to each other, and the outlet side of the four sides 60-d is blocked.

The first refrigeration cycle 100 is operated in the same manner as the conventional thermo-hygrostat with the reference cycle of the operation stop (ON-OFF) of the compressor 10 and the proportional control operation mode.

The second heat pump cycle 200, and the outdoor unit system 300, it can be classified into a cooling mode and a heating mode.

First, 1) the cooling mode is a mode of operation in which the indoor temperature is equal to or higher than a set value, and the refrigerant gas of the high temperature and high pressure of the compressor 11 is heat exchanged with the outdoor air in the outdoor unit 22 through the four sides 60- The liquid refrigerant in the high pressure is decompressed while passing through the expansion valve 51 and is converted into a gas phase from the liquid after heat exchange with the room air in the evaporator 31. [ So that the refrigerant is not drawn into the indoor condenser 21 due to the CLOSE operation of the control side 70. The outdoor unit 22 is connected to the condenser 11 via the four sides 60- It is a type of cooling operation of existing refrigeration cycle in the form of operation.

At this time, if the indoor temperature drops below the set value, the refrigerant is not drawn into the outdoor unit 22 due to the CLOSE operation of the expansion valve 52, but the second condenser 21 The refrigerant is condensed into refrigerant in a liquid state after heat exchange with air in the room and is drawn into the expansion valve 51.

2, the heating mode is an operation mode when a large amount of heating heat is required at room temperature below the set value in FIG. 2, and the high temperature and high pressure refrigerant gas of the compressor 11 is opened by OPEN operation of the control side 70, Exchanged with the indoor air in the condenser 21 and is condensed in the liquid state refrigerant. The refrigerant is reduced in pressure while passing through the expansion valve 51, exchanged with the outdoor air in the outdoor unit 22, The outdoor unit 22 is operated as an evaporator and the refrigerant is drawn into the evaporator 31 by the CLOSE operation of the expansion valve 51. [ And is operated at a heating capacity two to four times higher than the heat recovery cycle of the conventional refrigeration cycle.

At this time, the defrosting operation of the heat pump cycle is a mode in which the outdoor unit 22 is operated in the cooling mode by the switching operation of the four sides, and the outdoor unit 22 is operated by the condenser.

As described above, the cooling mode and the heating mode are used for each single mode operation or combined operation, and continuous heating, cooling, and dehumidification must be performed for constant temperature and humidity in the room. Since it is necessary to reheat after dehumidification in the evaporators (30, 31), it is operated in the cooling mode and the heating mode, and it is operated in a combined cycle for the constant temperature and humidity.

 As shown in FIG. 6, the first and second evaporators 30 and 31 of the first refrigeration cycle and the second heat pump cycle have a parallel structure in the air flow direction. The condensers 20 and 21 are also configured in a parallel structure.

 2) of the present invention comprises the first and second evaporators 30 and 31 in the first embodiment and the second and third condensers 20 and 31 in the air flow direction , 21) have a serial structure (see FIG. 1) and are configured by changing the arrangement and arrangement order.

The first and second evaporators 30 and 31 in the first embodiment of the present invention have a series structure (see FIG. 1) in the air flow direction and the first and second condensers 20 and 21 ) Is a parallel structure (see FIG. 6) in which the arrangement and arrangement order are changed.

7, the heat pump cycle 200 and the outdoor unit system 300 are connected to the outlet of the compressor 11 and the inlet sides of the four sides 60-a of the heat pump cycle 200 and the refrigerant piping, respectively, The connection port of the four sides 60-b and the outdoor unit 22 are connected by a refrigerant pipe and connected to the outdoor unit 22 and the expansion unit 52 by a refrigerant pipe. The expansion unit 52 is connected to the second condenser 21, And the expansion valve 51 and the evaporator 31 are connected to the refrigerant pipe and the evaporator 31 and the four sides 60-d are connected to the refrigerant pipe, The control side 70 is attached on the connecting refrigerant pipe of the condenser 21 by branching on the connecting refrigerant pipe of the outlet of the compressor 11 and the connecting side refrigerant pipe of the four sides 60- And the suction side of the compressor 11 is connected.

   In another embodiment 5 of the present invention, the first refrigeration cycle may be configured as a first heat pump cycle and a second heat pump cycle in the same manner as the second heat pump cycle. The first heat pump cycle, and the second refrigeration cycle, and the arrangement and arrangement order of the evaporators 30 and 31 and the condensers 20 and 21 may be changed.

10, 11: compressor 20, 21: evaporator
22: outdoor unit 30, 31: condenser
60: Four sides 70: Control side
100: first refrigeration cycle 200: second heat pump cycle
300: outdoor system

Claims (6)

A heat pump cycle consisting of a refrigeration cycle unit including a compressor, a condenser, an expansion valve and an evaporator, a heat pump cycle consisting of a compressor, a condenser, an expansion valve, an evaporator, a four-way valve, an outdoor unit, And a cycle section.
The system according to claim 1, wherein the refrigeration cycle is a refrigeration cycle comprising a compressor, a condenser, an expansion valve, and an evaporator, wherein refrigeration components such as a receiver and an outdoor unit are added as needed.      The heat pump system according to claim 1, wherein, in the heat pump cycle and the outdoor unit system, the heat exchanger of the outdoor unit is selectively operated to the evaporator and the condenser in the form of the compressor, the four sides, the control side, the outdoor unit, the condenser, Wherein a control side is attached to a refrigerant pipe branched from a refrigerant pipe between an outlet and a four-way opening and connected to the second condenser, and is selectively operated according to the operation mode.     The compressor according to claim 3, wherein one of the mouths and the outlets of the four sides is in a closed form and the low pressure side of the four sides is connected to the suction side of the compressor in such a manner that the refrigerant piping of the outlet of the second evaporator is connected, And the second evaporator is formed to be independently connected to the inlet and outlet of the four sides.     The system of claim 1, characterized in that, in the first and second system combinations of the combined system, the first system comprises a refrigeration system or a heat pump system and the second system comprises a refrigeration system or a heat pump system . The composite system according to claim 1, wherein the first and second evaporators are configured in parallel or series in the air flow direction, and the first and second condensers are selectively combined in a series or parallel structure.

Images