KR20230150445A - How to reduce the temperature of the receiver refrigerant liquid in the refrigeration cycle system - Google Patents

Abstract

The present invention relates to a method for reducing the temperature of refrigerant liquid in a receiver of a refrigeration cycle system, comprising: a compressor provided in the middle of a refrigerant circulation line, a primary condenser that condenses and liquefies the high-temperature, high-pressure gaseous refrigerant discharged from the compressor, and the primary condenser. A receiver that temporarily stores the liquid refrigerant condensed in the receiver, an expansion valve that rapidly expands the high-temperature liquid refrigerant flowing from the receiver into a fog state, and a device installed between the receiver and the expansion valve to increase the pressure of the liquid refrigerant and expand it. It consists of a refrigerant flow booster pump that transfers the refrigerant flow to the valve, and an evaporator that evaporates the foggy refrigerant rapidly expanded in the expansion valve through a heat exchange action that takes away heat from the surroundings. In a refrigeration cycle system configured to include a secondary condenser to circulate the refrigerant stored at the top to condense the refrigerant once again and supply it back to the receiver,
A bypass line connected between the refrigerant flow booster pump and the expansion valve to circulate the liquid refrigerant stored in the receiver to the secondary condenser, and 100% of the liquid refrigerant pumped and circulated by the refrigerant flow booster pump Most (60-70%) of the liquid refrigerant is supplied to the expansion valve, while a flow control valve is further included to send some (30-40%) of the liquid refrigerant to the secondary condenser. The high-temperature primary condensation liquid refrigerant, which is primarily condensed and liquefied in the secondary condenser, and the low-temperature secondary condensed liquid refrigerant, which is secondarily condensed and liquefied in the secondary condenser, are allowed to flow into the receiver together, so that the high temperature condensed liquid refrigerant condensed in the primary condenser is This invention is characterized in that the liquid refrigerant whose temperature is reduced can be stored in the receiver so that the temperature of the liquid internal medium and the low temperature liquid refrigerant condensed in the secondary condenser are mixed together to maintain a much lower temperature.

Description

How to reduce the temperature of the receiver refrigerant liquid in the refrigeration cycle system}

The present invention relates to a method of reducing the temperature of the refrigerant liquid in the receiver of a refrigeration cycle system, and more specifically, to reduce the temperature of the refrigerant liquid temporarily stored in the receiver of the refrigeration cycle, thereby smoothly circulating the refrigerant condensed and liquefied in the condenser to the receiver. This relates to a method of reducing the temperature of the refrigerant liquid in the receiver that reduces the power of the compressor and keeps the temperature of the refrigerant liquid sent to the expansion valve low, thus improving the cooling performance of the evaporator.

In general, refrigeration cycle systems are known to be used in devices such as refrigerators and freezers for storing food, beverages, and food at low temperatures for a long time, or air conditioners that maintain a comfortable indoor temperature against high outdoor air.

In the refrigeration cycle system used for the above purposes, the performance of the condenser installed outdoors is reduced due to fine dust generated due to global warming, so the discharge pressure of the compressor increases and the power required increases. As the efficiency of the refrigerator decreases, the operation time of the refrigerator becomes longer, which increases the cost of electrical energy, and also increases the maintenance cost of the compressor.

Looking at the cause of the above problems, the refrigeration cycle system of the prior art, as shown in FIG. 1, uses refrigerant gas evaporated through heat exchange with a heat exchange medium (air, water, etc.) in the evaporator 140. It flows into the compressor 100 through the liquid separator 150, is compressed at high temperature and high pressure, and is discharged to the condenser 110. The high temperature and high pressure refrigerant gas discharged from the condenser 110 has a high temperature due to heat exchange with outdoor air. The refrigerant liquid is condensed and stored in the receiver 120. At this time, the refrigerant liquid stored in the receiver 120 is maintained at the same temperature and pressure as the high-temperature refrigerant liquid condensed in the condenser 110. Because of this condition, the high-temperature refrigerant liquid condensed in the condenser 110 does not circulate smoothly toward the receiver 120, and the high-temperature refrigerant liquid condensed in the condenser 110 does not circulate smoothly toward the receiver 120. In order to circulate properly, the discharge pressure of the compressor 100 must be excessively increased, so there is a problem in that a lot of power is consumed by the compressor, and the temperature and pressure of the refrigerant liquid stored in the receiver 120 are high. When transferred to the expansion valve 130 in a maintained state, the phenomenon of evaporation of the refrigerant in the fog state supplied to the evaporator 140 through heat exchange is reduced, resulting in a problem in which the refrigeration and cooling effects are greatly reduced. do.

In order to solve the above problem, if the temperature of the liquid refrigerant temporarily stored in the receiver is adjusted to be much lower than the temperature of the liquid refrigerant that is condensed and liquefied in the condenser, the circulation of the refrigerant can be smooth. To this end, the present invention The applicant proposed prior art (Patent Registration No. 10-2350303) as a means of controlling the temperature of the liquid refrigerant temporarily stored in the receiver to maintain a lower temperature compared to the temperature of the liquid refrigerant that is condensed and liquefied in the condenser. there is.

In the above prior art, as shown in FIG. 2, the gaseous refrigerant compressed at high temperature and high pressure in the compressor 200 is condensed and liquefied through heat exchange with a heat exchange medium (air, water, etc.) in the primary condenser 210 and then transferred to a receiver ( 220), the gaseous refrigerant stored above the water surface of the liquid refrigerant stored in the receiver 220 is transferred to the secondary condenser 230 and performs heat exchange with a heat exchange medium (air, water, etc.) It is condensed and liquefied and stored again in the receiver 220 and then supplied to the expansion valve 240. The expansion valve 240 rapidly expands the liquid refrigerant supplied from the receiver 220 into a fog state to form an evaporator 250. ), and in the process in which the refrigerant in a fog state supplied to the evaporator 250 takes away heat from the surroundings and evaporates, it is used as an air conditioning system that blows cold air into the room, or takes away a lot of heat to increase the ambient temperature. When cooled and frozen to an appropriate temperature below room temperature, it can be used as a refrigerated freezing system.

However, in the case of the prior art described above, the high-temperature liquid refrigerant condensed in the primary condenser 210, which condenses and liquefies the high-temperature, high-pressure gaseous refrigerant compressed in the compressor 200, is temporarily stored in the receiver 220. , the high-temperature liquid refrigerant temporarily stored inside the receiver 220 is stored together with the gaseous refrigerant. At this time, the liquid refrigerant stored in the lower part of the receiver 220 is stored in the secondary condenser ( Since only the gaseous refrigerant stored in the upper part of the water surface of the receiver 30 is configured to be transferred and supplied to the secondary condenser 230, rather than being supplied to the secondary condenser 230, the liquid phase is condensed and liquefied in the secondary condenser 230. The amount of condensation of the refrigerant is very small and it has no choice but to condense and liquefy. For this reason, the amount of condensation and liquefaction of the liquid refrigerant secondarily condensed in the secondary condenser 230 is very small, so the amount of liquid refrigerant supplied and stored secondarily to the receiver 220 is small, so the receiver ( Since the temperature of the liquid refrigerant stored in 220) and supplied to the expansion valve 240 is not lowered to a large temperature difference compared to the temperature of the liquid refrigerant primarily condensed in the primary condenser 210, the temperature of the refrigerant It is pointed out that the problem is that the phenomenon of poor circulation still remains.

Registered Patent Publication No. 10-2350303 (announced on January 17, 2022)

The present invention is limited in consideration of various problems that appear in the prior art as described above. The liquid refrigerant temporarily stored in the receiver of the refrigeration cycle system is a primary condenser that primarily condenses and liquefies the high-temperature, high-pressure gas refrigerant compressed in the compressor. It is a means of mixing the high-temperature liquid refrigerant discharged from the receiver with the low-temperature liquid refrigerant discharged from the secondary condenser, which secondarily condenses and liquefies the high-temperature liquid refrigerant stored in the receiver, and is transferred and supplied from the receiver to the expansion valve. The liquid refrigerant was invented for the purpose of providing a refrigeration cycle system that allows smooth circulation of the refrigerant by maintaining a much lower temperature than the liquid refrigerant that is primarily condensed and liquefied in the primary condenser.

The present invention is a means to pursue the above objectives,

A compressor provided in the middle of the refrigerant circulation line, a primary condenser for converting the high-temperature and high-pressure gaseous refrigerant compressed to high temperature and pressure by the compressor into high-temperature and isostatic pressure liquid, and the high-temperature and high-pressure liquid refrigerant condensed in the primary condenser. A receiver that temporarily stores the liquid refrigerant, an expansion valve that rapidly expands the high-temperature liquid refrigerant flowing from the receiver into a fog state, and a device installed between the receiver and the expansion valve to control the pressure of the liquid refrigerant supplied from the receiver to the expansion valve. A refrigerant flow booster pump for supplying the refrigerant by increasing the pressure, and a foggy refrigerant rapidly expanded in the expansion valve is evaporated through a heat exchange action that takes away the heat from the external heat exchange medium, absorbing the surrounding heat and then producing low-temperature gas. It consists of an evaporator that changes the state, and a secondary condenser to circulate the refrigerant stored in the upper part of the liquid refrigerant stored in the receiver, condense the refrigerant once again, and supply it back to the receiver. In the refrigeration cycle system,

A bypass line connected between the refrigerant flow booster pump and the expansion valve to circulate the liquid refrigerant stored in the receiver to the secondary condenser, and 100% of the liquid refrigerant pumped and circulated by the refrigerant flow booster pump Most (60-70%) of the liquid refrigerant is supplied to the expansion valve, while a flow control valve is further included to send some (30-40%) of the liquid refrigerant to the secondary condenser. The high-temperature primary condensation liquid refrigerant, which is primarily condensed and liquefied in the secondary condenser, and the low-temperature secondary condensed liquid refrigerant, which is secondarily condensed and liquefied in the secondary condenser, are allowed to flow into the receiver together, so that the high temperature condensed liquid refrigerant condensed in the primary condenser is Low-temperature liquid refrigerant can be supplied to the expansion valve by storing the reduced-temperature liquid refrigerant in the receiver to maintain a much lower temperature by mixing the low-temperature liquid internal medium with the low-temperature liquid refrigerant condensed in the secondary condenser. It is characterized by being structured so that it can be used.

According to the present invention, the high-temperature liquid refrigerant discharged from the primary condenser that primarily condenses and liquefies the gaseous refrigerant compressed at high temperature and high pressure in the compressor and temporarily stored in the receiver, and the liquid refrigerant stored in the receiver is secondarily converted into liquid refrigerant. It is a means of storing the low-temperature liquid refrigerant discharged from the secondary condenser for condensation and liquefaction in a receiver together. The high-temperature liquid refrigerant condensed in the primary condenser and the low-temperature liquid refrigerant condensed in the secondary condenser are stored in the receiver. By storing and mixing together, the refrigerant stored in the receiver and supplied to the expansion valve has the effect of supplying low-temperature liquid refrigerant reduced to a much lower temperature than the temperature of the liquid refrigerant separately condensed in the primary and secondary condensers. There is.

In addition, the above effect is achieved by reducing the temperature of the liquid refrigerant temporarily stored in the receiver to a much lower state compared to the temperature of the liquid refrigerant that is condensed and liquefied in the condenser of the high-temperature, high-pressure gas refrigerant compressed and discharged from the compressor. It has the effect of smoothing circulation, and the expansion valve rapidly expands the liquid refrigerant supplied at a low temperature and supplies it to the evaporator, which has the effect of improving the cooling performance of the evaporator and without excessively increasing the discharge pressure of the compressor. Since the refrigerant can be circulated smoothly, it has the effect of reducing the power consumption of the compressor.

Figure 1 is a circuit diagram of a prior art refrigeration cycle system.
Figure 2 is a circuit diagram of a prior art refrigeration cycle system.
Figure 3 is a circuit diagram of a refrigeration cycle system of the first embodiment of the present invention.
Figure 4 is a refrigeration cycle system circuit diagram of the second embodiment of the present invention.

A specific embodiment of the method for reducing the temperature of the refrigerant liquid in the receiver of the refrigeration cycle system according to the present invention will be described in detail according to the attached drawings as follows.

Figure 3 shows the circuit configuration of the refrigeration cycle system of the first embodiment of the present invention. The refrigeration cycle consists of an outlet line (11) of the compressor (1) provided in the middle of the refrigerant circulation line (10) formed to form a closed circuit. is configured to be connected to the inlet line 21 of the primary condenser (2a), and the outlet line 22 of the primary condenser (2a) is connected to the inlet 31 of the receiver 3, and the sap The inlet line 41 of the refrigerant flow booster pump 4 is connected to the outlet 32 of the unit 3, and the outlet line 42 of the refrigerant flow booster pump 4 is the inlet line of the expansion valve 5. It is configured to be connected to (51).

A solenoid valve (symbol omitted) is installed between the outlet line 42 of the refrigerant flow booster pump 4 and the inlet line 51 of the expansion valve 5, and the outlet line 52 of the expansion valve 5 ) is connected to the inlet line (symbol omitted) of the evaporator 6, the outlet line 61 of the evaporator 6 is connected to the inlet of the liquid separator 7, and the outlet of the liquid separator 7 is connected to the compressor. As a structure formed to be connected to the inlet line 12 of (1), the refrigerant circulation line 10 of the refrigeration cycle is configured to form a closed circuit.

The present invention is to ensure a smooth flow of refrigerant circulating through each component formed in the refrigerant circulation line 10 of the refrigeration cycle formed to form a closed circuit as described above, at the outlet of the receiver 3. Most of the liquid refrigerant pumped by the refrigerant flow rate booster pump (4), which is connected to (32) and transfers the liquid refrigerant stored in the receiver (3), is transferred and supplied to the expansion valve (5), while the liquid refrigerant is supplied to the expansion valve (5). Some of them are configured to include a bypass line (8) for transport and supply to the secondary condenser (2b) and a flow control valve (9) installed in the bypass line (8) to control the flow amount of liquid refrigerant. In addition, in order to enable the refrigerant flow booster pump (4) to pump the liquid refrigerant stored in the receiver (3), the outlet (32) of the receiver (3) is extended to be submerged in the liquid refrigerant. Another feature is that it is configured to further include an extended suction end (32a).

In addition, a bypass line (8) is connected to the inlet line (23) of the secondary condenser (2b), and the outlet line (24) of the secondary condenser (2b) is connected to the liquid phase stored inside the receiver (3). The extended discharge stage 24a, which is formed to be submerged in the refrigerant, is configured to extend.

The flow control valve (9) installed in the bypass line (8) uses an expansion valve ( It is configured to be supplied to the 5) side, while the remaining 30 to 40% of the liquid refrigerant is configured to be adjustable so that it can be supplied to the secondary condenser (2b).

A feature of the present invention is that the flow control valve (9) installed in the bypass line (8) is a receiver in which the high-temperature liquid refrigerant that is primarily condensed and liquefied and discharged from the primary condenser (2a) is temporarily stored. From (3), the liquid refrigerant is pumped by the refrigerant flow booster pump (4) and 60 to 70% of the 100% liquid refrigerant that is discharged to the outlet line (42) is transferred to the expansion valve (5). Meanwhile, 30-40% of the remaining liquid refrigerant is controlled to be transported and supplied to the secondary condenser (2b), and is a means of controlling the high-temperature refrigerant that is primarily condensed and liquefied in the primary condenser (2a). By allowing the liquid refrigerant and the low-temperature liquid refrigerant, which is secondarily condensed and liquefied by the secondary condenser (2b), to flow together into the receiver (3) and mix, the receiver (3) has a primary condenser ( The liquid refrigerant that is discharged from the compressor (1) and is primarily condensed and liquefied in the primary condenser (2a) is stored so that the liquid refrigerant reduced to a much lower temperature is stored than the high temperature liquid refrigerant that is condensed and liquefied and discharged in 2a). Compared to the temperature, the temperature of the liquid refrigerant that is separately condensed in each of the primary condenser (2a) and the secondary condenser (2b) and flows into and mixed together in the receiver (3) is stored at a much lower temperature. This characteristic is such that the temperature of the liquid refrigerant temporarily stored in the receiver (3) is lower than the temperature of the liquid refrigerant that is discharged at high temperature and high pressure from the compressor (1) and is primarily condensed and liquefied in the primary condenser (2a). Even if the discharge pressure of the compressor (1) is not excessively increased by maintaining a low temperature, the high-temperature liquid refrigerant condensed and liquefied in the primary condenser (2a) is transferred to the receiver (3) where the lower liquid refrigerant is stored. In addition to the effect of ensuring smooth circulation, the effect of reducing the electrical energy required for the compressor (1) can be expected.

In the present invention as described above, the liquid refrigerant stored in the receiver (3) is maintained at a much lower temperature than the liquid refrigerant that is primarily condensed and liquefied in the primary condenser (2a), so the refrigerant flow rate booster pump (4) Since the liquid refrigerant pumped and supplied to the expansion valve (5) maintains a low temperature, the foggy refrigerant rapidly expanded by the expansion valve (5) is supplied to the evaporator (6) and performs a heat exchange action to take away heat from the surroundings. Since it is in an active state, there is another feature that allows the cooling performance of the evaporator 6 to be improved.

And, as described above, the low-temperature gaseous refrigerant that is supplied to the evaporator (6) and evaporated through a heat exchange action that takes away heat from the surroundings passes through the liquid separator (7) and enters the compressor (1) through the inlet line (12) of the compressor (1). It flows into the , is compressed at high temperature and high pressure, is discharged to the outlet line (11), and is supplied to the primary condenser (2a), repeating the process repeatedly.

Figure 4 shows the refrigeration cycle system of the second embodiment of the present invention, where the primary condenser (2a) and secondary condenser (2b) of the second embodiment are connected to each other as in the first embodiment of Fig. 3 described above. The only difference is that the primary condenser (2a) and secondary condenser (2b) are installed side by side inside one condenser body (2) as shown in the drawing, rather than being installed separately at separate locations. Since the components and the configuration in which each component is connected to form a closed circuit are the same as the first embodiment described above, detailed description thereof will be omitted.

The operational effects exhibited by the first and second embodiments of the present invention configured as described above will be described as follows.

In the first and second embodiments of the present invention, the high-temperature, high-pressure gas refrigerant compressed and discharged from the compressor (1) flows into the primary condenser (2a) and is condensed and liquefied through heat exchange with a heat exchange medium (air, water, etc.). At this time, the liquid refrigerant that is primarily condensed and liquefied in the primary condenser (2a) maintains a lower temperature than the high-temperature, high-pressure gas refrigerant compressed in the compressor (1), but maintains a temperature significantly higher than the outdoor air temperature. am. In this way, the high-temperature liquid refrigerant that is primarily condensed and discharged from the primary condenser (2a) is temporarily stored inside the receiver (3) through the inlet (31) of the receiver (3).

The high-temperature liquid refrigerant temporarily stored in the receiver (3) is discharged through the outlet (32) of the receiver (3) by the pumping operation of the refrigerant flow booster pump (4) and transferred to the discharge line (42). At this time, the high-temperature liquid refrigerant that is transported and discharged to the outlet line (42) through the pumping operation of the refrigerant flow booster pump (4) is controlled by a flow rate control system installed in the bypass line (8) connected to the outlet line (42). Most of the liquid refrigerant, which accounts for 60 to 70% of the 100% liquid refrigerant discharged to the outlet line 42 of the refrigerant flow booster pump 4 by the valve 9, is transferred to the expansion valve 5. Meanwhile, the remaining portion, or 30 to 40% of the liquid refrigerant, is transferred to the secondary condenser (2b) through the bypass line (8).

The high-temperature liquid refrigerant supplied to the secondary condenser (2b) is secondarily condensed and liquefied by heat exchange with a heat exchange medium (air, water, etc.) in the secondary condenser (2b) and reduced to a low-temperature liquid refrigerant. The liquid refrigerant whose temperature has been reduced to a low temperature in the secondary condenser (2b) is discharged through the outlet line (24) and temporarily stored in the receiver (3).

Therefore, the receiver (3) contains a high-temperature liquid refrigerant that is primarily condensed and liquefied in the primary condenser (2a) and a secondary condenser ( Since the low-temperature liquid refrigerant that is transferred to 2b) and is secondarily condensed and liquefied is stored and mixed together, the receiver (3) contains the high-temperature liquid refrigerant that is primarily condensed in the primary condenser (2a). The low-temperature liquid refrigerant that is secondarily condensed in the secondary condenser (2b) is mixed, and the reduced-temperature liquid refrigerant is temporarily stored.

Therefore, the amount of energy temporarily stored in the receiver (3) is reduced compared to the high-temperature liquid refrigerant liquefied in the primary condenser (2a), which primarily condenses the high-temperature, high-pressure gas refrigerant compressed and discharged from the compressor (1). The temperature of the liquid refrigerant is maintained at a much lower temperature, and accordingly, the temperature is lower than the high temperature of the liquid refrigerant liquefied in the primary condenser (2a), which primarily condenses the high-temperature, high-pressure gaseous refrigerant compressed and discharged from the compressor (1). Since the liquid refrigerant temporarily stored in the receiver (3) maintains a low temperature, it is compressed from the compressor (1) of the refrigerant circulation line (10) of the refrigeration cycle to the primary condenser (2a), secondary condenser (2b), and receiver. The circulation of the refrigerant circulating in the order of (3) is carried out smoothly.

As described above, each embodiment in which the refrigerant circulates smoothly in the order of the compressor (1), the primary condenser (2a), the secondary condenser (2b), and the receiver (3) will be described in more detail. , assuming that the temperature of the liquid refrigerant that is primarily condensed and liquefied in the primary condenser (2a) flows into the receiver (3) while maintaining 45°C when the outdoor temperature in the summer is 35°C, the sap The temperature of the liquid refrigerant discharged through the outlet 32 of the unit 3 is also maintained at 45°C, and in this state, the refrigerant flow booster pump 4 increases the flow rate of the liquid refrigerant to the expansion valve 5. Transfer and supply is carried out. At this time, a bypass line (8) is connected to the outlet line (42) of the refrigerant flow booster pump (4), and a flow control valve (9) is installed in the bypass line (8). Therefore, the liquid refrigerant pumped by the refrigerant flow booster pump (4) and transferred with an increased flow rate is transferred in a state where it is properly distributed to the expansion valve (5) and the secondary condenser (2b) by the flow control valve (9). It becomes a state of being.

In other words, the flow control valve (9) is adjusted so that most of the liquid refrigerant, which is 60 to 70% of the 100% liquid refrigerant pumped by the refrigerant flow booster pump (4), is transferred to the expansion valve (5). Meanwhile, a portion corresponding to 30 to 40% is adjusted to be transferred to the secondary condenser (2b) through the bypass line (8), so 60 to 70% of the portion that is transferred to the expansion valve (5) is controlled in this way. The liquid refrigerant, which depends on the ratio, expands rapidly in a fog state and is supplied to the evaporator (6), where it is evaporated and vaporized through a heat exchange action that takes away the surrounding heat, while being transferred to the secondary condenser (2b) at a ratio of 30 to 40%. The liquid refrigerant corresponding to is maintained at a temperature of 45°C and flows into the secondary condenser (2b), and the liquid refrigerant with a temperature of 45°C flowing into the secondary condenser (2b) is in contact with the outdoor air (35°C). The liquid refrigerant, which is secondarily condensed and liquefied through the heat exchange action and condensed to a lower temperature of about 37°C, is discharged to the outlet line (24) and stored in the receiver (3).

Therefore, the receiver (3) contains a liquid refrigerant with a temperature as high as 45°C, which is primarily condensed and liquefied in the primary condenser (2a), and a liquid refrigerant lowered to about 37°C, which is secondarily condensed and liquefied in the secondary condenser (2b). Since the refrigerant is stored and mixed together, the high-temperature liquid refrigerant condensed to 45°C in the primary condenser (2a) and the low-temperature liquid refrigerant condensed to 37°C in the secondary condenser (2b) are stored in the receiver (3). The refrigerants are stored and mixed together, so that the liquid refrigerant lowered to about 41°C is stored, and the pressure of the liquid refrigerant lowered to about 45°C, which is primarily condensed and liquefied in the primary condenser (2a), and the liquid refrigerant (3) ) The difference in pressure between the liquid refrigerant mixed to a temperature of about 41°C temporarily stored in ) results in a pressure difference of approximately 2 bar, so the temperature and pressure of the liquid refrigerant condensed and liquefied in the primary condenser (2a) are high. On the other hand, since the temperature and pressure of the liquid refrigerant temporarily stored in the receiver (3) remain relatively low, the high temperature (45°C) liquid refrigerant is primarily condensed and liquefied in the primary condenser (2a). The refrigerant circulates smoothly toward the receiver (3), where the liquid refrigerant at a lower temperature (37°C) is stored.

In addition, the low-temperature liquid refrigerant stored in the receiver (3), which accounts for 30 to 40% of the liquid refrigerant pumped by the refrigerant flow booster pump (4), is supplied through the bypass line (8). It is transferred to the secondary condenser (2b), condensed and liquefied at a lower temperature by the action of heat exchange with the outdoor air as described above, and sent to the receiver (3) together with the high temperature liquid refrigerant condensed in the primary condenser (2a). While being stored and mixed, most of the liquid refrigerant, which accounts for 60 to 70% of the liquid refrigerant pumped by the refrigerant flow booster pump (4), is transferred to the expansion valve (5) and is pressurized and supplied. Therefore, the expansion valve (5) rapidly expands the liquid refrigerant into a fog state, making it possible to normally transport and supply the fog refrigerant to the evaporator (6). The fog refrigerant supplied to the evaporator (6) is supplied to the surrounding environment. The low-temperature gaseous refrigerant evaporating from the evaporator (6) passes through the liquid separator (7) and then flows into the compressor (1) through the inlet line (12) of the compressor to produce high-temperature and high-pressure air. The operation of being compressed and discharged to the primary condenser (2a) is repeated repeatedly.

As described above, the first and second embodiments of the present invention are a high-temperature liquid refrigerant that is liquefied in the primary condenser (2a), which primarily condenses the high-temperature, high-pressure gaseous refrigerant compressed and discharged from the compressor (1). By storing and mixing the low-temperature liquid refrigerant that is secondarily condensed in the secondary condenser (2b) in the receiver (3), the temperature of the liquid refrigerant temporarily stored in the receiver (3) is lowered. It can be reduced as much as possible, and the liquid refrigerant pumped by the refrigerant flow booster pump (4) and transferred to the expansion valve (5) is reduced to a low temperature and supplied, so that the refrigerant in a fog state is rapidly expanded in the expansion valve (5). Since it can be normally supplied to the evaporator 6, the effect of improving the cooling performance of the evaporator 6 can be expected.

1: Compressor 2: Condenser body
2a: primary condenser 2b: secondary condenser
3: Receiver 31,32: Inlet and outlet
4: Refrigerant flow booster pump 5: Expansion valve
6: Evaporator 7: Liquid separator
8: Bypass line 9: Flow control valve
10: Refrigerant circulation line

Claims (1)

A compressor provided in the middle of the refrigerant circulation line, a primary condenser for converting the high-temperature and high-pressure gaseous refrigerant compressed to high temperature and pressure by the compressor into high-temperature and isostatic pressure liquid, and the high-temperature and high-pressure liquid refrigerant condensed in the primary condenser. A receiver that temporarily stores the liquid refrigerant, an expansion valve that rapidly expands the high-temperature liquid refrigerant flowing from the receiver into a fog state, and a device installed between the receiver and the expansion valve to control the pressure of the liquid refrigerant supplied from the receiver to the expansion valve. A refrigerant flow booster pump for supplying the refrigerant by increasing the pressure, and a foggy refrigerant rapidly expanded in the expansion valve is evaporated through a heat exchange action that takes away the heat from the external heat exchange medium, absorbing the surrounding heat and then producing low-temperature gas. It consists of an evaporator that changes the state, and a secondary condenser to circulate the refrigerant stored in the upper part of the liquid refrigerant stored in the receiver, condense the refrigerant once again, and supply it back to the receiver. In the refrigeration cycle system,
A bypass line connected between the refrigerant flow booster pump and the expansion valve to circulate the liquid refrigerant stored in the receiver to the secondary condenser, and 100% of the liquid refrigerant pumped and circulated by the refrigerant flow booster pump Most (60-70%) of the liquid refrigerant is supplied to the expansion valve, while a flow control valve is further included to send some (30-40%) of the liquid refrigerant to the secondary condenser. The high-temperature primary condensation liquid refrigerant, which is primarily condensed and liquefied in the secondary condenser, and the low-temperature secondary condensed liquid refrigerant, which is secondarily condensed and liquefied in the secondary condenser, are allowed to flow into the receiver together, so that the high temperature condensed liquid refrigerant condensed in the primary condenser is The liquid refrigerant of the refrigeration cycle system, which is configured to store the liquid refrigerant whose temperature has been reduced in the receiver so that the low-temperature liquid internal medium and the low-temperature liquid refrigerant condensed in the secondary condenser are mixed together to maintain a much lower temperature. Method of reducing the temperature of the refrigerant liquid.