KR101649193B1 - Cascade refrigeration cycle system - Google Patents

Abstract

Disclosed is a cascade refrigeration cycle system capable of performing cryogenic refrigeration effectively. The cascade refrigeration cycle system of the present invention includes: a first compressor for compressing a first refrigerant in a gas state and discharging the compressed first refrigerant; a first condenser for condensing the first refrigerant compressed in the first compressor and then discharging the condensed first refrigerant; a first heat exchanger which is provided with the first refrigerant condensed in the first condenser and then passes the first refrigerant through; a first expansion part for expanding the first refrigerant passing through the first heat exchanger; a second compressor for compressing a second refrigerant in a gas state and then discharging the compressed second refrigerant; an evaporation and condensation heat exchanger which condenses the second refrigerant compressed in the second compressor and then discharges the second refrigerant, and evaporates the first refrigerant expanded in the first expansion part using heat generated during condensation of the second refrigerant, and then provides the evaporated first refrigerant for the first heat exchanger; a second expansion part for expanding the second refrigerant condensed in the evaporation and condensation heat exchanger; and an evaporator which evaporates the second refrigerant expanded in the second expanding part while absorbing heat from the outside, and provides the evaporated second refrigerant for the second compressor. The first heat exchanger delivers the evaporated first refrigerant to the first compressor by passing the evaporated first refrigerant provided from the evaporation and condensation heat exchanger. So, the cascade refrigeration cycle system of the present invention can perform heat exchange between the evaporated first refrigerant and the condensed first refrigerant efficiently, while the evaporated first refrigerant and the condensed first refrigerant provided from the first condenser are passed.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a dual-

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dual refrigeration cycle system, and more particularly, to a dual refrigeration cycle system capable of linking two refrigeration cycles to form a cryogenic temperature.

A refrigerator is a device that takes heat from one side and transfers it to the other side to reduce the temperature of the other side. Such a refrigerator can generally be configured to include a compressor, a condenser, a receiver, an expansion valve and an evaporator.

The compressor compresses the low-temperature and low-pressure gas refrigerant supplied from the evaporator to high-temperature and high-pressure and delivers the gas refrigerant to the high-temperature and high-pressure refrigerant. And the liquid receiver temporarily stores the liquid refrigerant condensed at a high temperature and a high pressure in the condenser. The expansion valve rapidly expands the high-temperature and high-pressure liquid refrigerant supplied from the receiver to transfer the low-temperature low-pressure refrigerant to the evaporator. The evaporator controls the low-temperature and low-pressure refrigerant supplied from the expansion valve, Exchanges heat with the heat exchange medium to evaporate heat to generate low-temperature and low-pressure gaseous refrigerant, which is then transferred to the compressor.

However, since the refrigerator is performed by one refrigeration cycle, there is a limitation in cooling the temperature of one side of the refrigerator to an ultra-low temperature, for example, minus 50 or less. In order to solve such a problem, in recent years, a dual refrigeration cycle system has been mainly used. The two-way refrigeration cycle system refers to a device capable of cooling to a cryogenic temperature in the low-temperature-side refrigeration cycle by interconnecting the low-temperature-side refrigeration cycle and the high-temperature-side refrigeration cycle for heat exchange.

Generally, the two-way refrigeration cycle system includes a first refrigeration cycle device for circulating a first refrigerant such as R-22 to perform the high temperature side refrigeration cycle, and a second refrigeration cycle device for circulating the refrigerant such as R- And a condenser in the second refrigeration cycle apparatus is disposed adjacent to the evaporator in the first refrigeration cycle apparatus to perform heat exchange. That is, the heat generated in the condenser in the second refrigeration cycle apparatus is transferred to the evaporator in the first refrigeration cycle apparatus to induce the evaporation of the refrigerant, thereby improving the heat transfer efficiency. Thus, in the freezer of the second refrigeration cycle apparatus The internal temperature can be cooled to a very low temperature.

On the other hand, the dual-cycle refrigeration cycle system is also subjected to a load during driving, and in particular, a load may be applied to the second refrigeration cycle apparatus, leading to a reduction in efficiency or a failure. Therefore, in order to reduce the load of the binary refrigeration cycle system or to maintain a constant cooling efficiency, various additional apparatuses are installed. For example, in the second refrigeration cycle apparatus, there is a heat discharging device for lowering the temperature of the refrigerant by a heat exchange action with external heat and air exchange media such as air and water before the high-temperature and high-pressure gas refrigerant discharged from the compressor is transferred to the condenser .

However, the above-mentioned dual refrigeration cycle system may incur an increase in cost due to the additional device, and even if the additional device is further provided, there may be a limit to increase the heat transfer efficiency. Further, when the additional device is required to be powered on, the power consumption may increase.

Therefore, a problem to be solved by the present invention is to provide a two-way refrigeration cycle system capable of effectively performing cryogenic cooling.

In order to solve these problems, a binary refrigeration cycle system according to an exemplary embodiment of the present invention includes a primary compressor, a primary condenser, a primary heat exchanger, a primary expansion unit, a secondary compressor, an evaporative condensation heat exchanger, An expansion portion and an evaporator.

The primary compressor compresses and discharges the first refrigerant in a gaseous state. The primary condenser condenses and discharges the first refrigerant compressed in the primary compressor. The primary heat exchanger receives and passes the first refrigerant condensed in the primary condenser. The primary expansion portion expands the first refrigerant that has passed through the primary heat exchanger. The secondary compressor compresses and discharges the gaseous second refrigerant. The evaporating condensing heat exchanger condenses and discharges the second refrigerant compressed in the secondary compressor and evaporates the first refrigerant expanded in the primary expansion part by using heat generated during the condensation of the second refrigerant, It is provided as a car heat exchanger. The secondary expansion portion expands the condensed second refrigerant in the evaporative condensation heat exchanger. The evaporator evaporates the second refrigerant expanded in the second expansion part while absorbing heat from the outside, and provides the evaporated second refrigerant to the secondary compressor. Wherein the first heat exchanger passes the evaporated first refrigerant provided from the evaporative condensation heat exchanger to the primary compressor, and the condensed first refrigerant provided from the evaporated first refrigerant and the primary condenser Exchanges heat between the evaporated first refrigerant and the condensed first refrigerant.

Wherein the primary heat exchanger includes a primary body portion horizontally disposed with respect to an earth surface and having a primary heat exchange space formed therein, a primary heat exchange portion disposed through the primary body portion, a primary inlet portion connected to the primary body portion, And a primary outlet coupled to the primary body. At this time, the evaporated first refrigerant provided from the evaporative condensation heat exchanger may be introduced into the primary heat exchange space through the primary inlet and then discharged to the primary compressor through the primary outlet, When the condensed first refrigerant provided from the primary condenser passes through the primary heat exchanging unit, heat is exchanged with the evaporated first refrigerant introduced into the primary heat exchanging space, and the refrigerant can be discharged to the primary expansion unit.

The primary body may have a cylindrical shape elongated in a first direction parallel to the earth's surface and the primary heat exchanging part may have a pipe structure elongated along the first direction to penetrate the primary body, The primary discharge part may have a piping structure formed through the primary body part in a second direction perpendicular to the first direction.

The primary heat exchanging part may be disposed adjacent to the cylindrical side wall of the primary body part, and the end of the primary discharging part may have an oblique shape so as to form an inclined surface, wherein the long side part of the oblique- As shown in FIG.

A plurality of heat exchange fins may be formed on the outer surface of the primary heat exchanger to increase the surface area.

The binary refrigeration cycle system may further include a receiver for storing the condensed first refrigerant provided from the primary condenser and providing the condensed first refrigerant to the primary heat exchanger.

Wherein the binary refrigeration cycle system passes the compressed second refrigerant provided from the secondary compressor to the evaporative condensation heat exchanger and passes the evaporated second refrigerant provided from the evaporator to the secondary compressor And a second heat exchanger for exchanging heat between the compressed second refrigerant and the evaporated second refrigerant while the compressed second refrigerant and the evaporated second refrigerant pass through each other.

Wherein the secondary heat exchanger includes a secondary body portion horizontally disposed with respect to an earth surface and having a secondary heat exchange space formed therein, a secondary heat exchange portion disposed through the secondary body portion, a secondary inlet portion connected to the secondary body portion And a secondary discharge portion connected to the secondary body portion. At this time, the evaporated second refrigerant provided from the evaporator may be introduced into the secondary heat exchanging space through the secondary inlet and then discharged to the secondary compressor through the secondary outlet, When the compressed second refrigerant provided from the second heat exchange unit passes through the secondary heat exchange unit, heat is exchanged with the evaporated second refrigerant introduced into the secondary heat exchange space, and the refrigerant can be discharged to the secondary expansion unit.

The secondary body may have a cylindrical shape elongated in a first direction parallel to an earth surface and the secondary heat exchanger may have a piping structure elongated along the second direction so as to pass through the secondary body, The secondary discharge unit may have a piping structure formed through the secondary body in a second direction perpendicular to the first direction.

Wherein the secondary heat exchanging part is disposed adjacent to the cylindrical side wall of the secondary body part, and the end of the secondary discharging part has an oblique shape so as to form an inclined surface, the long side part of the oblique- As shown in FIG.

A plurality of heat exchange fins may be formed on the outer surface of the secondary heat exchanger to increase the surface area.

The binary refrigeration cycle system may further include a depressurization unit for reducing a pressure of the second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger.

The depressurizing portion is provided with a part of the second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger to reduce the pressure, and then the depressurized portion is supplied to the secondary heat exchanger together with the evaporated second refrigerant supplied from the evaporator .

The pressure reducing portion may include a pressure adjusting unit, an expansion tank, and a capillary. The pressure regulating unit receives and discharges a part of the second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger. The expansion tank stores the second refrigerant provided in the pressure regulating unit. The capillary tube expands the second refrigerant provided in the expansion tank and then provides the second refrigerant together with the evaporated second refrigerant provided from the evaporator to the secondary heat exchanger.

The evaporator may include at least one of a cooler capable of cooling the outside and a freezing device capable of freezing the object to be cooled.

The freezing device may be an immersion freezing device capable of freezing the object to be cooled at a cryogenic temperature.

The immersion type freezing apparatus may include a housing portion, a brine, a refrigerant evaporator, a cooled object mounting portion, and an object to be cooled. The housing part has a lower space inside and an upper space adjacent to the lower space. The brine is arranged in a liquid state in the lower space. Wherein the refrigerant evaporator is arranged to contact the brine in the lower space, evaporates the expanded second refrigerant provided from the secondary expansion part while absorbing heat from the brine, and supplies the evaporated second refrigerant to the secondary It is provided as a compressor. The object to be cooled is placed on the object to be cooled. The object to be cooled may move the object to be cooled from the lower space to the upper space or from the upper space to the lower space.

The immersion type freezing apparatus may further include a brine circulating unit capable of circulating the brine.

The brine circulation unit absorbs the gas in the upper space and discharges the brine to the brine to circulate the brine.

The brine circulation unit may include an air blower and an injection unit. The air blower absorbs the gas in the upper space through the suction pipe and discharges the gas through the discharge pipe. The injection unit is arranged to contact the brine in the lower space, and the gas discharged from the air blower is injected through a plurality of nozzles.

Next, a binary refrigeration cycle system according to another exemplary embodiment of the present invention includes a primary compressor, a primary condenser, a primary expansion unit, a secondary compressor, a secondary heat exchanger, an evaporation condensation heat exchanger, a secondary expansion unit, .

The primary compressor compresses and discharges the first refrigerant in a gaseous state. The primary condenser condenses and discharges the first refrigerant compressed in the primary compressor. The primary expansion portion expands the first refrigerant condensed in the primary condenser. The secondary compressor compresses and discharges the gaseous second refrigerant. The secondary heat exchanger receives and passes the second refrigerant compressed by the secondary compressor. The evaporating condensing heat exchanger condenses and discharges the second refrigerant that has passed through the secondary heat exchanger and evaporates the first refrigerant expanded in the primary expansion part by using heat generated during the condensation of the second refrigerant, Provided as a car compressor. The secondary expansion portion expands the condensed second refrigerant in the evaporative condensation heat exchanger. The evaporator evaporates the second refrigerant expanded in the second expansion part while absorbing heat from the outside, and provides the evaporated second refrigerant to the secondary heat exchanger. Wherein the second heat exchanger passes the evaporated second refrigerant provided from the evaporator to the secondary compressor, and the evaporated second refrigerant and the compressed second refrigerant provided from the secondary compressor pass each other The heat exchanged between the evaporated second refrigerant and the compressed second refrigerant.

Wherein the secondary heat exchanger includes a secondary body portion horizontally disposed with respect to an earth surface and having a secondary heat exchange space formed therein, a secondary heat exchange portion disposed through the secondary body portion, a secondary inlet portion connected to the secondary body portion And a secondary discharge portion connected to the secondary body portion. At this time, the evaporated second refrigerant provided from the evaporator may be introduced into the secondary heat exchanging space through the secondary inlet and then discharged to the secondary compressor through the secondary outlet, When the compressed second refrigerant provided from the second heat exchange unit passes through the secondary heat exchange unit, heat is exchanged with the evaporated second refrigerant introduced into the secondary heat exchange space, and the refrigerant can be discharged to the secondary expansion unit.

The secondary body may have a cylindrical shape elongated in a first direction parallel to an earth surface and the secondary heat exchanger may have a piping structure elongated along the second direction so as to pass through the secondary body, The secondary discharge unit may have a piping structure formed through the secondary body in a second direction perpendicular to the first direction.

Wherein the secondary heat exchanging part is disposed adjacent to the cylindrical side wall of the secondary body part, and the end of the secondary discharging part has an oblique shape so as to form an inclined surface, the long side part of the oblique- As shown in FIG.

A plurality of heat exchange fins may be formed on the outer surface of the secondary heat exchanger to increase the surface area.

The binary refrigeration cycle system may further include a depressurization unit for reducing a pressure of the second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger.

The depressurizing portion is provided with a part of the second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger to reduce the pressure, and then the depressurized portion is supplied to the secondary heat exchanger together with the evaporated second refrigerant supplied from the evaporator .

The pressure reducing portion may include a pressure adjusting unit, an expansion tank, and a capillary. The pressure regulating unit receives and discharges a part of the second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger. The expansion tank stores the second refrigerant provided in the pressure regulating unit. The capillary tube expands the second refrigerant provided in the expansion tank and then provides the second refrigerant together with the evaporated second refrigerant provided from the evaporator to the secondary heat exchanger.

As described above, according to the two-way refrigeration cycle system of the present invention, in the first heat exchanger, the first refrigerant in the liquid state supplied from the receiver to the first expansion unit, and the first refrigerant in the gas phase supplied to the first compressor in the evaporative condensation heat exchanger The first compressor is incompletely compressed due to the first refrigerant remaining in the liquid state due to incomplete vaporization in the evaporative condensation heat exchanger as the heat exchange between the first refrigerant is naturally performed, The piping resistance is increased due to the flash gas of the first refrigerant moving to the expansion portion, and the function of the primary expansion portion is prevented from being deteriorated. That is, the first refrigerant vaporized in the evaporative condensation heat exchanger is heated to evaporate the liquid-phase refrigerant that has not evaporated, and the liquid-phase first refrigerant supplied to the first expansion unit in the receiver is cooled, The efficiency in the primary refrigeration cycle can be increased.

Further, in the secondary heat exchanger, heat exchange is naturally performed between the gaseous second refrigerant supplied from the secondary compressor to the evaporative condensation heat exchanger and the gaseous second refrigerant supplied from the evaporator to the secondary compressor , The secondary compressor can be prevented from incompletely compressing due to the second liquid refrigerant remaining due to the incomplete vaporization in the evaporator, and the second refrigerant moving from the secondary compressor to the evaporative condensation heat exchanger So that it can be suppressed from increasing to a high temperature. That is, the efficiency of the secondary refrigeration cycle for performing cooling in the evaporator can be increased.

In addition, it is also possible that the depressurizing part receives a part of the gaseous second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger to reduce the pressure, and then the secondary refrigerant supplied from the evaporator, The second refrigerant flowing from the secondary compressor to the evaporative condensation heat exchanger is prevented from increasing to an excessively high pressure, thereby further increasing the efficiency of the secondary refrigeration cycle.

In addition, the freezing device, which is one of the evaporators, absorbs the cooling gas in the upper space of the housing part and discharges the brine to the brine disposed in the lower space of the housing part to circulate the brine so that the refrigerant evaporating part The efficiency of heat exchange between the second refrigerant circulated through the second refrigerant and the brine can be further improved.

1 is a block diagram illustrating a binary refrigeration cycle system according to an embodiment of the present invention.
Fig. 2 is a block diagram showing a specific example of the binary refrigeration cycle system of Fig. 1. Fig.
3 is a partially cutaway perspective view of the primary heat exchanger of the binary refrigeration cycle system of FIG.
4 is a front view of the primary heat exchanger of Fig. 3;
5 is a view showing a primary heat exchanger of an embodiment different from that of FIG.
FIG. 6 is a view showing a freezing device of the binary refrigeration cycle system of FIG. 1; FIG.

The present invention is capable of various modifications and various forms, and specific embodiments are illustrated in the drawings and described in detail in the text. It should be understood, however, that the invention is not intended to be limited to the particular forms disclosed, but includes all modifications, equivalents, and alternatives falling within the spirit and scope of the invention. Like reference numerals are used for like elements in describing each drawing. In the accompanying drawings, the dimensions of the structures may be exaggerated to illustrate the present invention.

The terms first, second, etc. may be used to describe various components, but the components should not be limited by the terms. The terms are used only for the purpose of distinguishing one component from another. For example, without departing from the scope of the present invention, the first component may be referred to as a second component, and similarly, the second component may also be referred to as a first component.

The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The singular expressions include plural expressions unless the context clearly dictates otherwise. In the present application, the terms "comprising" or "having ", and the like, are intended to specify the presence of stated features, integers, steps, operations, elements, parts, or combinations thereof, But do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, parts, or combinations thereof. In addition, A and B are 'connected' and 'coupled', meaning that A and B are directly connected or combined, and other component C is included between A and B, and A and B are connected or combined .

Unless defined otherwise, all terms used herein, including technical or scientific terms, have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. Terms such as those defined in commonly used dictionaries are to be interpreted as having a meaning consistent with the contextual meaning of the related art and are to be interpreted as either ideal or overly formal in the sense of the present application Do not. Also, in the claims of a method invention, each step may be reversed in order, unless the steps are clearly constrained in order.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings.

1 is a block diagram illustrating a binary refrigeration cycle system according to an embodiment of the present invention.

Referring to FIG. 1, the dual refrigeration cycle system according to the present embodiment includes a primary compressor 10, a primary condenser 20, a receiver 30, a primary heat exchanger 40, a primary expansion unit 50 A secondary condenser 70, a secondary heat exchanger 80, a secondary expansion unit 90, an evaporator 100, and a depressurization unit 200. The evaporator 100 may be a condenser,

The primary compressor (10) compresses and discharges the first refrigerant in a gaseous state. Specifically, the primary compressor (10) can receive the first refrigerant in the gaseous state from the primary heat exchanger (40), compress it, and provide it to the primary condenser (20).

The primary condenser 20 condenses and discharges the first refrigerant compressed in the primary compressor 10. Specifically, the primary condenser 20 receives the compressed first gaseous refrigerant from the primary compressor 10 to generate a first gaseous refrigerant in the liquid state, . Here, the first refrigerant discharged from the primary condenser 20 may be in a high-temperature, high-pressure liquid state.

The receiver (30) temporarily stores the condensed first refrigerant from the primary condenser (20) and then provides it to the primary heat exchanger (40).

The primary heat exchanger (40) can receive the condensed first refrigerant from the receiver (30) and pass it to the primary expansion unit (50). Here, the condensed first refrigerant passes through the primary heat exchanger (40) and releases heat to generate secondary condensation.

The primary expansion unit 50 may receive the condensed first refrigerant from the primary heat exchanger 40 and expand it to the evaporative condensation heat exchanger 60. Here, the primary expansion part 50 may be, for example, an expansion valve capable of expanding and reducing the condensed first refrigerant.

The evaporative condensation heat exchanger 60 may provide the expanded first refrigerant from the primary expansion unit 50 to the primary heat exchanger 40 by evaporating it. Specifically, the evaporative condensation heat exchanger (60) may include an evaporator (62) for evaporating and discharging the expanded first refrigerant while absorbing heat. Here, the first refrigerant evaporated in the evaporator 62 may be in a low-temperature, low-pressure state.

The primary heat exchanger 40 may pass the evaporated first refrigerant provided from the evaporator 62 to the primary compressor 10. At this time, the primary heat exchanger (40) is configured such that, while the evaporated first refrigerant provided from the evaporator (62) and the condensed first refrigerant provided from the receiver (30) Exchanged between the first refrigerant and the condensed first refrigerant. Specifically, for example, the heat released while the condensed first refrigerant passes through the primary heat exchanger (40) may be transferred to the evaporated first refrigerant passing through the primary heat exchanger (40) have.

Thereafter, the first refrigerant passing through the primary heat exchanger (40) and provided to the primary compressor (10) is compressed again through the primary compressor (10) and transferred to the primary condenser (20) , The primary refrigeration cycle can be repeatedly performed.

The first refrigerant in the liquid state supplied from the receiver 30 to the primary expansion unit 50 and the primary refrigerant in the evaporator 62 from the primary compressor 10 are supplied to the primary expansion unit 50, The first compressor 10 is prevented from being incompletely compressed due to the first refrigerant remaining in the liquid state due to the incomplete vaporization in the evaporator 62, And the piping resistance is increased due to the flash gas of the first refrigerant flowing from the receiver (30) to the primary expansion part (50), so that the function of the primary expansion part (50) Can also be suppressed. That is, the first refrigerant vaporized in the evaporator 62 is heated to vaporize the liquid refrigerant that has not evaporated, and at the same time, the liquid refrigerant, which is supplied to the primary expander 50 from the receiver 30, The efficiency of the first refrigeration cycle can be increased by cooling the first refrigerant of the first refrigeration cycle.

On the other hand, the secondary compressor 70 compresses and discharges the second refrigerant in a gaseous state. Specifically, the secondary compressor (70) can provide the secondary refrigerant in the gaseous state from the secondary heat exchanger (80), compress it, and provide it to the secondary heat exchanger (80). Here, the second refrigerant compressed by the secondary compressor (70) may be in a state of a high temperature and high pressure gas.

The secondary heat exchanger 80 may receive the compressed second refrigerant from the secondary compressor 70 and may pass the refrigerant to the evaporative condensation heat exchanger 60. Here, the compressed second refrigerant may discharge heat while passing through the secondary heat exchanger (80).

The evaporative condensation heat exchanger (60) can condense the compressed second refrigerant that has passed through the secondary heat exchanger (80) and provide it to the secondary expansion part (90). Specifically, the evaporative condensation heat exchanger (60) may further include a condensing portion (64) for condensing and discharging the compressed second refrigerant while releasing heat. At this time, the condensing part 64 may be disposed adjacent to the evaporating part 62 so as to perform heat exchange. That is, the heat released when the compressed second refrigerant is condensed in the condenser 64 is provided to the evaporator 62 to induce the evaporation of the expanded first refrigerant. Here, the evaporative condensation heat exchanger 60 may be, for example, a plate-type heat exchanger capable of simultaneously performing evaporation and condensation.

The secondary expansion part 90 may receive the condensed second refrigerant from the condensing part 90 and expand it, and then provide the expanded second refrigerant to the evaporator 100. Here, the primary expansion portion 50 may be, for example, an expansion portion capable of expanding and reducing the condensed second refrigerant.

The evaporator 100 may provide the expanded second refrigerant from the secondary expansion unit 90 to the secondary heat exchanger 80 by evaporating it. The evaporator 100 absorbs the ambient heat when the expanded second refrigerant is evaporated, thereby lowering the temperature. Here, the evaporator 100 may include at least one of a cooler 100A that can cool the outside air and a freezer 100B that can freeze the object to be cooled.

The secondary heat exchanger 80 may receive the evaporated second refrigerant from the evaporator 100 and may pass the evaporated second refrigerant to the secondary compressor 70. At this time, the secondary heat exchanger (80) is configured such that while the evaporated second refrigerant provided from the evaporator (100) and the compressed second refrigerant provided from the secondary compressor (70) Exchanged between the second refrigerant and the compressed second refrigerant. Specifically, for example, the heat released while the compressed second refrigerant passes through the secondary heat exchanger 80 may be transferred to the evaporated second refrigerant passing through the secondary heat exchanger 80 have.

The second refrigerant passing through the secondary heat exchanger 80 and supplied to the secondary compressor 70 is further compressed through the secondary compressor 70 and transferred to the secondary heat exchanger 80 By repeating the above process, the secondary refrigeration cycle can be repeated.

In this way, according to the second refrigeration cycle, the second refrigerant in the gaseous state supplied from the secondary compressor 70 to the condenser 64 and the second refrigerant supplied from the evaporator 100 to the secondary compressor 70 The second compressor 70 is prevented from incompletely compressing due to the second liquid refrigerant remaining due to the incomplete vaporization in the evaporator 100. As a result, And the second refrigerant flowing from the secondary compressor (70) to the condenser (64) can be prevented from increasing to an excessively high temperature. As a result, the efficiency of the secondary refrigeration cycle can be further increased.

In the present embodiment, the binary refrigeration cycle system further includes a decompression unit 200 for reducing the pressure of the gaseous second refrigerant transferred from the secondary heat exchanger 80 to the condenser unit 64 can do. Specifically, the depressurization unit 200 may be provided with a part of the second refrigerant transferred from the secondary heat exchanger 80 to the condenser unit 64 to reduce the pressure of the second refrigerant, And may be supplied to the secondary heat exchanger (80) together with the evaporated second refrigerant.

After the decompression unit 200 receives a portion of the gaseous second refrigerant transferred from the secondary heat exchanger 80 to the condenser unit 64 to reduce the pressure of the second refrigerant, The second refrigerant in the gaseous state moving from the secondary compressor 70 to the condenser 64 is excessively supplied to the secondary heat exchanger 80 together with the evaporated second refrigerant By suppressing the increase in the high pressure, the efficiency of the secondary refrigeration cycle can be further increased.

In the present embodiment, the primary refrigeration cycle is a high temperature side refrigeration cycle, and the secondary refrigeration cycle may be a low temperature side refrigeration cycle. For example, the first refrigerant used in the primary refrigeration cycle may be R-22, and the second refrigerant used in the secondary refrigeration cycle may be R-23.

Fig. 2 is a block diagram showing a specific example of the binary refrigeration cycle system of Fig. 1. Fig.

1 and 2, in the primary refrigeration cycle, the binary refrigeration cycle system includes a first filter drier D1, a first level gauge L1, a primary valve L1 and a primary pressure switch P1 ). ≪ / RTI >

The first filter drier D1 is disposed between the primary heat exchanger 40 and the primary expansion unit 50 so that the condensed first refrigerant that has passed through the primary heat exchanger 40 And the impurities can be removed and discharged. The primary level gauge L1 is disposed between the primary filter dryer D1 and the primary expansion unit 50 to check the amount of the first refrigerant flowing through the piping. The primary electron L1 may be disposed between the primary level gauge L1 and the primary expansion unit 50 to turn on / off the flow of the first refrigerant through the piping. The primary pressure switch P1 can control the pressure while checking the pressure of the first refrigerant at any position in the primary refrigerant cycle. For example, the primary pressure switch P1 may be a Differential Pressure Transmitter (DPT).

The two-way refrigeration cycle system may further include a second filter drier D2, a second level gauge L2, a secondary valve L2 and a secondary pressure switch P2 in the secondary refrigeration cycle .

The second filter dryer D2 is disposed between the condenser 64 and the secondary expansion unit 90 to remove moisture and impurities from the condensed second refrigerant supplied from the condenser 64, . The second level gauge (L2) is disposed between the secondary filter drier (D2) and the secondary expansion unit (90) to check the amount of the second refrigerant flowing through the piping. The secondary electron L2 may be disposed between the secondary level gauge L2 and the secondary expansion unit 90 to turn on / off the flow of the second refrigerant through the pipe. The secondary pressure switch P2 can control the pressure while checking the pressure of the second refrigerant at an arbitrary position in the secondary refrigerant cycle. For example, the secondary pressure switch P2 may be a differential pressure transmitter (DPT).

In addition, the binary refrigeration cycle system may include a plurality of ball valves in the secondary refrigeration cycle. For example, the binary refrigeration cycle system may further include first, second, and third ball valves B1, B2, and B3.

The first ball valve (B1) is disposed on the input side of the condenser (64) and is capable of interrupting the compressed second refrigerant supplied to the condenser (64). The second ball valve B2 is disposed on the output side of the condenser 64 and can interrupt the condensed second refrigerant discharged from the condenser 64. The third ball valve B1 is disposed between the secondary expansion part 90 and the evaporator 100 and is disposed between the secondary expansion part 90 and the evaporator 100. The third ball valve B1 is disposed between the secondary expansion part 90 and the evaporator 100, The refrigerant can be interrupted.

The pressure reducing unit 200 may include a pressure adjusting unit 210, an expansion tank 220, and a capillary tube 230, for example.

The pressure regulating unit 210 receives a part of the compressed second refrigerant transferred from the secondary heat exchanger 80 to the condenser 64, and primarily regulates and discharges the pressure. The expansion tank 220 secondarily reduces the pressure while storing the second refrigerant supplied from the pressure regulating unit 210. The capillary tube 230 expands the second refrigerant provided in the expansion tank 220 to reduce the pressure of the tertiary pressure, and then the capillary tube 230, together with the evaporated second refrigerant supplied from the evaporator 100, (80).

The depressurization unit 200 may further include a first check valve 240, a second check valve 250, and an electronic valve 260. The first check valve 240 may be disposed on the input side of the pressure adjusting unit 210 to prevent the compressed second refrigerant supplied to the pressure adjusting unit 210 from flowing backward. The second check valve 250 is disposed between the expansion tank 220 and the capillary 230 so that the compressed second refrigerant transferred from the expansion tank 220 to the capillary 230 flows back You can block things. The electronic valve 260 may be disposed between the second check valve 250 and the capillary 230 to turn on / off the flow of the second refrigerant through the piping.

FIG. 3 is a partially cutaway perspective view showing a primary heat exchanger of the binary refrigeration cycle system of FIG. 1, and FIG. 4 is a front view of the primary heat exchanger of FIG.

3 and 4, the primary heat exchanger 40 includes a primary body 11, a primary heat exchanger 12, a primary inlet 13, and a primary outlet 14 .

The primary body 11 may be horizontally disposed with respect to the ground surface and a primary heat exchange space may be formed therein. For example, the primary body part 11 may have a cylindrical shape elongated in a first direction parallel to the surface of the earth.

The primary heat exchanging part 12 may be arranged to pass through the primary body part 11. For example, the primary heat exchanging part 12 may have a piping structure extending along the first direction so as to pass through the primary body part 11. [

The primary inlet (13) may be connected to the primary body (11). For example, the primary inlet 13 may be connected to the primary body 11 in a second direction perpendicular to the first direction. Therefore, the evaporated first refrigerant provided from the evaporator 62 may be introduced into the primary heat exchange space through the primary inlet 13.

The primary discharge part 14 may be connected to the primary body part 11. For example, the primary discharge portion 14 may have a piping structure formed through the primary body portion in the second direction. Therefore, the evaporated first refrigerant introduced into the primary heat exchange space can be discharged to the primary compressor (10) through the primary discharge portion (14).

As the primary heat exchanging part 12 is arranged to penetrate the primary body part 11, the condensed first refrigerant provided from the receiver 30 is introduced into the primary heat exchanging part 12 The refrigerant is heat-exchanged with the evaporated first refrigerant introduced into the primary heat exchange space and discharged to the primary filter dryer D1.

The primary heat exchanging part 12 may be disposed adjacent to the cylindrical side wall of the primary body part 11. The primary discharge portion 14 may be formed so as to be adjacent to the primary heat exchange portion 12. At this time, the end of the primary discharge portion 14 may have an oblique shape, and the long side of the oblique shape may be disposed adjacent to the cylindrical sidewall of the primary body portion 11.

Since the primary discharge portion 14 is formed so as to be adjacent to the primary heat exchanging portion 12, the evaporated first refrigerant introduced into the primary heat exchanging space is discharged to the primary heat exchanging portion 12 can be effectively heat-exchanged with the condensed first refrigerant and discharged to the primary compressor (10).

Meanwhile, the primary discharge portion 14 may be formed in a plurality corresponding to the number of the primary compressors 10. For example, when the primary compressors 10 are separately disposed, the primary discharge units 14 may be formed separately from the two primary discharge units 14a and 14b.

Here, when the primary body part 11 is arranged horizontally with respect to the ground surface, when the primary heat exchanger 40 is connected to a plurality of compressors, the imbalance between the plurality of compressors is eliminated .

5 is a view showing a primary heat exchanger of an embodiment different from that of FIG.

Referring to FIG. 5, a plurality of heat exchange fins may be formed on the outer surface of the primary heat exchanger 12 to increase the surface area. As a result, when the condensed first refrigerant provided from the receiver (30) passes through the primary heat exchange unit (12), the evaporated first refrigerant introduced into the primary heat exchange space through the heat exchange fins As shown in Fig.

Subsequently, the secondary heat exchanger 80 substantially has the same structure as the primary heat exchanger 40 and includes, for example, a secondary body portion, a secondary heat exchanger portion, a secondary inlet portion, and a secondary outlet portion can do.

The secondary body may be disposed horizontally with respect to the ground surface and a secondary heat exchange space may be formed therein. For example, the secondary body may have a cylindrical shape elongated in a third direction parallel to the surface of the earth.

The secondary heat exchanger may be arranged to pass through the secondary body. For example, the secondary heat exchanger may have a pipe structure extending along the third direction so as to pass through the secondary body. A plurality of heat exchange fins may be formed on the outer surface of the secondary heat exchanger to increase the surface area.

The secondary inlet may be connected to the secondary body. For example, the secondary inlet may be connected to the secondary body in a fourth direction perpendicular to the third direction. Accordingly, the evaporated second refrigerant supplied from the evaporator 100 may be introduced into the secondary heat exchange space through the secondary inlet.

The secondary discharge portion may be connected to the secondary body portion. For example, the secondary outlet may have a piping structure formed through the secondary body in the fourth direction. Therefore, the evaporated second refrigerant introduced into the secondary heat exchange space can be discharged to the secondary compressor (70) through the secondary discharge portion.

When the compressed second refrigerant supplied from the secondary compressor (70) passes through the secondary heat exchange unit, the secondary heat exchange unit is disposed in the secondary heat exchange space And may be discharged to the condenser 64 while exchanging heat with the second evaporated refrigerant.

Meanwhile, the secondary heat exchanger may be disposed adjacent to the cylindrical side wall of the secondary body. In addition, the secondary discharge portion may be formed so as to protrude so as to be adjacent to the secondary heat exchange portion. At this time, the end of the secondary discharge part may have a curved shape so as to form an inclined surface, and the long side of the curved shape may be disposed adjacent to the cylindrical side wall of the secondary body part.

Meanwhile, the secondary discharge portion may be formed in a plurality corresponding to the number of the secondary compressors. For example, when the secondary compressors are separated into two, the secondary discharge units may be separately formed.

Hereinafter, the power unit 100B, which is one of the evaporators 100, will be described in detail.

FIG. 6 is a view showing a freezing device of the binary refrigeration cycle system of FIG. 1; FIG.

6, the freezing device 100B may be an immersion freezing device capable of freezing an object to be cooled such as vegetables or the like at a cryogenic temperature, and may be a soaking device such as a housing part 110, a brine 120, An object to be cooled 130, an object to be cooled 140, and a object to be cooled 150.

The housing part 110 may have a lower space 112 and an upper space 114 adjacent to the lower space 112 and the upper side. The brine 120 may be disposed in the lower space 112 of the housing part 110 in a liquid state. The refrigerant evaporator 130 is disposed in the lower space 112 of the housing part 110 so as to be in contact with the brine 120. The refrigerant evaporator 130 is connected to the brine 120 via the suction line 132, The expanded second refrigerant may be evaporated while absorbing heat from the brine 120 and the evaporated second refrigerant may be provided to the secondary heat exchanger 80 through the discharge line 134. [ The object to be cooled 140 is mounted on the object to be cooled. The object to be cooled 150 is moved from the lower space 112 to the upper space 114 or from the upper space 114 to the lower space 112 .

In this way, the refrigerant evaporator 130 cools the brine 120 while evaporating the expanded second refrigerant provided from the secondary expansion unit 90, and the cooled brine 120 is cooled The object to be cooled, which has been placed in the water holder 140, can be frozen at an extremely low temperature, for example, between -65 and 75 degrees.

The freezing apparatus 100B may further include a brine circulating unit 160 capable of circulating the brine 120. [

The brine circulation unit 160 absorbs the gas in the upper space 114 of the housing unit 110 and discharges the gas to the brine 120 to circulate the brine 120. For example, the brine circulation unit 160 may include an air blower 162 and an injection unit 164.

The air blower 162 can absorb the gas in the upper space 114 through the suction pipe 162a and discharge the gas through the discharge pipe 162b. The injection unit 164 is disposed in the lower space 112 so as to be connected to the discharge pipe 162b and is in contact with the brine 120. The gas discharged through the air blower 162 is passed through a plurality of nozzles Can be sprayed. Here, a plurality of the injection units 164 may be disposed so as to improve circulation efficiency of the brine 120.

The freezing apparatus 100B absorbs the cooling gas at a low temperature in the upper space 114 of the housing unit 110 and absorbs the cooling gas at the lower space 112 of the housing unit 110, The refrigerant circulates through the refrigerant evaporator 130 while minimizing the temperature drop of the brine 120 and the heat exchange between the brine 120 and the second refrigerant circulated through the refrigerant evaporator 130. [ The efficiency can be further improved.

While the present invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims.

10: primary compressor 20: primary condenser
30: Receiving machine 40: Primary heat exchanger
50: primary expansion part 60: evaporative condensation heat exchanger
62: evaporator 64: condenser
70: Secondary compressor 80: Secondary heat exchanger
90: Secondary expansion part 100: Evaporator
100A: Cooler 100B: Freezer
110: housing part 112: lower space
114: upper space 120: brine
130: Refrigerant evaporator 140:
150: object to be cooled moving part 160: brine circulation part
162: air blower 164: injection unit

Claims (28)

A primary compressor for compressing and discharging the gaseous first refrigerant;
A primary condenser for condensing and discharging the first refrigerant compressed in the primary compressor;
A primary heat exchanger for receiving and passing the first refrigerant condensed in the primary condenser;
A primary expansion unit for expanding the first refrigerant passing through the primary heat exchanger;
A secondary compressor for compressing and discharging the gaseous second refrigerant;
The first refrigerant compressed in the secondary compressor is condensed and discharged, and the first refrigerant expanded in the primary expansion part is evaporated using the heat generated during the condensation of the second refrigerant to provide the primary refrigerant as the primary heat exchanger An evaporative condensation heat exchanger;
A secondary expansion unit for expanding the second refrigerant condensed in the evaporative condensation heat exchanger;
And an evaporator which evaporates the second refrigerant expanded in the secondary expansion part while absorbing heat from the outside and provides the evaporated second refrigerant to the secondary compressor,
The primary heat exchanger
Passing the evaporated first refrigerant provided from the evaporative condensation heat exchanger to the primary compressor, while the condensed first refrigerant provided from the evaporated first refrigerant and the primary condenser are passed through each other , Heat exchange between the evaporated first refrigerant and the condensed first refrigerant,
The evaporator
And an immersion freezing device capable of freezing the object to be cooled at a cryogenic temperature,
The immersion freezing apparatus
A housing part having a lower space inside and an upper space adjacent to the lower space;
A brine arranged in a liquid state in the lower space;
The second refrigerant being disposed in contact with the brine in the lower space, evaporating the expanded second refrigerant from the brine while absorbing heat from the brine, and providing the evaporated second refrigerant to the secondary compressor A refrigerant evaporator;
An object to be cooled for placing the object to be cooled;
An object to be cooled that can move the object to be cooled from the lower space to the upper space or from the upper space to the lower space; And
And a brine circulation unit capable of circulating the brine,
The brine circulation unit
Absorbing the gas in the upper space, discharging the gas to the brine, circulating the brine,
An air blower which absorbs gas in the upper space through a suction pipe and discharges the gas through a discharge pipe; And
And a jetting unit arranged to contact the brine in the lower space and jetting the gas discharged from the air blower through a plurality of nozzles. The heat exchanger according to claim 1, wherein the primary heat exchanger
A primary body portion disposed horizontally with respect to an earth surface and having a primary heat exchange space formed therein, a primary heat exchanger portion disposed through the primary body portion, a primary inlet portion connected to the primary body portion, And a primary discharge portion connected to the body portion,
The evaporated first refrigerant supplied from the evaporative condensation heat exchanger is introduced into the primary heat exchange space through the primary inlet and then discharged to the primary compressor through the primary outlet,
And the condensed first refrigerant provided from the primary condenser is heat-exchanged with the evaporated first refrigerant flowing into the primary heat exchange space when the refrigerant passes through the primary heat exchange unit, and is discharged to the primary expansion unit Binary refrigeration cycle system. [3] The apparatus according to claim 2, wherein the primary body has a cylindrical shape elongated in a first direction parallel to an earth surface,
Wherein the primary heat exchanger has a pipe structure extending along the first direction so as to pass through the primary body,
Wherein the primary discharge portion has a piping structure formed through the primary body portion in a second direction perpendicular to the first direction. 4. The heat exchanger according to claim 3, wherein the primary heat exchanger is disposed adjacent to a cylindrical sidewall of the primary body,
Wherein the end portion of the primary discharge portion has an oblique shape so that the longer side portion of the oblique shape is disposed adjacent to the cylindrical side wall of the primary body portion. The heat exchanger according to claim 3, wherein an outer surface of the primary heat exchanger
Wherein a plurality of heat exchange fins are formed to increase the surface area. 2. The dual refrigeration cycle system of claim 1, further comprising a receiver that stores the condensed first refrigerant provided from the primary condenser and provides the primary refrigerant to the primary heat exchanger. 2. The refrigerating machine according to claim 1, further comprising: a second refrigerant passing from the secondary compressor to the evaporative condensation heat exchanger; a second refrigerant provided from the evaporator to be passed to the secondary compressor; Further comprising a secondary heat exchanger for exchanging heat between the compressed second refrigerant and the evaporated second refrigerant while the compressed second refrigerant and the evaporated second refrigerant are passing through each other, Refrigeration cycle system. 8. The heat exchanger according to claim 7, wherein the secondary heat exchanger
A secondary body portion disposed horizontally with respect to the ground surface and having a secondary heat exchange space formed therein, a secondary heat exchanger portion disposed through the secondary body portion, a secondary inlet portion connected to the secondary body portion, And a secondary discharge portion connected to the body portion,
The evaporated second refrigerant supplied from the evaporator flows into the secondary heat exchange space through the secondary inlet and is discharged to the secondary compressor through the secondary outlet,
Characterized in that the compressed second refrigerant provided from the secondary compressor is discharged to the secondary expansion portion while heat-exchanging with the evaporated secondary refrigerant introduced into the secondary heat exchange space when passing through the secondary heat exchange portion Binary refrigeration cycle system. 9. The apparatus according to claim 8, wherein the secondary body has a cylindrical shape elongated in a first direction parallel to an earth surface,
Wherein the secondary heat exchanger has a pipe structure extending along the first direction so as to pass through the secondary body,
Wherein the secondary discharge portion has a piping structure formed through the secondary body portion in a second direction perpendicular to the first direction. 10. The heat exchanger according to claim 9, wherein the secondary heat exchanger is disposed adjacent to a cylindrical sidewall of the secondary body,
Wherein the end of the secondary discharge portion has a slant shape so as to form an inclined surface and the long side portion of the slant shape is disposed adjacent to the cylindrical side wall of the secondary body portion. The heat exchanger according to claim 9, wherein an outer surface of the secondary heat exchanger
Wherein a plurality of heat exchange fins are formed to increase the surface area. The dual refrigeration cycle system according to claim 7, further comprising a depressurization unit for reducing a pressure of the second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger. 13. The apparatus according to claim 12, wherein the pressure-
The second heat exchanger is provided with a part of the second refrigerant transferred to the evaporative condensation heat exchanger to reduce the pressure and then to the secondary heat exchanger together with the evaporated second refrigerant provided from the evaporator. Binary refrigeration cycle system. 14. The apparatus according to claim 13, wherein the pressure-
A pressure regulating unit for receiving and discharging a part of the second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger;
An expansion tank for storing the second refrigerant supplied from the pressure adjusting unit; And
And a capillary that expands the second refrigerant provided in the expansion tank and then provides the secondary refrigerant together with the evaporated second refrigerant provided from the evaporator to the secondary heat exchanger. delete delete delete delete delete delete A primary compressor for compressing and discharging the gaseous first refrigerant;
A primary condenser for condensing and discharging the first refrigerant compressed in the primary compressor;
A primary expansion unit for expanding the first refrigerant condensed in the primary condenser;
A secondary compressor for compressing and discharging the gaseous second refrigerant;
A secondary heat exchanger for receiving and passing the second refrigerant compressed by the secondary compressor;
The second refrigerant that has passed through the second heat exchanger is condensed and discharged and the first refrigerant expanded in the first expansion portion is evaporated using the heat generated during the condensation of the second refrigerant to be supplied to the primary compressor An evaporative condensation heat exchanger;
A secondary expansion unit for expanding the second refrigerant condensed in the evaporative condensation heat exchanger;
And an evaporator which evaporates the second refrigerant expanded in the second expansion part while absorbing heat from the outside and provides the evaporated second refrigerant to the secondary heat exchanger,
The secondary heat exchanger
Passing the evaporated second refrigerant provided from the evaporator to the secondary compressor, while the evaporated second refrigerant and the compressed second refrigerant provided from the secondary compressor are passed through each other, Exchanges heat between the second refrigerant and the compressed second refrigerant,
The evaporator
And an immersion freezing device capable of freezing the object to be cooled at a cryogenic temperature,
The immersion freezing apparatus
A housing part having a lower space inside and an upper space adjacent to the lower space;
A brine arranged in a liquid state in the lower space;
The second refrigerant being disposed in contact with the brine in the lower space, evaporating the expanded second refrigerant from the brine while absorbing heat from the brine, and providing the evaporated second refrigerant to the secondary compressor A refrigerant evaporator;
An object to be cooled for placing the object to be cooled;
An object to be cooled that can move the object to be cooled from the lower space to the upper space or from the upper space to the lower space; And
And a brine circulation unit capable of circulating the brine,
The brine circulation unit
Absorbing the gas in the upper space, discharging the gas to the brine, circulating the brine,
An air blower which absorbs gas in the upper space through a suction pipe and discharges the gas through a discharge pipe; And
And a jetting unit arranged to contact the brine in the lower space and jetting the gas discharged from the air blower through a plurality of nozzles. 22. The system of claim 21, wherein the secondary heat exchanger
A secondary body portion disposed horizontally with respect to the ground surface and having a secondary heat exchange space formed therein, a secondary heat exchanger portion disposed through the secondary body portion, a secondary inlet portion connected to the secondary body portion, And a secondary discharge portion connected to the body portion,
The evaporated second refrigerant supplied from the evaporator flows into the secondary heat exchange space through the secondary inlet and is discharged to the secondary compressor through the secondary outlet,
Characterized in that the compressed second refrigerant provided from the secondary compressor is discharged to the secondary expansion portion while heat-exchanging with the evaporated secondary refrigerant introduced into the secondary heat exchange space when passing through the secondary heat exchange portion Binary refrigeration cycle system. 23. The method of claim 22, wherein the secondary body has a cylindrical shape elongated in a first direction parallel to the ground surface,
Wherein the secondary heat exchanger has a pipe structure extending along the first direction so as to pass through the secondary body,
Wherein the secondary discharge portion has a piping structure formed through the secondary body portion in a second direction perpendicular to the first direction. 24. The apparatus of claim 23, wherein the secondary heat exchanger is disposed adjacent a cylindrical sidewall of the secondary body,
Wherein the end of the secondary discharge portion has a slant shape so as to form an inclined surface and the long side portion of the slant shape is disposed adjacent to the cylindrical side wall of the secondary body portion. 24. The heat exchanger according to claim 23, wherein an outer surface of the secondary heat exchanger
Wherein a plurality of heat exchange fins are formed to increase the surface area. 22. The dual refrigeration cycle system of claim 21, further comprising a depressurization unit for reducing the pressure of the second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger. 27. The apparatus as claimed in claim 26, wherein the pressure-
The second heat exchanger is provided with a part of the second refrigerant transferred to the evaporative condensation heat exchanger to reduce the pressure and then to the secondary heat exchanger together with the evaporated second refrigerant provided from the evaporator. Binary refrigeration cycle system. 28. The apparatus as claimed in claim 27, wherein the pressure-
A pressure regulating unit for receiving and discharging a part of the second refrigerant transferred from the secondary heat exchanger to the evaporative condensation heat exchanger;
An expansion tank for storing the second refrigerant supplied from the pressure adjusting unit; And
And a capillary that expands the second refrigerant provided in the expansion tank and then provides the secondary refrigerant together with the evaporated second refrigerant provided from the evaporator to the secondary heat exchanger.

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