KR20100006351U - refrigeration system - Google Patents

Abstract

The present invention relates to a refrigeration system, the purpose of which is to increase the evaporation pressure of the freezer, an apparatus having an ejector 10, a separator 20, a distributor 40 in addition to the existing refrigeration cycle, evaporator The low-temperature low-pressure refrigerant gas at the outlet of the evaporator 3 is introduced into the suction part 12 of the ejector 10. At this time, the high pressure liquid refrigerant at the outlet of the condenser 2 is introduced into the nozzle part 11 of the ejector 10 at high speed through the expansion valve 5 and then mixed with the refrigerant vapor of the suction part 12 in the mixing part 13. After the pressure is increased in the diffuser unit 14, the refrigerant gas in the separator 20 is introduced into the compressor 1, so that the refrigerant specific volume of the compressor 1 is decreased, thereby increasing the cooling capacity by increasing the refrigerant circulation amount, and the liquid refrigerant is After passing through the decompression device (4) is decompressed and introduced to the evaporator (3).

Therefore, since the evaporation pressure of the evaporator (3) is boosted after passing through the ejector (10) in the summer and winter, the heating capacity is increased in the winter, the cooling capacity is increased in the summer, and the compression ratio (high pressure / low pressure) of the compressor (1) is increased. Pressure) to reduce power consumption, and to reduce the discharge temperature of the compressor (1) outlet can prevent the burner of the compressor (1).

In addition, it is to provide a refrigeration system to prevent the rapid deterioration of the heating capacity that occurs in the cold climate of the winter, as in Korea, to promote the spread of the heat pump, and to improve the performance and power saving with a high-efficiency refrigeration system.

Refrigerator, Condenser, Evaporator, Compressor, Heat Exchanger, Ejector, Separator

Description

Refrigeration system {refrigeration system}

The present invention relates to a refrigerating system, which relates to a device for boosting the evaporator pressure of an evaporator in an ejector and drawing it into a compressor, and is driven only by a high-pressure refrigerant liquid of a refrigerating cycle itself, not a pressurization device such as a separate compressor or booster pump. The present invention relates to an apparatus for improving cooling capacity in summer and winter and reducing power consumption of a compressor.

A typical refrigeration system includes a compressor for compressing a refrigerant gas at a high temperature and high pressure, and a refrigerant compressed in the compressor is a cooling fan (in the case of water cooling, water, not air, other coolant or equipment is used, and air is described. A condenser condensed into the liquid phase by heat dissipation by air blowing, an expansion valve for expanding the liquid refrigerant in the high temperature and high pressure state condensed in the condenser into a low-pressure gas phase refrigerant by throttling action, and a refrigerant expanded in the expansion valve. The air blown by the blower by using the latent heat of evaporation of the refrigerant, depending on the type or structure of the liquid, milk or other freezing device depending on the object to be cooled. It is a refrigerant circulation cycle consisting of an evaporator that cools and returns the refrigerant gas to the compressor.

This refrigeration system continuously changes state from gas to liquid and liquid to gas during the refrigeration cycle.

However, in the conventional refrigeration system as described above, however, when the outside temperature decreases, the evaporation pressure decreases, causing a sudden drop in heating capacity, the required power increases due to the increase in the compression ratio, and the damage of the compressor due to the increase in the discharge temperature of the compressor. There is a problem that occurs.

An object of the present invention is a device to press the evaporation pressure of the refrigeration cycle in the summer and winter without an external device (compressor, booster) to enter the compressor, to increase the cooling capacity in the summer, to prevent the deterioration of heating performance in the winter, It is to provide a refrigeration system that prevents the compressor burn out by preventing excessive rise in the compression ratio and the discharge temperature of the compressor outlet.

The present invention is an apparatus having an ejector 10, a separator 20, a distributor 40 in addition to the existing refrigeration cycle, the low-temperature low-pressure refrigerant gas at the outlet of the evaporator 3, the inlet 12 of the ejector 10 ). At this time, the high pressure liquid refrigerant at the outlet of the condenser 2 is introduced through the expansion valve 5 into the nozzle part 11 of the ejector 10, and then mixed with the refrigerant vapor of the suction part 12 at the mixing part 13. Since the refrigerant gas is introduced into the compressor 1 in the separator 20 after being boosted by the diffuser unit 14, the refrigerant specific volume of the compressor 1 is decreased, thereby increasing the cooling capacity by increasing the refrigerant circulation amount, and the liquid refrigerant is a pressure reducing device. After passing through (4), the pressure is reduced and drawn into the evaporator (3, evaporator).

Therefore, since the evaporation pressure of the evaporator 3 is elevated after passing through the ejector 10 in the summer and winter, the heating capacity is increased in the winter season, the cooling capacity is increased in the summer season, and the compression ratio of the compressor 1 (high pressure pressure / Low pressure pressure) to reduce the power required by reducing the discharge temperature of the compressor (1) is characterized in that to prevent the burner of the compressor (1).

The present invention is to increase the pressure of the evaporator to be introduced into the compressor, to reduce the power consumption of the compressor, to prevent the burner of the compressor, to improve the cooling and heating capacity to reduce the cooling power of the summer to sleep, It greatly reduces the heating room power in winter, and has the effect of coping with the heating heat source of fossil fuel with high efficiency heat pump device.

A compressor for compressing and discharging the refrigerant gas to a high temperature and high pressure state, a condenser for condensing the refrigerant compressed in the compressor to a liquid phase, and an expansion for expanding the high temperature and high pressure liquid refrigerant condensed in the condenser into a low pressure liquid refrigerant Evaporator and refrigerant for evaporating the low temperature and low pressure gaseous refrigerant gas into the ejector while achieving a freezing effect by heat exchange with the object to be cooled by using the latent heat of evaporation of the valve and the refrigerant expanded by the expansion valve. In the refrigeration system comprising an ejector for ejecting the refrigerant of the evaporator by injecting a high pressure to the high pressure and a separator for separating the refrigerant liquid and steam,

A condenser system (300) consisting of the compressor (1), the condenser (2) and the control valve (35);

An evaporator system 400 including the evaporator 3 which is operated by cold air and cold water;

The ejector system 10 is operated by the ejector 10, the distributor 40, the separator 20, and the expansion valves 4 and 5.

The condenser system 300, the evaporator system 400, and the ejector system 500 may be implemented in one form or in combination.

Features and advantages of the present invention will become more apparent from the detailed description of the preferred embodiments based on the accompanying drawings.

Prior to this, the terms or words used in this specification and claims should not be construed as being limited to their usual or dictionary meanings, and the inventors will properly interpret the concept of terms in order to best explain their own design. Based on the principle that it can be defined, it should be interpreted as meaning and concept corresponding to the technical idea of the present invention.

<First Embodiment>

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

1 is a cycle diagram showing a schematic diagram of a heat pump system according to the present invention.

Reference numeral 1 denotes a compressor, which is used to suck refrigerant gas and compress it at high temperature and high pressure to discharge it, and according to the purpose of use, various types of reciprocating type, crank type, swash plate type, wobble plate type, rotary type, scroll type, etc. Compressors of the type may be applied.

The discharge line of the compressor 1 is connected to the condenser 2.

Although not shown in detail, the condenser 2 is a plurality of tubes forming a predetermined flow path by connecting an inlet header, an outlet header, and an inlet / outlet header when the air heat exchanger is connected to each other, and the Conventional forms of corrugated heat transfer fins laminated between the tubes can be applied. Therefore, the air blown by the cooling fan passes through the heat transfer fins between the tubes. In this process, the refrigerant flowing in the condenser loses heat to the blower air, thereby performing the condensation of the refrigerant.

In addition, when the condenser is a water heat exchanger, a plate heat exchanger, a cell-and-tube heat exchanger, a spiral tube and a double tube heat exchanger, and the like, loses heat to water in the heat exchanger, and thus loses heat, thereby condensing the refrigerant.

The high pressure liquid refrigerant at the outlet of the condenser 2 is reduced in the expansion valve 5 and introduced into the ejector 10.

The ejector 10 is composed of a nozzle unit 11, the inlet 12, the mixing unit 13 and the diffuser 14, the high-pressure liquid refrigerant in the nozzle unit when the high-speed injection of the evaporator (3, evaporator) ) After the gaseous refrigerant at the outlet is sucked by the venturi action, the liquid refrigerant of the nozzle unit 11 and the gaseous refrigerant of the inlet unit 12 are mixed in the mixing unit 13, and then the dynamic pressure is converted into a static pressure in the diffuser 14. In the process, the pressure of the evaporator 3 rises from P1 to P1 'as shown in FIG.

At this time, the outlet of the ejector 10 is connected to the distributor 40, the outlet of the distributor 40 is connected to the top and bottom of the separator 20, respectively, the separator 20 is the outlet of the distributor 40 The refrigerant branched from the side is introduced into the upper and lower portions, respectively, and the refrigerant liquid in the gaseous state in the upper portion of the separator 20 is introduced into the compressor 1, and the refrigerant introduced into the lower portion of the separator 20 in the distributor 40. Has a structure in which the nozzle 50 is injected into the diffuser 51, and attracts the coolant liquid at the lower part of the separator 20 to the inside of the diffuser 51 when the nozzle 50 sprays the refrigerant. 4) After the pressure is reduced through the evaporator (2) is introduced into the inlet 12 of the ejector (10).

In addition, a hot gas control valve 35 is attached to a pipe connecting the expansion valve 4 and the evaporator 3 by branching the high temperature and high pressure refrigerant gas at the outlet of the compressor 1.

Although not shown in detail here, the distributor 40 may be manufactured in various forms such as a T-shape (T) and a Wei-shape (Y), and the nozzle 50 and the diffuser 51 at the bottom of the separator 20 may be formed. As shown in Fig. 7, the nozzle 50 is inserted into the diffuser 51, or the nozzle 50 is a tube having a smaller diameter, and the diffuser 51 has a larger diameter than the nozzle 50. Can be replaced with a tube

On the other hand, the evaporator (3) which achieves a freezing effect by exchanging the object to be cooled with the refrigerant by using the latent heat of evaporation by evaporating the refrigerant flowing from the expansion valve (4) has an inlet header and an outlet header, By connecting the outlet headers so that they are in communication with each other, a conventional type having a plurality of tubes forming a predetermined flow path and corgate-type heat transfer fins stacked between the tubes can be applied. Therefore, the air blown by the cooling fan passes through the heat transfer fins between the tubes, and in this process, the refrigerant flowing in the evaporator 3 takes the temperature (heat amount) of the blowing air, and thus the refrigerant evaporates.

At the inlet end of the evaporator 3, an expansion valve 4 for supplying the liquid refrigerant in the high temperature and high pressure state to the refrigerant in the low pressure state by the throttling action to supply the evaporator 3 so that the evaporation is easily performed is provided. Is installed. Although not shown in detail, the expansion valves 4 and 5 are internally equalized and capillary which regulates the trajectory of the high-pressure refrigerant passage through the pressure transfer rod by the expansion displacement of the diaphragm according to the temperature inside the temperature reduction chamber. Thermostatic expansion valves, such as TEV, capillary type, throttle, orifice and electronic expansion valves, etc., which are generally externally compressed to control the trajectory of the high-pressure refrigerant flow path by the expansion displacement of the diaphragm through the tube, can be used in various forms. .

In addition, the flow of the refrigerant in FIG. 1 is compressed into a refrigerant gas of high temperature and high pressure in the compressor 1, and decompressed after passing through the expansion valve 5 from the gas phase to the liquid phase after heat exchange in the condenser 2, and thus the evaporator 10 in the ejector 10 After mixing with the refrigerant of 3) is passed through the diffuser (14), through the distributor (40) and introduced into the separator (20), the liquid refrigerant is decompressed through the nozzle 50 and the diffuser (51) at the expansion valve (4) In the evaporator 3, the refrigerant liquid is evaporated into the refrigerant vapor and introduced into the suction unit 12 of the ejector 10, and the refrigerant gas at the top of the separator 20 is introduced into the compressor 1.

In addition, since the expansion valve 4 has a smaller pressure difference than the expansion valve 5, the expansion valve 4 may be replaced with a capillary tube or an ear tube.

Referring to the operation of the present invention, the refrigerant gas of the high temperature and high pressure of the compressor 1 is introduced into the condenser (2, condenser).

The refrigerant flowing into the condenser (2) is a gaseous state, and after being heat-exchanged with the outdoor air, the refrigerant is condensed and supercooled into a liquid refrigerant, and the refrigerant at the outlet of the condenser (2) is decompressed at the expansion valve (5) to eject the ejector ( 10) After being injected into the nozzle 11, it is sprayed at high speed by the nozzle unit 11, and the refrigerant gas of the inlet unit 12 is introduced into the mixing unit 13 by a venturi action to cool the nozzle unit 11 and the refrigerant of the inlet unit 12. Are mixed, and the dynamic pressure of the refrigerant in the diffuser 14 is converted into a static pressure and introduced into the distributor 40.

The refrigerant at the outlet of the distributor 40 is introduced into the upper and lower portions of the separator 20, the gaseous refrigerant in the upper portion of the separator 20 is introduced into the compressor 1, and the separator 20 in the distributor 40. The refrigerant introduced into the lower part of the nozzle is injected from the nozzle 50 into the diffuser 51 to draw the refrigerant liquid in the lower part of the separator 20 into the diffuser 51 to be decompressed at the expansion valve 4, and then the evaporator. In (3), after the heat exchange with the indoor air is converted into the gas phase in the liquid phase is drawn into the inlet 12 of the ejector 10.

The hot gas control valve 35 on the bypass pipe connecting the expansion valve 4 and the evaporator 3 by branching the refrigerant gas of the high temperature and high pressure at the outlet of the compressor 1, defrosts the evaporator 3 at the same time. For the sake of simplicity, the method is the same as that of a general hot gas defrosting method, and incidentally, when the pressure drop of the evaporator 3 or the supply of the refrigerant to the inside of the evaporator 3 is insufficient, the refrigerant can be smoothly supplied.

In addition, the deflection 35 and the bypass pipe may be omitted in the use of household air conditioners and industrial cooling systems, and may be used as a defrost heat source in a system utilizing a heat source of the four season condenser 2 such as a hot water supply system. .

The operation according to the first embodiment will be described with reference to FIG. 2 for the refrigeration cycle.

Fig. 2 is a Moliere diagram (pressure-enthalpy) schematically showing a refrigerating cycle according to the first embodiment, where point “a” is a high temperature and high pressure refrigerant vapor at the outlet of the compressor 1 in the outside air in the condenser 2 (condenser). And condensed by heat exchange with the supercooled liquid refrigerant ”b”, the pressure is reduced from the expansion valve 5 to the state “c”, and is ejected at high speed from the nozzle part 11 of the ejector 10 to the state ”d”. In (12), the incoming refrigerant state "k" is mixed in the mixing section 13 into the state "e", and as the state "f" in the diffuser 14, the dynamic pressure of the refrigerant is static pressure. Vapor phase pressure is increased from P1 → P1 ', through the distributor 40, the gaseous refrigerant state “g” is introduced into the compressor 1 in the separator 20, and the liquid refrigerant is supplied to the lower nozzle ( 50) and pass through the decompression state ”j” at the expansion valve 4 at state “h” at diffuser 51 3) is introduced into the inlet 12 of the diffuser 10 in the state "k" by evaporation from the liquid phase to the gaseous phase after heat exchange with indoor air.

In FIG. 2, since the suction pressure P1 '> P1 of the compressor 1 and the inlet specific volume Vg <Vk of the compressor 1, the cooling capacity in the refrigeration cycle = refrigerant circulation amount (refrigerant circulation amount = compressor exclusion volume / specific volume) x unit If the unit cooling capacity is constant as the cooling amount (cooling capacity of 1 kg of refrigerant = i1-i3 '), the cooling capacity is proportional to the refrigerant circulation amount, which is inversely proportional to the specific volume since the exclusion volume of the compressor 1 is constant.

Therefore, since the specific volume of the state "g" is smaller than the state "k", the state "g" point increases the cooling capacity at the pressure P1 ', and the work amount W of the compressor 1 = m (refrigerant circulation amount) xw (compressor inlet and outlet) Unit work), w (unit work) is (i2-i1 ') <(i2-i1), so state “g” is less power consumption of compressor 1 than state “k” and cooling capacity is increased, In heating mode, the heating capacity (cooling capacity + compressor volume) is determined by the cooling capacity of the evaporator (2, condenser) .However, under cold conditions like Korea, heating capacity increases when the outside air temperature decreases, Since the heating capacity decreases rapidly, it is the biggest obstacle to the dissemination of the heat pump as a heating source for winter.

However, in the refrigerating system of the present invention, when the outside temperature decreases, the evaporation pressure P1 of the condenser (2, evaporator) is increased to P1 'by using the ejector 10, thereby increasing heating capacity.

In addition, since the discharge temperature of the refrigerant state "a" at the outlet of the compressor 1 is lower than the suction state "g" of the compressor 1 is "k", it prevents carbonization of the refrigeration oil and prevents burnout of the coil of the compressor motor. can do.

  Example 2

In the first embodiment described above, the nozzle 50 and the diffuser 51 are employed inside the separator 20. In the second embodiment, the Y-type distributor 41 is employed as shown in Figs.

The configuration of the other components in the refrigeration cycle apparatus may be the same as those of the embodiment.

3 is a schematic diagram of a refrigerating cycle of the second embodiment, and FIG. 8 is a cross-sectional view when the Y-type distributor 41 is implemented with an external nozzle 52 and a diffuser 53.

The operation according to FIG. 3 introduces a refrigerant gas of high temperature and high pressure from the compressor 1 into the condenser 2.

The refrigerant flowing into the condenser 2 is a gaseous state, and after being heat exchanged with outdoor air, the refrigerant is condensed and subcooled into a liquid refrigerant, and the refrigerant at the outlet of the condenser 2 is reduced in the expansion valve 5 to eject the ejector 10. After being introduced into the nozzle section 11, the nozzle section 11 is sprayed at a high speed to introduce the refrigerant gas from the inlet section 12 into the mixing section 13 by a venturi action to mix the refrigerant in the nozzle section 11 with the refrigerant in the inlet section 12. In the diffuser 14, the dynamic pressure of the refrigerant is converted into a static pressure and introduced into the distributor 40.

The refrigerant at the outlet of the distributor 40 is introduced into the upper part of the separator 20 and the distributor 41, and the gaseous refrigerant in the upper part of the separator 20 is introduced into the compressor 1, and in the distributor 40. The refrigerant introduced into the distributor (41) is depressurized in the expansion valve (4) by attracting the refrigerant liquid at the lower part of the separator (20), and then exchanged with the indoor air in the evaporator (3), and then converted from the liquid phase to the gas phase, and then the ejector (10). Is drawn into the suction portion 12 of the.

The schematic implementation in the Moliere diagram (pressure-enthalpy) of the refrigeration cycle is the same as in Example 1.

In this refrigeration cycle, the distributor 41 of the liquid refrigerant supply line at the front end of the expansion valve 4 may be implemented with a nozzle 52 and a diffuser 53 as shown in FIG. 8.

At this time, the refrigeration cycle is a structure in which the refrigerant at the outlet of the distributor 40 is introduced into the nozzle 52 and the refrigerant liquid at the lower part of the separator 20 is introduced into the diffuser 53. At the time of injection, the refrigerant around the diffuser 53 is attracted and introduced into the expansion valve 4.

Example 3

In the first embodiment described above, the distributor 40 is employed at the outlet of the diffuser 14 of the ejector 10. However, in the third embodiment, as shown in FIG. 4, a branch is formed between the condenser 2 and the ejector 10. After entering the nozzle 50, it was ejected at a high speed.

The configuration of the other components in the refrigeration cycle apparatus may be the same as those of the first embodiment.

4 is a schematic diagram of a refrigeration cycle of a third embodiment.

The operation of the refrigeration system according to FIG. 4 introduces the refrigerant gas of the high temperature and high pressure of the compressor 1 into the condenser 2 (condenser).

The refrigerant flowing into the condenser (2) is a gaseous state, and after being heat-exchanged with the outdoor air, the refrigerant is condensed and supercooled into a liquid refrigerant, and the refrigerant at the outlet of the condenser (2) is decompressed at the expansion valve (5) to eject the ejector ( 10) After being injected into the nozzle 11, it is sprayed at high speed by the nozzle unit 11, and the refrigerant gas of the inlet unit 12 is introduced into the mixing unit 13 by a venturi action to cool the nozzle unit 11 and the refrigerant of the inlet unit 12. The mixture is mixed, and the dynamic pressure of the refrigerant in the diffuser 14 is converted into a static pressure and introduced into the upper portion of the separator 20.

At this time, the gaseous refrigerant in the upper part of the separator 20 is introduced into the compressor (1), the high-pressure refrigerant liquid branched between the condenser (2) and the ejector (10) of the diffuser (51) in the nozzle (50) Injected into the refrigerant liquid in the lower part of the separator (20) to the inside of the diffuser (51) to reduce the pressure in the expansion valve (4), after the heat exchange with the room air in the evaporator (3) after converting from the liquid phase to the gas phase and ejector ( It enters into the suction part 12 of 10).

In this refrigeration cycle, the driving refrigerant of the nozzle 50 is directly branched from the high pressure side and injected into the diffuser 51, so that the refrigerant supplied to the evaporator 3 via the expansion valve 4 is more reliably supplied. The state of the refrigerant at the inlet of (4) has the advantage of supplying a completely liquid refrigerant, the high-pressure refrigerant branch position can achieve a predetermined purpose, just before and after the expansion valve (5).

Example 4

In the first embodiment described above, the nozzle 50, the diffuser 51 and the distributor 40 are employed inside the separator 20. In the fourth embodiment, as shown in FIGS. 5 and 8, the Y-type distributor 41 ) And the high pressure refrigerant was branched between the condenser (2) and the ejector (10).

The configuration of the other components in the refrigeration cycle apparatus may be the same as those of the first embodiment.

5 is a schematic diagram of a refrigerating cycle of the fourth embodiment, and FIG. 8 is a cross-sectional view when the Y-type distributor 41 is implemented with an external nozzle 52 and a diffuser 53.

The operation according to FIG. 5 introduces a refrigerant gas of a high temperature and high pressure of the compressor 1 into the condenser 2 (condenser).

The refrigerant flowing into the condenser (2) is a gaseous state, and after being heat-exchanged with the outdoor air, the refrigerant is condensed and supercooled into a liquid refrigerant, and the refrigerant at the outlet of the condenser (2) is decompressed at the expansion valve (5) to eject the ejector ( 10) After being injected into the nozzle 11, it is sprayed at high speed by the nozzle unit 11, and the refrigerant gas of the inlet unit 12 is introduced into the mixing unit 13 by a venturi action to cool the nozzle unit 11 and the refrigerant of the inlet unit 12. Are mixed, and the dynamic pressure of the refrigerant in the diffuser 14 is converted into a static pressure and introduced into the separator 20.

The gaseous refrigerant in the upper part of the separator 20 is introduced into the compressor 1, and the high-pressure refrigerant liquid branched between the condenser 2 and the ejector 10 is introduced into the distributor 41 and then separated by a high-speed jet separator. The refrigerant liquid in the lower part of 20) is attracted to the inlet 12 of the ejector 10 after the pressure is reduced in the expansion valve 4, the heat exchange with the indoor air in the evaporator 3, and then converted into the gas phase in the liquid phase.

In this refrigeration cycle, since the driving refrigerant of the distributor 41 is directly branched from the high pressure side and injected into the distributor 41, the refrigerant supplying the expansion valve 4 to the evaporator 3 and the evaporator more reliably is provided. The state of the refrigerant at the inlet of the expansion valve 4 has the advantage of supplying a completely liquid refrigerant, and the high-pressure refrigerant branch position can achieve a predetermined purpose just before and after the expansion valve 5.

In addition, the distributor 41 of the liquid refrigerant supply line in front of the expansion valve 4 may be implemented as a nozzle 52 and a diffuser 53 as shown in FIG.

At this time, the refrigeration cycle is a structure in which the high-pressure branched refrigerant liquid is introduced into the nozzle 52, and the refrigerant liquid in the lower portion of the separator 20 is introduced into the diffuser 53, the diffuser during the injection of the row (52) ( The refrigerant around 53) is attracted and introduced into the expansion valve 4.

 &Lt; Example 5 >

In the first embodiment described above, the nozzle 50, the diffuser 51, and the distributor 40 are employed inside the separator 20. In the fifth embodiment, the apparatus is omitted as shown in FIG. It was.

The configuration of the other components in the refrigeration cycle apparatus may be the same as those of the embodiment.

6 is a schematic diagram of a refrigeration cycle of a fifth embodiment.

The operation according to FIG. 6 introduces a refrigerant gas of high temperature and high pressure from the compressor 1 into the condenser 2.

The refrigerant flowing into the condenser 2 is a gaseous state, and after being heat exchanged with outdoor air, the refrigerant is condensed and subcooled into a liquid refrigerant, and the refrigerant at the outlet of the condenser 2 is reduced in the expansion valve 5 to eject the ejector 10. After being introduced into the nozzle section 11, the nozzle section 11 is sprayed at a high speed to introduce the refrigerant gas from the inlet section 12 into the mixing section 13 by a venturi action to mix the refrigerant in the nozzle section 11 with the refrigerant in the inlet section 12. In the diffuser 14, the dynamic pressure of the refrigerant is converted into a static pressure and introduced into the separator 20.

The gaseous refrigerant in the upper part of the separator 20 is introduced into the compressor 1, and the lower refrigerant liquid is decompressed in the expansion valve 4, and then converted into a gas phase after being heat-exchanged with indoor air in the evaporator 3. It is then introduced into the suction part 12 of the ejector 10.

The schematic implementation in the Moliere diagram (pressure-enthalpy) of the refrigeration cycle is the same as in Example 1.

In the present refrigeration cycle, the distributor 40, the nozzle 50, and the diffuser 51 of FIG. 1 are omitted.

In the above embodiments, 1, 2, 3, and 4, the expansion valve 4 may be omitted because the pressure reduction ratio is less than that of the expansion valve 5, and in this case, the pressure in the pipe through adjustment of the refrigerant pipe diameter from the separator 20 to the evaporator may be omitted. It is possible to cope with loss.

In addition, although not shown in detail in this drawing, the refrigerant gas in the upper portion of the separator 20 in the above embodiments, 1, 2, 3, 4 can be passed through the intermediate heat exchanger when the compressor 1 is introduced.

At this time, the high-pressure liquid refrigerant between the condenser 2 and the ejector 10 and the low-temperature intake gas between the compressor 1 in the separator 20, the heat exchanger in the form of a plate heat exchanger, It can be implemented in various forms such as cell antu corrosion and double tube heat exchangers.

In the above embodiments, 1, 2, 3, 4, the distributor 40, 41, nozzles 50, 52, diffusers 51, 53 and the high pressure branch between the condenser 2 and the ejector 10 are evaporator 3 As a device for more assuring the flow of the coolant, the inlet of the expansion valve 4 also has the side effect of supplying only the liquid coolant.

In the above embodiments, 1, 2, 3, 4, the system using the condenser 2 is a form for supplying four seasons to a hot water supply system and a warm air system, and the form using the evaporator 3 is a household air conditioner, industrial Chillers and ice making systems.

1 is a schematic diagram showing a refrigeration system according to the present invention

2 is a view showing a Moliere diagram of the refrigeration system according to the present invention

Figure 3 is a schematic diagram of a second embodiment of a refrigeration system according to the present invention

Figure 4 is a schematic diagram of a third embodiment of a refrigeration system according to the present invention

5 is a schematic view of a fourth embodiment of a refrigeration system according to the present invention

Figure 6 is a schematic diagram of a fifth embodiment of a refrigeration system according to the present invention

7 is a detailed cross-sectional view of the nozzle and the diffuser of the refrigeration system according to the present invention

8 is a detailed cross-sectional view of the external nozzle and the diffuser of the refrigeration system according to the present invention

Claims (11)

A compressor for compressing and discharging the refrigerant gas to a high temperature and high pressure state, a condenser for condensing the refrigerant compressed in the compressor to a liquid phase, and an expansion for expanding the high temperature and high pressure liquid refrigerant condensed in the condenser into a low pressure liquid refrigerant Evaporator and refrigerant for evaporating the low temperature and low pressure gaseous refrigerant gas into the ejector while achieving a freezing effect by heat exchange with the object to be cooled by using the latent heat of evaporation of the valve and the refrigerant expanded by the expansion valve. In the refrigeration system comprising an ejector for ejecting the refrigerant of the evaporator by injecting the refrigerant at a high pressure and a separator for separating the refrigerant liquid and steam, A condenser system (300) consisting of the compressor (1), the condenser (2), and the control valve (35); An evaporator system 400 including the evaporator 3 which is operated by cold wind and cold water; In the refrigeration system, characterized in that the ejector system 500 is operated by the ejector 10, the distributor 40, the separator 20 and the expansion valve (4, 5), the condenser system 300, the evaporator system 400 And the ejector system 500 in one form or in combination. The expansion valve (5) is installed at the rear end of the condenser (2), and the ejector (10) is installed at the rear end of the expansion valve (5). 12), the mixing section 13 and the diffuser 14, the outlet diffuser 14 of the ejector 10 is connected to the distributor 40, the outlet of the distributor 40 is the top and bottom of the separator 20 The refrigerant gas in the upper part of the separator 20 is connected to the compressor 1, and the pipe connected to the lower part of the separator 20 in the distributor 40 is expanded by the nozzle 50 and the diffuser 51. Refrigeration system characterized in that the refrigeration system is introduced into the evaporator (2), and connected to the inlet portion (12) of the evaporator outlet ejector (10). 2. The valve according to claim 1, wherein the expansion valve (4) is omitted, or a system in which a capillary tube or a two-tube tube is replaced, and the expansion valves (4, 5) are used as pressure drop means, are orifices and capillary tubes. Refrigeration system, characterized in that selected from the group of expansion valve, electronic expansion valve, refrigeration temperature expansion valve and throttle device. 3. The outlet of the distributor 40 is introduced into the upper part of the separator 20 and the distributor 41 as shown in FIG. 3, and the refrigerant gas above the separator 20 is connected to the compressor 1. There is a distributor 41 between the lower side of the 20 and the expansion valve 4, the piping of the separator 20 and the distributor 40 is connected to the inlet pipe of the distributor 41, so that the refrigerant from the expansion valve (4) Refrigerating system, characterized in that changed to be drawn into the evaporator (3). The system of claim 2, wherein the distributor 40 is omitted as shown in FIG. 4, and the high pressure pipe is branched between the condenser 2 and the ejector 10 and drawn into the nozzle 50 at the bottom of the separator 20. With the system, the outlet diffuser 14 of the ejector 10 is connected to the separator 20, the refrigerant gas above the separator 20 is connected to the compressor 1, and the nozzle 50 at the bottom of the separator 20. There is a refrigeration system, characterized in that the high-pressure branch pipe is changed to be introduced. The system of claim 2, wherein the distributor 40, the nozzle 50, and the diffuser 51 are changed to a high pressure branch and the distributor 41 as shown in FIG. 5, and the outlet diffuser 14 of the ejector 10 is a separator ( It is connected to the upper portion of the 20, the refrigerant gas in the upper part of the separator 20 is connected to the compressor (1), there is a distributor 41 between the separator 20 and the expansion valve (4), the inlet of the distributor 41 The piping is a lower pipe of the separator 20 and a high-pressure branch pipe between the condenser 2 and the ejector 10, and the distributor 41 is a refrigeration characterized in that the expansion valve 4 is changed to enter the evaporator (3). system. The system of claim 2, wherein the dispenser 40, the nozzle 50, and the diffuser 51 are omitted as shown in FIG. The outlet diffuser 14 of the ejector 10 is connected to the upper portion of the separator 20, the refrigerant gas above the separator 20 is connected to the compressor (1), the lower pipe of the separator 20 is the expansion valve (4) Refrigeration system, characterized in that changed to be led through the evaporator. The structure according to claim 2, 4, 5, 6, and 7, wherein the refrigerant gas in the upper portion of the separator 20 passes through the intermediate heat exchanger when the compressor 1 is introduced into the compressor 1, 2) It is a structure to heat exchange the liquid refrigerant of high pressure between the ejector 10 and the intake gas of low temperature between the compressor 1 in the separator 20, and in the form of a heat exchanger, a plate heat exchanger, a cell-and-tube corrosion type, Refrigeration system, characterized in that implemented in various forms, such as double tube heat exchanger. 5. The distributor 40 according to claim 2, wherein the distributor 40 is manufactured in the form of a T-shape or a Y-shape, and the nozzle 50 and the diffuser 51 in the lower part of the separator 20. ) Is a structure in which the nozzle 50 is inserted into the diffuser 51 or the refrigeration system, characterized in that the nozzle 50 and the diffuser 51 is composed of the pipe diameters. The dispenser 41 is formed in the form of a T-shape (T) or a Wei-shape (Y), and the dispenser 41 has an external nozzle 52 as shown in FIG. Refrigeration system, characterized in that the system has been changed to the shape inserted into the diffuser (53). The method according to claim 2, 4, 5, 6 and 7, wherein the refrigerant gas at the high temperature and high pressure at the outlet of the compressor 1 is branched and connected between the expansion valve 4 and the evaporator 3. A system having a hot gas control valve (35) on the bypass pipe and a bypass pipe or control valve (35) optionally omitted.

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