KR102477314B1 - A method for reducing the temperature of the coolant in the receiver of the refrigeration cycle system and improving the cooling performance of the evaporator - Google Patents

Abstract

The present invention relates to a method for reducing the temperature of a refrigerant liquid in a receiver of a refrigeration cycle system, and a method for improving evaporator cooling performance. The present invention relates to a refrigeration cycle system including: a compressor provided in the middle of a refrigerant circulation line; a primary condenser for turning the high-temperature and high-pressure gaseous refrigerant compressed and discharged from the compressor into a high-temperature and uniform-pressure liquid; a receiver for temporarily storing high-temperature and high-pressure liquid refrigerant condensed and liquefied in the primary condenser and discharged; a refrigerant flow rate boosting pump for pumping the liquid refrigerant stored in the receiver and supplying it to an expansion valve; an evaporator for absorbing ambient heat and then converting it into a low-temperature gaseous state in the process of evaporating the refrigerant in a fog state rapidly expanded in the expansion valve by a heat exchange action that takes away heat from the external heat exchange medium; and a secondary condenser configured to form a liquid separator for filtering out liquid refrigerant contained in the low-temperature gaseous refrigerant that evaporates by taking heat from the surroundings by heat exchange action with the external heat exchange medium in the evaporator, and sending only gaseous refrigerant to the compressor, to condense and liquefy the liquid refrigerant pumped by the refrigerant flow rate boosting pump and store it in the receiver.

Description

A method for reducing the temperature of the coolant in the receiver of the refrigeration cycle system and improving the cooling performance of the evaporator}

The present invention relates to a method for reducing the temperature of a refrigerant solution in a receiver of a refrigeration cycle system and a method for improving evaporator cooling performance, and more particularly, in a primary condenser and a secondary condenser installed in the middle of a refrigerant circulation line of a refrigeration cycle. As a means of mixing and storing the liquid refrigerant that is separately condensed and liquefied in the receiver, it is possible to reduce the temperature of the refrigerant liquid stored in the receiver, and most of the lower temperature liquid refrigerant that is secondarily condensed in the secondary condenser By supplying to the expansion valve side, the expansion valve rapidly expands the low-temperature liquid refrigerant to supply the misty refrigerant to the evaporator, and is configured to improve the cooling performance of the evaporator. It relates to a method for reducing the temperature of a refrigerant liquid and a method for improving evaporator cooling performance.

In general, refrigerating cycle systems are used in refrigerators and freezers for storing food and beverages as well as food ingredients and food at low temperatures for a long time, or air conditioners and refrigerating and freezing equipment used to maintain a comfortable indoor temperature against high outdoor air. It is known that there are

In the refrigeration cycle system used for the above purposes, as the performance of the condenser installed to be exposed to the outdoors deteriorates due to fine dust generated due to global warming, the discharge pressure of the compressor increases, and as a result, the required power of the compressor is reduced. In addition, the efficiency of the refrigerator is lowered, resulting in a longer operation time of the refrigerator, which increases the cost of electric energy and increases the maintenance cost of the compressor.

Looking at the cause of the above problems, the prior art refrigeration cycle system is configured as shown in FIG. 5.

That is, in the prior art refrigeration cycle system, the low-temperature and low-pressure refrigerant gas evaporated by heat exchange with a heat exchange medium (air, water, etc.) in the evaporator 140 flows into the compressor 100 via the liquid separator 150, and the The refrigerant gas flowing into the compressor 100 is compressed to a high temperature and high pressure, discharged, and flows into the condenser 110. Condensed and discharged, the high-temperature refrigerant liquid discharged from the condenser 110 flows into the receiver 120 and is temporarily stored. At this time, the temperature of the refrigerant liquid temporarily stored in the receiver 120 is the condenser 110 Since the temperature is maintained at the same temperature as the refrigerant liquid discharged from the condenser 110, a phenomenon in which the high-temperature refrigerant liquid condensed into a liquid phase does not smoothly circulate toward the receiver 120 appears. In order for the high-temperature refrigerant liquid condensed into a liquid phase in the condenser 110 to be circularly circulated toward the receiver 120, the discharge pressure of the compressor 100 must be excessively increased. It is pointed out as a problem that the power of the compressor 100 is excessively consumed.

In addition, when the refrigerant liquid stored in the receiver 120 is transferred to the expansion valve 130 in a state where the temperature and pressure are maintained high, the temperature of the liquid refrigerant flowing into the expansion valve 130 increases and the evaporator 140 ) causes a problem that significantly reduces the cooling performance.

In order to solve the above problem, when the temperature of the liquid refrigerant temporarily stored in the receiver is lower than the temperature of the liquid refrigerant condensed and liquefied in the condenser, not only the circulation of the refrigerant can be smoothly performed, but also the expansion valve Since it is possible to adjust the temperature of the liquid refrigerant flowing into the receiver to be lowered, the inventors of the present invention for this purpose, compared to the temperature of the liquid refrigerant condensed and liquefied in the condenser, the temperature of the liquid refrigerant temporarily stored in the receiver to maintain a lower temperature As a means for improvement, prior art-1 (Patent Registration No. 10-2350303) has been proposed.

As shown in FIG. 6, in the prior art-1 described above, the gaseous refrigerant compressed to a high temperature and high pressure in the compressor 200 and discharged flows into the primary condenser 210, and flows into the primary condenser 210. The high-temperature, high-pressure gaseous refrigerant is condensed and liquefied through heat exchange with a heat exchange medium (air, water, etc.) and discharged. The liquid refrigerant discharged from the primary condenser 210 is temporarily stored in the receiver 220, and the water The gaseous refrigerant stored on the water surface (w) of the liquid refrigerant temporarily stored in the condenser 220 is transferred to the secondary condenser 230 and condensed and liquefied by heat exchange with a heat exchange medium (air, water, etc.) It is temporarily stored 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 to transfer the misty refrigerant to the evaporator 250. and the refrigerant supplied to the evaporator 250 is used as an air conditioning system that blows the cooled air into the room in the process of evaporating by taking away heat from the surroundings, or taking away a lot of heat to lower the ambient temperature below room temperature. It is configured to be used as a refrigeration and freezing system that cools and freezes to an appropriate temperature.

However, in the case of the prior art-1 (Patent Registration No. 10-2350303), the high-temperature liquid refrigerant condensed in the primary condenser 210 condenses and liquefies the gaseous refrigerant compressed to a high temperature and high pressure in the compressor 200. When temporarily stored in the receiver 220, the high-temperature liquid refrigerant temporarily stored inside the receiver 220 is stored together with the gaseous refrigerant in the gaseous state. At this time, the receiver 220 The liquid refrigerant stored in the lower part is not supplied to the secondary condenser 230, but the gaseous refrigerant stored in the upper part of the water surface (w) of the receiver 220 is transported and supplied to the secondary condenser 230. Therefore, the condensation amount of the liquid refrigerant condensed and liquefied in the secondary condenser 230 is inevitably condensed and liquefied in a very small amount. For this reason, since the amount of condensation and liquefaction of the liquid refrigerant secondarily condensed in the secondary condenser 230 is very small, the liquid refrigerant secondarily condensed and liquefied in the secondary condenser 230 is stored in the receiver 220 in a small amount. This is because it is in a state of supply.

Therefore, in the receiver 22, a large amount of the firstly condensed liquid refrigerant that is primarily condensed and liquefied in the first condenser 210 and a small amount of secondarily condensed and liquefied secondarily condensed in the second condenser 23 Since the stored liquid refrigerant is stored and mixed together, the temperature of the liquid refrigerant stored and mixed in the receiver 230 is not lowered enough to show a significant temperature difference compared to the temperature of the liquid refrigerant condensed and liquefied in the primary condenser 210. There is a concern that the circulation of the refrigerant circulated from the primary condenser 210 to the receiver 230 is not smooth and the circulation of the refrigerant becomes slow.

In order to solve the above problems in the prior art and pre-registered prior art-1, the inventors of the present invention have proposed prior art-2 (Patent Registration No. 10-2022-0049809) as an earlier application.

In the prior art prior art-2 described above, as shown in FIG. 7, the high-temperature and high-pressure gaseous refrigerant compressed and discharged from the compressor 301 formed in the middle of the refrigerant circulation line 300 constituting the closed circuit is a primary condenser (302a) In the primary condenser 302a, the liquid refrigerant condensed and liquefied by heat exchange with outdoor air of the high-temperature and high-pressure gaseous refrigerant is temporarily stored in the receiver 303, and stored in the receiver 303 The liquid refrigerant is pumped by the refrigerant flow-increase pump 304 and transferred to the expansion valve 305, and the expansion valve 305 rapidly expands the liquid refrigerant and supplies the refrigerant in a fog state to the evaporator 306. The misty refrigerant supplied to the evaporator 306 takes heat from the surrounding heat exchange medium (air, water, etc.) and cools the surroundings, while evaporating in the process of taking the heat and changing into a low-temperature, low-pressure gaseous refrigerant. The gaseous refrigerant evaporating at low temperature and low pressure flows into the compressor 301 through the liquid separator 307 and is compressed to a high temperature and high pressure, which is configured to repeat the process repeatedly.

In addition, the prior art-2 of the prior application described above is a bypass circuit (308) in the middle of the refrigerant circulation line (300) configured as a closed circuit to pump the liquid refrigerant stored in the receiver (303) and supply it to the expansion valve (305). ) is connected, and the secondary condenser (302b) is configured in the bypass circuit 308, while the bypass circuit 308 is pumped and supplied to the expansion valve 305 by the refrigerant flow boosting pump 304 A flow control valve 309 for controlling the flow rate of the refrigerant supplied to the secondary condenser 302b of the liquid refrigerant corresponding to 30 to 40% of the total ratio of 100% of the liquid refrigerant is installed, and the secondary condenser In (302b), the liquid refrigerant condensed and liquefied by the heat exchange action with the heat exchange medium (air, water, etc.) flows into the receiver 303 so that the receiver 303 is primarily condensed in the primary condenser 302a. A means for supplying and transporting the liquid refrigerant stored in the receiver 303 to the expansion valve 305 by reducing the temperature of the liquid refrigerant stored in the receiver 303 by storing the liquid refrigerant and the liquid refrigerant secondarily condensed and liquefied in the secondary condenser 302b. , It is configured to improve the cooling performance of the evaporator 306 by supplying the refrigerant in a fog state rapidly expanded in the expansion valve 305 to the evaporator 306 .

If the prior art-2 configured as described above predicts and looks at an embodiment according to reducing the temperature of the liquid refrigerant stored in the receiver 304, for example; When the outdoor temperature in the summer season is 35 ° C, the temperature of the high-temperature and high-pressure gas refrigerant compressed at the compressor 301 and introduced into the inlet of the primary condenser 302a is 90 ° C, and in the primary condenser 302a Assuming that the temperature of the liquid refrigerant that is primarily condensed and liquefied by heat exchange with a heat exchange medium (air, water, etc.) is 45°C, the temperature of the liquid refrigerant flowing into the inlet of the secondary condenser 302b is 45°C. The temperature of the liquid refrigerant that flows into and is condensed and liquefied by the heat exchange action with the heat exchange medium will be reduced to 37 ° C and stored in the receiver 303.

Therefore, in the prior art-2 of the prior application, the 45° C. liquid refrigerant that is primarily condensed and liquefied in the primary condenser (302a) and the 37° C. liquid refrigerant that is secondarily condensed and liquefied in the secondary condenser (302b) are together. Since it is introduced into the receiver 303 and mixed, the liquid refrigerant stored in the receiver 303 maintains a temperature reduced to approximately 41 ° C. The temperature of the liquid refrigerant condensed and liquefied in the primary condenser 302a (45 ° C), while the temperature (41 ° C) of the liquid refrigerant stored in the receiver 303 is low, so the high temperature (45 ° C) liquid refrigerant condensed and liquefied in the primary condenser 302a By providing an effect that allows the liquid refrigerant of a lower temperature (41 ° C.) to be smoothly circulated to the receiver 303 in which it is stored, the required power of the compressor 301 is reduced by preventing the compressor 301 from operating excessively. While it can be assumed that there is an advantage that can be reduced, the high temperature (45 ℃) liquid refrigerant condensed and liquefied in the primary and secondary condensers (302a) (302b) and low temperature (37 ℃) When the liquid refrigerant is mixed, the cooling performance of the evaporator 306 is improved to some extent by supplying the liquid refrigerant of the difference value (41 ℃) to the expansion valve 305 for the temperature difference between the two types of high and low liquid refrigerants. It can be assumed that it can be done, but the liquid refrigerant that is condensed and liquefied at the lowest temperature (37 ℃) of the two types of high and low liquid refrigerants that are condensed and liquefied in the primary and secondary condensers (302a) (302b) is an expansion valve It is pointed out as a problem that the regret of not being able to improve the cooling performance of the evaporator 306 as a means of supplying it to 305 still remains.

Prior Art: Patent Registration No. 10-1429070 (2014. 08. 12. Notice) Prior Art-1: Registered Patent Publication No. 10-350303 (Announced on January 17, 2022)

The present invention has been proposed to solve the various problems appearing in the prior art and prior art-1,2 as described above, and temporarily stores the low-temperature primary condensed liquid refrigerant condensed and liquefied in the primary condenser of the refrigeration cycle system in a receiver. The liquid refrigerant stored in the receiver is supplied to the secondary condenser to further improve the cooling performance of the evaporator by supplying the secondary condensed liquid refrigerant condensed and liquefied at a lower temperature to the expansion valve. In addition, the secondary condensation liquid refrigerant corresponding to some 20 to 30% of the total ratio of 100% of the liquid refrigerant condensed and liquefied at a lower temperature in the secondary condenser is introduced into the receiver, so that the liquid refrigerant stored in the receiver It was invented with the aim of providing a refrigeration cycle system capable of reducing the temperature of

The present invention is a means for pursuing the above object,

A compressor provided in the middle of the refrigerant circulation line, a primary condenser for converting the high-temperature and high-pressure gaseous refrigerant discharged after being compressed to a high-temperature and high-pressure in the compressor into a high-temperature, equal-pressure liquid, and a high-temperature and high-pressure condenser that is condensed and liquefied in the primary condenser and discharged. A receiver for temporarily storing the liquid refrigerant in the receiver, a refrigerant flow-increasing pump for pumping the liquid refrigerant stored in the receiver and supplying it to the expansion valve, and a misty refrigerant rapidly expanding in the expansion valve An evaporator that absorbs ambient heat and converts it into a low-temperature gaseous state in the process of evaporating by a heat exchange action that takes away heat; A secondary condenser configured to filter out the liquid refrigerant contained in the liquid refrigerant and form a liquid separator for sending the gaseous refrigerant to the compressor, condensing and liquefying the liquid refrigerant pumped by the refrigerant flow-increasing pump and storing it in a receiver In the refrigeration cycle system configured to include,

The outlet of the receiver is connected to the inlet line of the refrigerant flow booster pump, and the outlet line of the refrigerant flow booster pump is configured to be connected to the inlet line of the secondary condenser, while the outlet line of the secondary condenser is connected to the expansion valve. It is connected to the inlet line, and means for connecting the outlet line of the secondary condenser and the receiver to a bypass line, configured to supply the liquid refrigerant condensed and liquefied in the secondary condenser to the expansion valve and the receiver, respectively, Some of the liquid refrigerant corresponding to a ratio of 20 to 30% of the total ratio of 100% of the liquid refrigerant discharged to the outlet line after being condensed and liquefied in the secondary condenser by the control operation of the flow control valve installed in the pass line While being stored in the receiver through the line, most of the liquid refrigerant corresponding to 70 to 80% of the total ratio of 100% of the liquid refrigerant discharged to the outlet line of the secondary condenser can be supplied to the expansion valve so that the evaporator It is characterized in that it is configured to improve the cooling performance of.

In addition, the flow control valve installed in the bypass line passes some of the liquid refrigerant corresponding to 20 to 30% of the total ratio of 100% of the liquid refrigerant discharged to the outlet line of the secondary condenser to be stored in the receiver. And, it is characterized in that most of the liquid refrigerant corresponding to 70 to 80% of the liquid refrigerant discharged through the outlet line is configured to be transferred to the expansion valve.

In addition, the flow control valve installed in the bypass line is a means for controlling a portion of the liquid refrigerant discharged through the outlet line of the secondary condenser to flow into the receiver, and in the receiver, the primary condenser liquefied in the primary condenser. It is characterized in that the condensed liquid refrigerant and the secondary condensed liquid refrigerant condensed and liquefied in the secondary condenser are stored and mixed in the receiver to reduce the temperature of the liquid refrigerant stored in the receiver.

According to the present invention, the primary condensed liquid refrigerant discharged from the primary condenser for primarily condensing and liquefying the high-temperature and high-pressure gaseous refrigerant compressed in the compressor and the liquid refrigerant stored in the receiver are pumped with a refrigerant flow-increasing pump to produce secondary It is a method of storing and mixing the secondary condensed liquid refrigerant sent to the condenser, condensed and liquefied in the secondary condenser and discharged together in the receiver, and has an effect of reducing the temperature of the liquid refrigerant stored in the receiver. By transferring the liquid refrigerant discharged from the secondary condenser, which is condensed and liquefied at a lower temperature than the stored liquid refrigerant, to the expansion valve, there is an advantage of providing an improved effect that can further improve the cooling performance of the evaporator.

1 is a circuit diagram in which primary and secondary condensers are separated in a refrigeration cycle system according to a first embodiment of the present invention.
2 is a circuit configuration diagram in which primary and secondary condensers of a refrigeration cycle system according to a second embodiment of the present invention are arranged side by side with a condenser body.
3 is a circuit configuration diagram in which a liquid separator is inserted into the receiver of the refrigeration cycle system according to the first embodiment of the present invention and coupled to the receiver in a dual structure.
4 is a circuit configuration diagram in which a liquid separator is inserted into the receiver of the refrigeration cycle system according to the second embodiment of the present invention and coupled to the receiver in a dual structure.
5 is a circuit diagram of a prior art refrigeration cycle system;
6 is a circuit diagram of a refrigeration cycle system of Prior Art-1.
7 is a circuit diagram of a refrigeration cycle system of Prior Art-2.

A detailed description of a method for reducing the temperature of a refrigerant liquid in a receiver and a method for improving evaporator cooling performance of a refrigeration cycle system according to the present invention is described in detail with reference to the accompanying drawings.

1 is a circuit diagram of the refrigerating cycle system of the first embodiment of the present invention, the refrigerating cycle is an outlet line 11 of the compressor 1 provided in the middle of the refrigerant circulation line 10 configured 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 configured to be connected to the inlet 31 of the receiver 3 has been

The outlet 32 of the receiver 3 of the first embodiment is connected to the inlet line 41 of the refrigerant flow booster pump 4, and the outlet line 42 of the refrigerant flow booster pump 4 is a secondary It is configured to be connected to the inlet line 23 of the condenser 2b, and the outlet line 24 of the secondary condenser 2b is configured to be connected to the inlet line 51 of the expansion valve 5.

The outlet line 52 of the expansion valve 5 of the first embodiment is connected to the inlet line 61 of the evaporator 6, and the outlet line 62 of the evaporator 6 is the inlet of the liquid separator 7. 71, and the outlet 72 of the liquid separator 7 is configured to be connected to the inlet line 12 of the compressor 1, and is rapidly expanded in the expansion valve 5 to form an evaporator 6 The misty refrigerant supplied to the evaporator 6 is configured to further improve the cooling performance of the evaporator 6 as the temperature of the liquid refrigerant flowing into the inlet line 51 of the expansion valve 5 is lower.

Therefore, the feature of the refrigeration cycle of the first embodiment of the present invention is that the bypass line 8 connected to the outlet line 24 of the secondary condenser 2b is connected to the receiver 3, and the secondary condenser In the configuration to supply the low-temperature liquid refrigerant condensed and liquefied in (2b) to the expansion valve 5 and simultaneously supplied and stored in the receiver 3, the low-temperature liquid refrigerant condensed and liquefied in the secondary condenser 2b Some of the liquid refrigerant corresponding to 20 to 30% of the total ratio of 100% of the liquid refrigerant is stored in the receiver (3), while the low-temperature liquid refrigerant 100 condensed and liquefied in the secondary condenser (2b) Most of the liquid refrigerant corresponding to 70 to 80% of the total ratio of % is characterized in that it is configured to be supplied to the expansion valve (5).

To this end, only a part of the liquid refrigerant corresponding to 20 to 30% of the total ratio of 100% of the liquid refrigerant discharged to the outlet line 24 of the secondary condenser 2b is provided in the bypass line 8. The liquid phase discharged to the outlet line 24 of the secondary condenser 2b by detecting the flow rate or pressure of the liquid refrigerant discharged from the secondary condenser 2b so as to be stored in the receiver 3 through the A portion of the liquid refrigerant corresponding to 20 to 30% of the total ratio of 100% of the refrigerant is flowed into the receiver (3) and stored, while the liquid phase corresponding to 70 to 80% of the total ratio of 100% of the liquid refrigerant A flow control valve (9) is installed that has a control function to control supply and transfer of most of the refrigerant to the expansion valve (5).

In addition, the liquid refrigerant stored in the receiver 3 is pumped to the outlet 32 of the receiver 3 by the pumping operation of the refrigerant flow booster pump 4 to pump the liquid refrigerant stored in the receiver 3. An extended suction end 32a extending while being immersed in the water surface w is formed.

In addition, a one-way check valve 81 for blocking the reverse flow of the refrigerant stored in the receiver 3 is installed in the bypass circuit 8, and the one-way check valve 81 is a refrigerant flow increase pressure pump ( When 4) does not operate, it has a function of blocking the reverse flow of the gaseous refrigerant stored in the receiver (3).

Figure 2 shows a circuit diagram of the refrigeration cycle system of the second embodiment of the present invention, the refrigeration cycle system of the second embodiment includes the primary and secondary condensers 2a in one condenser body 2 (2b) is different from the first embodiment in that it is configured in parallel, but the other configurations are largely the same. Therefore, in describing the refrigeration cycle system of the second embodiment, a detailed description of the same or similar configuration as that of the first embodiment will be omitted, but the connection configuration of the refrigerant circulation circuit 10 for forming a closed circuit will be briefly described. The explanation is as follows.

In addition, the refrigeration cycle system of the second embodiment will be described using the same names and reference numerals for the same components as compared to the first embodiment.

That is, the refrigeration cycle system of the second embodiment is configured by juxtaposing primary and secondary condensers 2a and 2b inside one condenser body 2, and the outlet line 11 of the compressor 1 is It is 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.

In addition, the outlet 32 of the receiver 3 of the second embodiment is connected to the inlet line 41 of the refrigerant flow-increase pump 4, and the outlet line 42 of the refrigerant flow-increase pump 4 is The refrigerant circulation line ( 10) is configured to form.

In addition, a bypass line 8 for supplying a part of the liquid refrigerant to the receiver 3 is connected to the outlet line 24 of the secondary condenser 2b of the second embodiment, and the bypass line 8 ) is provided with a flow control valve 9 for controlling a portion of the liquid refrigerant discharged from the secondary condenser 2b to be supplied to the receiver 3.

In addition, a one-way check valve 81 for preventing a reverse flow of the refrigerant stored in the receiver 3 is installed in the bypass line 8 of the second embodiment.

Like the first embodiment, the flow control valve 9 of the second embodiment detects the flow rate or pressure of the liquid refrigerant discharged to the outlet line 24 of the secondary condenser 2b, and the outlet line 24 ) to supply some of the liquid refrigerant corresponding to 20 to 30% of the total ratio of 100% of the liquid refrigerant discharged to the receiver (3), while 70 to 80% of the total ratio of 100% of the liquid refrigerant Most of the liquid refrigerant corresponding to the ratio has a control function so that it can be supplied to the expansion valve (5).

In addition, the expansion valve 5 of the second embodiment rapidly expands the liquid refrigerant discharged and transported from the secondary condenser 2b and supplies it to the evaporator 6, whereupon the inlet line 51 of the expansion valve 5 As the temperature of the inflowing liquid refrigerant decreases, the refrigerant in a fog state rapidly expanded by the expansion valve 5 is configured to improve the cooling performance of the evaporator 6, and the refrigerant supplied to the evaporator 6 The refrigerant in the fog state absorbs heat in the process of evaporating by taking away heat through a heat exchange action with an external heat exchange medium (air, water, etc.) and cools the attention.

In addition, the refrigerant in a fog state rapidly expanded in the expansion valve 5 improves the cooling performance of the evaporator 6 as the temperature of the liquid refrigerant flowing into the inlet line 51 of the expansion valve 5 decreases. characterizes it.

Therefore, the refrigeration cycle of the second embodiment of the present invention is also configured to connect to the receiver 3 through the bypass line 8 connected to the outlet line 24 of the secondary condenser 2b, and the secondary condenser 2b ), the low-temperature liquid refrigerant condensed and liquefied in the secondary condenser (2b) is configured to be supplied to the expansion valve (5) and also supplied and stored in the receiver (3). A part of the liquid refrigerant corresponding to a ratio of 20 to 30% of the total ratio of 100% is configured to be stored in the receiver (3), while the low-temperature liquid refrigerant 100 condensed and liquefied in the secondary condenser (2b) It is configured to supply most of the liquid refrigerant corresponding to 70-80% of the total ratio of % to the expansion valve (5).

3 and 4 show circuit diagrams of the refrigerating cycle systems of the third and fourth embodiments of the present invention, the refrigeration cycles of the third and fourth embodiments include a liquid separator inside the receiver 3 As a configuration in which (7) is inserted, the liquid separator (7) absorbs heat from the surroundings in the evaporator (6) and evaporates low-temperature gaseous refrigerant flowing into the inlet (71) and stored in the receiver (3) Each component and Since the connection configuration is almost the same, a detailed description thereof will be omitted.

On the other hand, in the refrigerant circulation line 10 of each of the refrigeration cycle systems of the first to fourth embodiments, an inlet line 41 is formed between the inlet line 41 and the outlet line 42 of the refrigerant flow rate boosting pump 4 A pressure measurement sensor 4a is provided to compare and measure whether the pressure of the liquid refrigerant flowing into the outlet line 42 and the pressure of the liquid refrigerant flowing out to the outlet line 42 are introduced and discharged at a set pressure, and the secondary condenser ( Between the outlet line 24 of 2b) and the inlet line 51 of the expansion valve 5, a dryer 11 for filtering out foreign substances contained in the liquid refrigerant circulating in the refrigerant circulation line 10 and an input signal Solenoid valves 12 and the like that are automatically opened and closed according to are installed.

Since the action and effect of each of the refrigeration cycles of the first to fourth embodiments of the present invention configured as described above are the same, the specific description of the refrigeration cycle of the first embodiment is as follows, and the second to fourth embodiments of the present invention The refrigeration cycle will be briefly described.

First, if the refrigeration cycle of the first embodiment is described, the high-temperature and high-pressure gaseous refrigerant compressed to a high temperature and high pressure in the compressor 1 provided in the middle of the refrigerant circulation line 10 is discharged through the outlet line 11 It flows into the primary condenser 2a through the inlet line 21 of the primary condenser 2a and is condensed and liquefied by heat exchange with an external heat exchange medium (air, water, etc.) and discharged through the outlet line 22, The primary condensed liquid refrigerant discharged through the outlet line 22 is temporarily stored in the receiver 3 through the inlet 31 of the receiver 3.

The liquid refrigerant stored in the receiver 3 is sucked into the extended suction end 32a by the pumping operation of the refrigerant flow intermediate pressure pump 4, and passes through the outlet 32 to the inlet line of the refrigerant flow booster pump 4 ( 41) is pumped and discharged to the outlet line 42, and the liquid refrigerant discharged to the outlet line 42 of the refrigerant flow-increasing pump 4 passes through the inlet line 23 of the secondary condenser 2b. It flows into the secondary condenser (2b) and is condensed and liquefied by heat exchange with an external heat exchange medium (air, water, etc.). At this time, the liquid refrigerant condensed in the primary condenser (2b) is temporarily stored in the receiver (3). It becomes a state of being condensed and liquefied at a temperature lower than the temperature of the liquid refrigerant, and the specific reason for this will be described later.

The low-temperature liquid refrigerant secondarily condensed and liquefied in the secondary condenser 2b is discharged through the outlet line 24 and introduced into the expansion valve 5 through the inlet line 51 of the expansion valve 5. In this way, the liquid refrigerant that condenses and liquefies the liquid refrigerant stored in the receiver 3 at a lower temperature in the secondary condenser 2b flows into the inlet line 51 of the expansion valve 5, so eventually The liquid refrigerant condensed in the secondary condenser (2b) is condensed and liquefied at a lower temperature than the liquid refrigerant stored and mixed in the receiver (3), and flows into the inlet line 51 of the expansion valve (5) to rapidly expand. The liquid refrigerant that is condensed at a lower temperature and introduced through the inlet line 51 of the expansion valve 5 is rapidly expanded by the expansion valve 5 and changed into a refrigerant in a fog state, which is stored in the evaporator 6. Accordingly, the expansion valve 5 is secondarily condensed by the secondary condenser 2b in which the liquid refrigerant stored in the receiver 3 is condensed once more, and the liquid refrigerant liquefied at a lower temperature. By supplying the refrigerant in the rapidly expanded fog state to the evaporator 6, the evaporator 6 greatly improves the cooling performance.

Therefore, as described above, the secondary condenser (2b) supplies the refrigerant in a fog state that rapidly expands in the expansion valve (5) into which the liquid refrigerant condensed and liquefied at a lower temperature than the liquid refrigerant stored in the receiver (3) flows. The evaporator 6 to be received can expect the effect of further improving the cooling performance of taking away heat through heat exchange action with an external heat exchange medium (air, water, etc.).

As described above, the cooling performance of the evaporator 6 supplied with the refrigerant in the form of a mist that rapidly expands in the expansion valve 5 into which the liquid refrigerant that is secondarily condensed in the secondary condenser 2b and condensed and liquefied at a lower temperature is introduced. is further improved, and the low-temperature, low-pressure gaseous refrigerant that evaporates after taking away heat from the heat exchange action in the evaporator (6) flows into the inlet (71) of the liquid separator (7) and passes through the outlet (71) to the compressor (1). ) is introduced into the inlet line 12, compressed to high temperature and high pressure in the compressor 1, and discharged to the outlet line 11 is repeated repeatedly.

An example of an experiment conducted by applying the refrigeration cycle of the first embodiment configured as described above to the summer season will be described as follows.

When the outdoor temperature in the summer season is 35 ℃, the gaseous refrigerant compressed to high temperature and high pressure in the compressor (1) flows into the inlet line (21) of the primary condenser (2a), condenses and liquefies through heat exchange with the external heat exchange medium, and Assuming that the liquid refrigerant discharged through the line 22 is condensed and liquefied at a temperature of 45° C. and then introduced into the inlet 31 of the receiver 3 and stored therein, the liquid refrigerant stored in the receiver 3 is While maintaining the temperature of 45 ° C., the liquid refrigerant discharged to the outlet 32 by the pumping operation of the refrigerant flow booster pump 4 is connected to the outlet line 42 of the refrigerant flow booster pump 4. It flows into the secondary condenser (2b) through the inlet line (23) of the primary condenser (2b) and is condensed and liquefied by the action of exchanging heat with an external heat exchange medium. The liquid refrigerant is condensed and liquefied at a temperature of 37 ° C., which is lower than the liquid refrigerant temperature (45 ° C.) when introduced into the inlet line 23, and discharged to the outlet line 24. At this time, the above-mentioned outlet line 24 37 ℃ liquid refrigerant discharged to the bypass line (8) by the flow control valve (9) installed in the outlet line 24 of the secondary condenser (2b) 100% of the liquid refrigerant discharged to the total ratio Some of the liquid refrigerant corresponding to 20 to 30% of the liquid refrigerant flows into the receiver (3) through the bypass line (8) and is stored, and most of the liquid refrigerant corresponding to 70 to 80% is transferred to the expansion valve (5). can be assumed to be supplied.

Therefore, the liquid refrigerant stored in the receiver 3 includes a 45° C. liquid refrigerant that is first condensed and liquefied in the primary condenser 2a and a 37° C. liquid refrigerant that is secondarily condensed and liquefied in the secondary condenser 2b. It is in a state of being mixed and stored, and accordingly, the liquid refrigerant mixed and stored in the receiver 3 is a state in which the liquid refrigerant at 41 ° C., which is the difference between the liquid refrigerant at 45 ° C. and the liquid refrigerant at 37 ° C., is stored. The liquid refrigerant at 41°C stored in the receiver 3 is transferred to the secondary condenser 2b by the pumping operation of the refrigerant flow-increasing pump 4. The liquid refrigerant is liquefied at a temperature lower than 41℃ at 37℃ in the condensation process by the heat exchange action with the external heat exchange medium, and 70 to 80% of the total ratio of 100% of the liquid refrigerant at 37℃ liquefied at a lower temperature. Since most of the liquid refrigerant of % is transferred to the inlet line 51 of the expansion valve 5, the expansion valve 5 is a liquid phase of 37 ° C that is condensed and liquefied at a lower temperature in the secondary condenser 2b. Since the refrigerant in a fog state in which the refrigerant is rapidly expanded is supplied to the evaporator (6), the liquid refrigerant condensed and liquefied at a lower temperature (37° C.) by the secondary condenser (2b) is discharged from the expansion valve (5). It can be assumed that the evaporator 6 supplied with the refrigerant in a rapidly expanding fog state exhibits an effect of greatly improving cooling performance of absorbing heat from the surroundings to cool the surroundings.

Next, in the case of the refrigeration cycle of the second embodiment, the primary and secondary condensers (2a) (2b) show a difference from the first embodiment only in that the primary and secondary condensers (2a) (2b) are arranged side by side in one condenser body (2), and the primary condenser The liquid refrigerant condensed and liquefied in (2a) and the liquid refrigerant condensed and liquefied in the secondary condenser (2b) are stored together in the receiver (3) and mixed, and the temperature of the liquid refrigerant stored in the receiver (3) The means for reducing the and the configuration of supplying most of the liquid refrigerant, which is 70 to 80% of the total ratio of the liquid refrigerant condensed and liquefied at a lower temperature in the secondary condenser (2b) to the expansion valve (5), etc. It can be judged that it exhibits the same function and effect as the first embodiment.

In addition, in the refrigeration cycles of the third and fourth embodiments, the liquid separator 7 into which the gaseous refrigerant evaporated by absorbing ambient heat in the evaporator 6 flows is inserted into the receiver 3. The only difference from the first and second embodiments is that the liquid refrigerant condensed and liquefied in the primary condenser 2a and the liquid refrigerant condensed and liquefied in the secondary condenser 2b are stored and mixed together in the receiver 3. The ratio of 70 to 80% of the total ratio of 100% of the liquid refrigerant condensed and liquefied at a lower temperature in the means for reducing the temperature of the liquid refrigerant stored in the receiver (3) and the secondary condenser (2b) Most of the liquid refrigerant corresponding to is supplied to the expansion valve 5, and the liquid refrigerant corresponding to a ratio of 20 to 30% is supplied to the receiver 3, so that the liquid stored in the receiver 3 Since the means for reducing the temperature of the refrigerant exhibits the same effect as those of the first and second embodiments described above, a detailed description thereof will be omitted.

As described above, the present invention, as in the first to fourth embodiments, the high temperature and high pressure condensed and liquefied in the primary condenser 2a for condensing the high-temperature and high-pressure gaseous refrigerant discharged after being compressed at high temperature and high pressure in the compressor 1 ( 45 ℃) liquid refrigerant and low temperature (37 ℃) liquid refrigerant that is condensed and liquefied in the secondary condenser (2b) are stored together in the receiver (3) and mixed, so that the liquid refrigerant stored in the receiver (3) It has the effect of reducing the temperature. In particular, most of the liquid refrigerant that is condensed and liquefied at a low temperature (37 ° C) in the secondary condenser (2b) is transported to the expansion valve (5) and rapidly expanded. By configuring to supply to (6), the effect of improving the cooling performance of the evaporator (6) can be expected to be greatly improved.

When the present invention is applied to refrigeration cycle systems installed in various industrial sites, it is possible to reduce the required power of the compressor and greatly improve the cooling performance of the evaporator, so that air conditioners and refrigeration and It has the effect of increasing the cooling performance of evaporators such as refrigerators, and also saves fuel energy such as oil or gas and electric energy when the present invention is applied to automobiles, trains, ships, and airplanes. The effect of greatly improving the cooling performance of the evaporator can be expected.

1: compressor 10: refrigerant circulation line
2: condensation main body 2a: primary condenser
2b: secondary condenser 3: receiver
4: refrigerant flow rate boosting pump 5: expansion valve
6: evaporator 7: liquid separator
8: bypass line 81: one-way check valve
9: flow control valve

Claims (3)

A compressor 1 provided in the middle of the refrigerant circulation line 10, a primary condenser 2a for converting the high-temperature and high-pressure gaseous refrigerant discharged after being compressed to a high-temperature and high-pressure in the compressor into a high-temperature, equal-pressure liquid, and the primary condenser 2a. A receiver (3) for temporarily storing high-temperature and high-pressure liquid refrigerant condensed and liquefied in the condenser and discharged, and a refrigerant flow-increase pump (4) for pumping and supplying the liquid refrigerant stored in the receiver to the expansion valve (5) An evaporator ( 6) and a liquid separator (7) that filters out the liquid refrigerant contained in the low-temperature gaseous refrigerant that evaporates by taking heat from the surroundings by heat exchange action with an external heat exchange medium in the evaporator and sends the gaseous refrigerant to the compressor (1) It is configured to form, and is configured to include a secondary condenser (2b) configured to condense and liquefy the liquid refrigerant pumped by the refrigerant flow-increasing pump (4) and store it in the receiver (3) Refrigeration cycle system in
The outlet 32 of the receiver 3 is connected to the inlet line 41 of the refrigerant flow booster pump 4, and the outlet line 42 of the refrigerant flow booster pump 4 is connected to the secondary condenser 2b. While configured to be connected to the inlet line 23 of the secondary condenser 2b, the outlet line 24 is connected to the inlet line 51 of the expansion valve 5, and the secondary condenser 2b The outlet line 24 and the receiver 3 are connected to the bypass line 8, and the liquid refrigerant condensed and liquefied in the secondary condenser 2b is transferred to the expansion valve 5 and the receiver 3, respectively. The liquid refrigerant 100 condensed and liquefied in the secondary condenser (2b) and discharged to the outlet line (24) by the control operation of the flow control valve (9) installed in the bypass line (8). The liquid refrigerant corresponding to a ratio of 20 to 30% of the total ratio of % is stored in the receiver 3 through the bypass line 8, while the outlet line 24 of the secondary condenser 2b Characterized in that it is configured to improve the cooling performance of the evaporator (6) by configuring the liquid refrigerant corresponding to 70 to 80% of the total ratio of 100% of the liquid refrigerant discharged to the expansion valve (5) A method for improving evaporator cooling performance using a method for reducing the temperature of a refrigerant liquid in a receiver of a refrigeration cycle system. delete delete

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