KR100755008B1 - Cooling apparatus equipped with branch pipe for early collection of vaporized refrigerant - Google Patents

Abstract

A cooling apparatus equipped with branch pipes for early recovering vaporized refrigerant is provided to improve heat exchange capacity, and to reduce size of the evaporator by early recovering vapor refrigerant vaporized in an evaporator. A cooling apparatus equipped with branch pipes for early recovering vaporized refrigerant comprises a compressor, a condenser(120), an expansion valve(130), an evaporator(140), a first branch pipe(L20), a second branch pipe(L30) and a heat exchanger(150). The condenser is connected to the compressor and liquidizes the refrigerant sent from the compressor. The expansion valve is connected to the condenser, and decreases pressure of the refrigerant sent from the condenser. The evaporator is connected to the compressor and the expansion valve, and sends the refrigerant to the compressor. The first branch pipe early recovers the refrigerant vaporized in the evaporator and sends the refrigerant between the evaporator and the compressor. The second branch pipe branches off a part of the refrigerant flowed from the compressor so as to make a detour to an inflow side of the condenser. The heat exchanger makes the refrigerant flowing in the first branch pipe and the second branch pipe heat-exchange.

Description

COOLING APPARATUS EQUIPPED WITH BRANCH PIPE FOR EARLY COLLECTION OF VAPORIZED REFRIGERANT}

1 is a block diagram showing a schematic configuration of a cooling apparatus according to the prior art.

Figure 2 is a reference diagram for explaining the flow pattern inside the evaporator in the conventional cooling apparatus.

Figure 3 is an overall configuration for explaining the cooling device of the present invention.

Figure 4 is a partial perspective view for explaining the steam refrigerant early recovery branch pipe according to the present invention.

Figure 5 is a cross-sectional view for explaining the action of the steam refrigerant early recovery branch pipe according to the present invention.

6 is a cross-sectional view taken along line II ′ of FIG. 4;

Figure 7 is a reference diagram for explaining the operation and action of the cooling apparatus according to the present invention.

* Description of the symbols for the main parts of the drawings *

110: compressor 120: condenser

130: expansion valve 140: evaporator

150: heat exchanger 160: temperature measuring sensor

L10: Circulation line L20: First branch pipe for early recovery of steam refrigerant

L30, L40: 2nd, 3 branch engines V10, V20: Solenoid valve

The present invention relates to a cooling device such as an air conditioner, a refrigerator, an air conditioner, and the like, by early recovery of vapor refrigerant evaporated from the evaporator to improve the heat exchange capacity of the evaporator and to optimize the temperature of the refrigerant flowing into the compressor close to the design value. It can be adjusted to the state of the present invention relates to a cooling device having a branch pipe for early recovery of steam refrigerant can be expected to improve the overall cooling performance.

In general, the cooling device refers to a refrigerant compressed by a compressor in a condenser and then evaporated again in an evaporator through an expansion valve. Refers to a device for cooling.

In such a cooling device, the cooling performance depends on how effectively heat can be removed from the condenser and how smoothly heat exchange occurs in the evaporator.

 Thus, Figure 1 is a block diagram showing a schematic configuration of a conventional cooling apparatus, Figure 2 is a reference diagram for explaining the flow pattern inside the evaporator in the conventional cooling apparatus.

As shown, a conventional cooling apparatus includes a compressor 11 for compressing a refrigerant at high temperature and high pressure, a condenser 12 for liquefying the refrigerant with a high pressure liquid refrigerant, and an expansion valve for pressure drop of the liquid refrigerant with a low pressure liquid refrigerant ( 13), an evaporator 14 for evaporating the pressure-reduced low pressure liquid refrigerant.

According to such a configuration, the compressor 11, the condenser 12, the expansion valve 13, and the evaporator 14 repeat the compression-condensation-expansion-evaporation process of the refrigerant, and in this case, the evaporator 14 When the refrigerant evaporates, it absorbs heat of vaporization from the surroundings, thereby cooling the surroundings.

In the conventional cooling apparatus, as shown in FIG. 2, the liquid refrigerant FL and the steam refrigerant FG are present together during the evaporation of the liquid refrigerant FL inside the refrigerant pipe 41 of the evaporator 14. This leads to a transitional state. In such a state in the refrigerant pipe 41, there is a problem in that the vaporization of the liquid refrigerant FL is not performed smoothly because the ratio (dryness) of the vapor refrigerant FG to the liquid refrigerant FL is very high. Therefore, the heat exchange capacity of the evaporator 14 which performs heat exchange mainly depending on the phase change of the refrigerant was inevitably deteriorated.

Accordingly, various methods have been proposed to improve the heat exchange ability of the evaporator 14 as described above. For example, in order to reduce air-side heat resistance, the cooling fins 43 may be provided with high efficiency fins such as super slit fins to increase air-side convective heat transfer coefficients, or micro fins may be introduced into the refrigerant tube 41 of the evaporator 14. By increasing the turbulence intensity and flow velocity of the refrigerant by processing or using microtubes, the convective heat transfer coefficient of the refrigerant was increased.

However, as described above, the method of providing the cooling fins 43 as the super slit fins takes a lot of time and cost, and thus is difficult to develop in the case of a company that lacks technology and financial power, and the effect does not meet the expectations relatively. It was.

In addition, the method of applying the micro fin or the micro tube in the refrigerant tube 41 of the evaporator 14 has a problem that it is inevitable to introduce a new manufacturing equipment.

On the other hand, in the conventional cooling device, due to various environmental effects, the temperature of the refrigerant flowing into the compressor 11 drops considerably, but there is no situation in which a device capable of adjusting the design value is not provided at all. As a result, the compressor 11 does not exhibit its original performance, resulting in a decrease in the overall cooling performance.

Therefore, the present invention has been proposed to solve the conventional problems as described above, and an object of the present invention is to recover the steam refrigerant evaporated from the evaporator early on the way to improve the heat exchange capacity of the evaporator to improve the heat exchange capacity of the evaporator It is to provide a cooling device having an engine.

In order to achieve the above object, a cooling device having a branch pipe for early recovery of steam refrigerant according to the technical idea of the present invention includes: a compressor for compressing and releasing a refrigerant; and liquefied a refrigerant sent from the compressor connected to the compressor. An expansion valve connected to the condenser to pressure-reduce the refrigerant sent from the condenser; an evaporator connected to the expansion valve and the compressor to evaporate the pressure-reduced refrigerant from the expansion valve and to discharge the refrigerant to the compressor; It is characterized in that it comprises a first branch pipe branched from the evaporator, and the vapor refrigerant evaporated in the evaporator prematurely recovered and sent out between the evaporator and the compressor.

Here, the first branch pipe may include a plurality of branch pipes branched from the refrigerant pipes in the middle of the evaporator, and a main pipe that joins the recovered steam refrigerant connected to the branch pipes and discharges them between the evaporator and the compressor. have.

In addition, the branch pipe may be installed at a position immediately after branching from the refrigerant pipe of the evaporator to prevent the refrigerant in the droplet state from flowing.

The first branch pipe and the second branch pipe may include a second branch pipe which diverges some of the refrigerant from the compressor and bypasses the inflow side of the condenser, and the first branch pipe and the second branch pipe together. It may be characterized by further comprising a heat exchanger for heat exchange the flowing refrigerant to each other.

In addition, the second branch pipe may be characterized in that the solenoid valve for adjusting the flow rate of the refrigerant is installed.

In addition, the refrigerant inlet side of the compressor may be characterized by further comprising a temperature measuring sensor for measuring the temperature of the refrigerant flowing into the compressor.

The apparatus may further include a third branch pipe branching from the second branch pipe and returning a part of the refrigerant flowing through the second branch pipe between the evaporator and the compressor.

In addition, the third branch pipe may be characterized in that the solenoid valve for adjusting the flow rate of the refrigerant is installed.

In addition, the refrigerant inlet side of the compressor may be characterized by further comprising a temperature measuring sensor for measuring the temperature of the refrigerant flowing into the compressor.

Hereinafter, embodiments of the present invention as described above will be described in detail with reference to the accompanying drawings.

EXAMPLE

The cooling apparatus of the present invention is configured to allow early recovery of vapor refrigerant evaporated from the evaporator to the outside of the evaporator. Thus, the cooling apparatus of the present invention can drastically improve the heat exchange capacity of the evaporator by dropping the dryness in the evaporator to more actively evaporate the refrigerant and increase the thermal conductivity of the refrigerant.

In addition, the cooling apparatus of the present invention is configured to adjust the temperature (superheat degree) of the refrigerant flowing into the compressor according to a design value by using some of the high temperature refrigerant from the compressor. As a result, the cooling device of the present invention allows the compressor to exhibit the best performance, thereby improving the performance of the entire cooling device.

Hereinafter, the structure of the cooling device provided with the branch pipe for steam refrigerant early recovery according to the present invention. However, the cooling device refers to all products using a refrigerant such as an air conditioner, a refrigerator, and an air conditioner.

Figure 3 is an overall configuration for explaining the cooling apparatus of the present invention, Figure 4 is a partial perspective view for explaining the steam refrigerant early recovery branch according to the present invention, Figure 5 is a refrigerant for early recovery of steam refrigerant according to the present invention Reference cross-sectional view for explaining the operation of the organ.

As shown, the cooling apparatus of the present invention has a first branch pipe (L20) branched from the evaporator 140 to recover the vapor refrigerant evaporated first in the evaporator 140 on the way, and then the evaporator 140 and It was possible to export between the compressor (110). As described above, the present invention is constructed by recovering the steam refrigerant evaporated from the evaporator 140 at an early stage. In the following, the configuration of the present invention will be described in detail based on the technical content of early recovery and export of the vapor refrigerant of the evaporator 140 as described above.

Looking at the cooling device of the present invention as a whole, the compressor 110, the condenser 120, the expansion valve 130 and the evaporator 140 connected to the refrigerant circulation line (L10) is basically provided as in the other cooling device. However, as described above, a second branch pipe L30, a third branch pipe L40, and a heat exchanger 150 are further provided, including the first branch pipe L20 for early recovery of the steam refrigerant. Various valves V10 and V20 are provided together. Hereinafter, each component will be described in detail with respect to the first branch engine L20.

The compressor 110 serves to circulate the refrigerant by compressing the refrigerant in a high temperature, high pressure steam state. The compressor 110 is able to fully exhibit its original function because it receives the refrigerant adjusted to the optimum temperature according to the design value with the help of each branch pipe (L20, L30, L40) and the heat exchanger 150. This can improve the performance of the entire chiller. This will be described later in detail.

The condenser 120 is connected to the compressor 110 and cools the refrigerant in a vapor state sent from the compressor 110 while condensing it into a liquid state at room temperature and high pressure.

The expansion valve 130 is connected to the condenser 120 serves to lower the high temperature and high pressure refrigerant sent to the evaporator 140 to make a low temperature low pressure refrigerant. The expansion valve 130 is installed in the middle of the circulation line (L10) connecting the condenser 120 and the evaporator 140.

The evaporator 140 serves to evaporate the liquid refrigerant of the low pressure lowered in the expansion valve 130. While evaporation of the refrigerant occurs in the evaporator 140, the heat is exchanged with the surrounding air through the cooling fins 143 to absorb the vaporization heat to cool the surroundings. The evaporator 140 according to the present invention discharges the vapor refrigerant evaporated therein by the first branch pipe L20 to the outside. Accordingly, as the dryness decreases in the evaporator 140, the evaporation of the liquid refrigerant is very active, and the thermal conductivity is increased, thereby greatly improving the heat exchange capacity. As a result, the surroundings of the evaporator 140 may be cooled more quickly. As described above, in the cooling apparatus of the present invention, since the performance of the evaporator 140 can be expected to be dramatically improved, only a small sized evaporator 140 can exhibit excellent cooling performance.

Here, the compressor 110, the condenser 120, the expansion valve 130 and the evaporator 140 described above need only be utilized by applying those that are commonly used.

On the other hand, the first branch pipe (L20) serves to recover the steam refrigerant evaporated first in the evaporator 140 on the way as described above, and to send it out between the evaporator 140 and the compressor 110. To this end, referring to FIGS. 3 and 4, the first branch pipe L20 includes a plurality of branch pipes L21 branched from refrigerant pipes 141 belonging to an intermediate portion of the evaporator 140, and one piece of the plurality of branch pipes L20. It is connected to the branch pipe (L21) of the opposite side is composed of the main pipe (L23) connected to the circulation line (L10) between the evaporator 140 and the compressor (110). As a result, the branch pipe L21 of the first branch pipe L20 recovers a part of the vapor refrigerant from the refrigerant pipes 141 at the middle portion of the evaporator 140, and the main tube L23 of the first branch pipe L20 is The steam refrigerant FG recovered from the refrigerant pipes 141 may be combined and discharged between the evaporator 140 and the compressor 110.

As such, when the first branch pipe L20 is provided, the vapor refrigerant FG generated in the evaporator 140 is recovered early, so that the dryness in the evaporator 140 is lowered, as shown in FIG. 5. Evaporation is very active. When the phase change of the refrigerant is actively made in the evaporator 140 as described above, the thermal conductivity of the evaporator 140 is increased as a whole and the heat exchange ability is dramatically improved. Therefore, the surroundings can be cooled more quickly. As such, the cooling apparatus of the present invention may be expected to have a significant improvement in heat exchange capacity of the evaporator 140 by including the first branch pipe L20 for early recovery of the refrigerant. Accordingly, even a small sized evaporator 140 can exhibit excellent cooling performance.

The second branch pipe (L30) serves to divert some of the refrigerant from the compressor (110) to pass through the heat exchanger (150) and then bypass the inlet side of the condenser (120). To this end, the second branch pipe (L30) is branched in the circulation line (L10) connecting the compressor 110 and the condenser 120, but branched near the compressor 110, the opposite side of the compressor 110 and the condenser It is connected back to the circulation line (L10) connecting the 120, but is connected to the vicinity of the compressor (110). The second branch pipe L30 passes through the heat exchanger 150 together with the first branch pipe L20.

Due to the configuration of the second branch pipe L30, the high temperature refrigerant from the compressor 110 branches and flows to exchange heat with the refrigerant flowing through the first branch pipe L20 in the heat exchanger 150. Thus, when the liquid refrigerant flows into the first branch pipe L20, all of the heat is evaporated. In addition, as the temperature of the refrigerant flowing through the first branch pipe L20 increases, the temperature of the refrigerant flowing into the compressor 110 may be increased to easily match the design value. For reference, the temperature of the refrigerant flowing into the compressor 110 is generally considered to be 3 ° C. to 5 ° C., which is also considered in the present invention. However, even if the design value of the refrigerant has a higher temperature, it is only necessary to increase the temperature of the refrigerant flowing through the first branch pipe L20 by increasing the amount of the refrigerant branched through the second branch pipe L30. Thus, the solenoid valve (V10) is installed to adjust the flow rate of the second branch pipe (L30).

The solenoid valve V10 installed in the second branch pipe L30 is controlled through a controller (not shown) and based on the temperature measured by the temperature measuring sensor 160 installed at the inlet side of the compressor 110 by the controller. The degree of opening and closing is controlled.

The third branch engine L40 branches off from the second branch engine L30 and serves to return some of the refrigerant from the compressor 110 between the evaporator 140 and the compressor 110. To this end, the third branch pipe L40 is branched from the second branch pipe L30 and the opposite side thereof is connected to a circulation line L10 connecting the evaporator 140 and the compressor 110. Unlike the first branch pipe L20 and the second branch pipe L30, the third branch pipe L40 directly supplies a high temperature refrigerant to the inlet side of the compressor 110 without passing through the heat exchanger 150. There is a purpose.

According to such a configuration, the third branch pipe L40 returns the high-temperature refrigerant from the compressor 110 directly between the evaporator 140 and the compressor 110 without passing through the heat exchanger 150 and flows into the compressor 110. It serves to quickly raise the temperature of the refrigerant.

In the case of the third branch pipe L40, like the second branch pipe L30, a solenoid valve V20 for adjusting the flow rate of the refrigerant is provided. The solenoid valve V20 is controlled through the controller like the solenoid valve V10 installed in the second branch pipe L30 and measured by the temperature measuring sensor 160 installed at the inlet side of the compressor 110 by the controller. The degree of opening and closing is adjusted based on one temperature.

The heat exchanger 150 passes through the first branch pipe L20 and the second branch pipe L30 together to exchange heat between the refrigerant flowing therein. Then, the refrigerant flowing through the first branch pipe L20 receives heat from the high temperature refrigerant flowing through the second branch pipe L30 and joins the refrigerant flowing from the evaporator 140 to the compressor 110 while the temperature is high. Done. The heat exchanger 150 may be any suitable one, such as a plate heat exchanger. Particularly, in the case of the plate heat exchanger, a plurality of thin metal plates on which the flow paths of the refrigerant of the first branch pipe L20 and the refrigerant of the second branch pipe L30 flow are stacked, so that a high temperature coolant and a low temperature coolant flow along the flow paths. Heat exchanges with each other while flowing. The plate heat exchanger is for heat-exchanging two or more kinds of fluids and corresponds to a known technology in which various excellent products such as a brazing type have already been developed in other fields. Therefore, detailed description of the configuration will be omitted.

The temperature measuring sensor 160 is installed in the circulation line (L10) connecting the evaporator 140 and the compressor 110. However, the first branch pipe L20 and the third branch pipe L40 are installed at a point after the confluence of the refrigerant. As a result, the temperature of the refrigerant finally flowing into the compressor 110 may be measured. The temperature measuring sensor 160 provides the measured value to the controller, thereby contributing the controller to control the solenoid valves V10 and V20 respectively installed in the second branch pipe L30 and the third branch pipe L40. .

On the other hand, the first branch pipe (L20) is provided with a wire mesh (wire mesh) for the purpose of blocking the refrigerant in the liquid droplet state that may be introduced. The wire mesh will be described below.

6 is a cross-sectional view taken along line II ′ of FIG. 4.

As shown, the present invention is provided with a wire mesh 170 for the purpose of blocking the refrigerant in the liquid droplet state that can be introduced through the first branch pipe (L20). The wire mesh 170 is installed in the branch pipe L21 of the first branch pipe L20 and is installed at a position immediately after branching from the refrigerant pipe 141 of the evaporator 140.

Referring to FIG. 7 and other drawings attached to the operation and action of the cooling device having a branch for the early recovery of steam refrigerant according to the present invention configured as described above are as follows. 7 is a reference view for explaining the operation and operation of the cooling apparatus according to the present invention.

First, when power is applied to the cooling apparatus of the present invention, the refrigerant in the compressor 110 is compressed to a high temperature and high pressure vapor state and starts to circulate along the circulation line L10. At this time, the refrigerant passes through the condenser 120, the expansion valve 130 and the evaporator 140 in sequence (see the flow of refrigerant 11-12-13-14-15).

Here, the refrigerant passing through the condenser 120 is condensed in a liquid state in a high temperature and high pressure steam state, expands through the expansion valve 130 and becomes a low temperature low pressure state. At this time, the temperature is drastically dropped to below zero as the vapor and liquid are mixed or changed into a vapor state.

Thereafter, the refrigerant exiting the expansion valve 130 absorbs the heat of the surroundings while passing through the evaporator 140 and becomes a state of low temperature at room temperature, and enters the compressor 110 in a state where liquid and vapor are mixed.

At this time, in the evaporator 140, the vapor refrigerant (FG) already evaporated by the first branch pipe (L20) connected to the refrigerant pipe 141 of the middle portion is recovered early, and then the evaporator 140 and the compressor 110 ) Is sent to circulation line L10 (see refrigerant flow 21-22-23).

As such, when the vapor refrigerant (FG) in the evaporator 140 is discharged at an early stage, the evaporation of the liquid refrigerant proceeds more actively as the dryness is lowered in the evaporator 140. As such, when the evaporation of the liquid refrigerant occurs actively, the heat of vaporization can be further absorbed from the surroundings, and the thermal conductivity is increased, thereby greatly improving the heat exchange capacity of the evaporator 140. This allows the surroundings to be cooled more quickly even with the same size evaporator 140 only.

On the other hand, some of the high-temperature refrigerant from the compressor 110 flows bypass the heat exchanger 150 through the second branch pipe (L30) (see the flow of refrigerant 31-32). Thus, the high temperature refrigerant flowing through the second branch pipe L30 and the lower temperature refrigerant flowing through the first branch pipe L20 exchange heat with each other in the heat exchanger 150. Then, the liquid refrigerant, which may have flowed into the first branch pipe L20, is evaporated under heat, while the refrigerant flowing through the first branch pipe L20 is at a higher temperature, thereby circulating the circulation line L10. Accordingly, the refrigerant flows into the compressor 110. As a result, the temperature of the refrigerant flowing into the compressor 110 is increased to an appropriate level to reach a design value.

As described above, in order to precisely adjust the temperature of the refrigerant flowing into the compressor 110 to a design value, a controller (not shown) grasps the temperature of the refrigerant measured through the temperature measuring sensor 160. Then, according to the adjustment of the opening and closing degree of the solenoid valve (V10) installed in the second branch pipe (L30) to adjust the flow rate of the high temperature refrigerant. Accordingly, as the amount of the refrigerant flowing through the second branch pipe L30 is large and small, the temperature of the refrigerant flowing through the first branch pipe L20 becomes higher or lower so that the temperature of the refrigerant flowing into the compressor 110 is optimal. The value can be adjusted.

On the other hand, when the measured value measured by the temperature measuring sensor 160 does not significantly reach the design value, the controller opens the solenoid valve V20 installed in the third branch engine L40. Then, a part of the high temperature refrigerant from the compressor 110 branches in the second branch pipe L30 to directly join the refrigerant flowing into the compressor 110 (see the flow of the refrigerant 41-42). Then, the temperature of the refrigerant flowing into the compressor 110 very quickly reaches a design value.

As described above, the cooling device according to the present invention improves the performance of the evaporator 140 and can adjust the temperature of the refrigerant flowing into the compressor 110 to an optimum state close to a design value, thereby dramatically reducing the performance of the entire cooling device. It can be improved.

Although the preferred embodiment of the present invention has been described above, the present invention may use various changes, modifications, and equivalents. It is clear that the present invention can be applied in the same manner by appropriately modifying the above embodiments. Accordingly, the above description does not limit the scope of the invention as defined by the limitations of the following claims.

As described above, the cooling device provided with the steam refrigerant early recovery branch pipe according to the present invention allows the liquid refrigerant to be more actively evaporated by the method of early recovery of the vapor refrigerant evaporated from the evaporator to improve the heat exchange capacity of the evaporator. Can be improved.

In addition, the present invention can reduce the evaporator to a smaller size or exhibit a higher cooling performance at the same size in accordance with the improvement of the heat exchange capacity of the evaporator as described above.

In addition, the present invention is able to adjust the temperature of the refrigerant flowing into the compressor to the optimum state by using some of the high temperature refrigerant from the compressor, the compressor can fully exhibit the original performance. As a result, the overall cooling performance is improved.

Claims (11)

Compressor for compressing the refrigerant out; A condenser connected to the compressor to liquefy the refrigerant sent from the compressor; An expansion valve connected to the condenser to reduce a pressure of the refrigerant sent from the condenser; An evaporator connected to the expansion valve and the compressor to evaporate the refrigerant depressurized in the expansion valve and to discharge the refrigerant to the compressor; A first branch pipe branched from the evaporator, the first branch pipe collecting the vapor refrigerant evaporated in the evaporator early and being discharged between the evaporator and the compressor; A second branch pipe which diverges a portion of the refrigerant from the compressor and bypasses the inlet side of the condenser; And a heat exchanger configured to exchange heat between the refrigerant flowing in the first branch pipe and the second branch pipe by passing through the first branch pipe and the second branch pipe together. The method of claim 1, The first branch pipe is composed of a plurality of branch pipes branched from the refrigerant pipes in the middle of the evaporator, and the steam refrigerant preliminary circuit, characterized in that the main pipe for joining the recovered steam refrigerant connected to the branch pipes and sent between the evaporator and the compressor Chiller with receiving branch pipe. The method of claim 2, The branch pipe is provided with a wire mesh at a position immediately after branching from the refrigerant pipe of the evaporator to prevent the refrigerant in the droplet state flowing in the cooling device having a branch pipe for early recovery of the refrigerant refrigerant. delete The method of claim 1, And a solenoid valve for controlling a flow rate of the refrigerant is installed in the second branch pipe. The method of claim 1, The refrigerant inlet of the compressor further comprises a temperature measuring sensor for measuring the temperature of the refrigerant flowing into the compressor characterized in that the cooling device having a steam refrigerant early recovery branch pipe. The method of claim 1, And a third branch pipe branched from the second branch pipe and returning a part of the refrigerant flowing through the second branch pipe between the evaporator and the compressor. The method of claim 7, wherein The third branch pipe is provided with a solenoid valve for controlling the flow rate of the refrigerant, characterized in that the cooling device having a steam refrigerant early recovery branch pipe. The method of claim 8, The refrigerant inlet of the compressor further comprises a temperature measuring sensor for measuring the temperature of the refrigerant flowing into the compressor characterized in that the cooling device having a steam refrigerant early recovery branch pipe. Compressor for compressing the refrigerant out; A condenser connected to the compressor to liquefy the refrigerant sent from the compressor; An expansion valve connected to the condenser to reduce a pressure of the refrigerant sent from the condenser; An evaporator connected to the expansion valve and the compressor to evaporate the refrigerant depressurized in the expansion valve and to discharge the refrigerant to the compressor; A first branch pipe branched from the evaporator, the first branch pipe collecting the vapor refrigerant evaporated in the evaporator early and being discharged between the evaporator and the compressor; A second branch pipe which diverges a portion of the refrigerant from the compressor and bypasses the inlet side of the condenser; A third branch pipe branched from the second branch pipe to return a part of the refrigerant flowing through the second branch pipe between the evaporator and the compressor; And a heat exchanger configured to exchange heat between the refrigerant flowing in the first branch pipe and the second branch pipe by passing through the first branch pipe and the second branch pipe together. The method of claim 10, A temperature sensor installed at an inflow side of the pressure gauge to measure a temperature of the refrigerant flowing into the pressure gauge; And a solenoid valve installed in the third branch pipe to adjust a flow rate of the refrigerant according to the temperature of the refrigerant measured by the temperature measuring sensor.

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