KR101610252B1 - Energy saving freezer and refrigerator with reduced dryness - Google Patents

Energy saving freezer and refrigerator with reduced dryness Download PDF

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Publication number
KR101610252B1
KR101610252B1 KR1020150074765A KR20150074765A KR101610252B1 KR 101610252 B1 KR101610252 B1 KR 101610252B1 KR 1020150074765 A KR1020150074765 A KR 1020150074765A KR 20150074765 A KR20150074765 A KR 20150074765A KR 101610252 B1 KR101610252 B1 KR 101610252B1
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South Korea
Prior art keywords
refrigerant
temperature
heat exchanger
main
branch
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KR1020150074765A
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Korean (ko)
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정문환
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장현수
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F25B41/043—
    • F25B41/062—
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0417—Refrigeration circuit bypassing means for the subcooler
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers

Abstract

An object of the present invention is to provide an energy saving type freezing / refrigerating apparatus having a reduced degree of drying, and an object of the present invention is to provide an energy saving type freezing and refrigerating apparatus which is provided with a heat exchanger and is supercooled in a high temperature and high pressure liquid state, And to provide an energy-saving refrigerator or refrigerator which does not require a separate liquid separator by reducing the liquid component of the refrigerant flowing into the compressor.
In the refrigeration or refrigeration apparatus of the present invention, a main electromagnet valve for controlling the flow of the refrigerant is provided on the main refrigerant tube between the receiver and the expansion valve, and the main refrigerant tube in both directions is bypassed And a high-temperature high-pressure liquid refrigerant flowing through the main refrigerant pipe according to the temperature measurement flows through the branch refrigerant pipe through the inside of the heat exchanger provided in the main refrigerant pipe between the evaporator and the compressor. Temperature low-pressure state refrigerant passing through the evaporator, and then the main-electric valve is returned to the main refrigerant tube past the high-temperature and low-pressure state refrigerant. By this, the high-temperature and high-pressure state supercooled liquid refrigerant whose drying degree is reduced is supplied to the expansion valve, Is supplied to the compressor, the energy saving type refrigeration and refrigeration apparatus having a reduced drying degree.

Description

(Energy saving freezer and refrigerator with reduced dryness)

The present invention relates to an energy-saving freezing / refrigerating apparatus that reduces the drying degree. More specifically, the present invention relates to an energy-saving freezing / refrigerating apparatus that supercooled a high-temperature high-pressure liquid refrigerant passing through a condenser and then supplies the refrigerant to an expansion valve to increase the freezing capacity Thereby improving energy efficiency.

In the refrigeration cycle of the refrigeration or refrigeration apparatus, the refrigerant passing through the evaporator is compressed by the compressor to be gasified at high temperature and high pressure and then sent to the condenser through the refrigerant circuit. Then, the refrigerant is sent to the expansion valve through the refrigerant circuit, After low-pressure liquidization, the refrigerant is sent to the evaporator through the refrigerant circuit, and then the low-temperature low-pressure gasification cycle is repeated in the evaporator.

The evaporator is a heat exchanger installed in the freezer (or refrigerating chamber) to lower the internal temperature by exchanging heat with indoor air.

FIG. 4 is a view illustrating a conventional refrigeration apparatus, and FIG. 5 is a view illustrating a Mollier diagram of a conventional refrigeration apparatus.

Referring to FIG. 4, refrigerant in a low-temperature low-pressure liquid state passing through the expansion valve 400 is heat-exchanged with the air inside the freezer 500 while passing through the evaporator 100 to freeze the indoor space Temperature low-pressure gaseous refrigerant.

Thereafter, the liquid contained in the low-temperature low-pressure gas is separated through the liquid separator 210 and is supplied to the compressor 200 in a gaseous state. At this time, the refrigerant in the separated liquid state is evaporated again and gasified and then supplied to the compressor.

The low-temperature low-pressure gaseous refrigerant supplied to the compressor 200 is compressed to be a high-temperature high-pressure gaseous refrigerant.

The compressed high temperature and high pressure gaseous refrigerant undergoes latent heat change in the high temperature and high pressure liquid state in the condenser 300 after the oil is separated through the oil separator (not shown) And is stored in a liquid state as a refrigerant.

The high-temperature, high-pressure liquid refrigerant passed through the receiver then passes through the expansion valve 400 and becomes a low-temperature, low-pressure liquid refrigerant. Then, the refrigerant undergoes heat exchange with the air in the freezer room through the evaporator 100 as described above The refrigerating cycle which is changed into the low-temperature low-pressure gaseous refrigerant is repeated.

The thermodynamic state of the refrigerant in each refrigeration cycle of the conventional refrigerating apparatus constructed as above is shown in the Mollier diagram of FIG. 5 based on pressure and enthalpy. It can be seen that the conventional freezing cycle proceeds from a to b to C to D to E to a in the drawing. In the figure, the enthalpy at the point converted to the compression process during the evaporation process is 150 Kcal / kg, the enthalpy at the point converted to the condensation process during the compression process is 163 Kcal / kg, Lt; RTI ID = 0.0 > 115 Kcal / kg. ≪ / RTI > Accordingly, the refrigeration force and the coefficient of performance of the refrigeration apparatus having the refrigeration cycle according to the conventional embodiment are as follows.

Refrigeration force (Kcal / kg) = 150 - 115 = 35

The coefficient of performance (Cop) = 150 - 115/163 - 150 = 2.69

Dryness (x) = 0.3 (gas component 30%, liquid component 70%)

4 and 5, it can be seen that the time of the evaporation process showing the refrigeration capability is shifted to the right side of the saturated liquid line much as in the conventional cooling system, and the refrigeration cycle of the existing refrigerator / It is possible to increase the amount of flash gas generated by passing the high-temperature and high-pressure liquid refrigerant through the expansion valve without passing the supercooling degree. As a result, the freezing force is reduced, There is a structural disadvantage that it has various adverse effects such as degradation of the coefficient of performance due to carbonization and lowering of hydraulic pressure, liquid hammer ring due to evaporator reboiler, compressor burnout, and the like. Therefore, a solution to this problem is very necessary.

Korean Patent Registration No. 10-0796283 (Jan. 14, 2008) Korean Patent Registration No. 10-0948584 (Mar. 12, 2010) Korean Patent Registration No. 10-0155652 (July 16, 1998) Korean Utility Model Publication No. 20-1999-0040762 (Dec. 6, 1999)

In order to solve the above problems, an object of the present invention is to provide a heat exchanger, which is configured to supercool the high-temperature high-pressure liquid refrigerant and supply the expanded refrigerant to the expansion valve to increase the refrigerant volume by reducing the degree of drying, And to provide an energy-saving freezing or refrigeration apparatus that does not require a separate liquid separator by reducing the liquid component of the refrigerant being introduced.

Another object of the present invention is to provide a refrigerating or refrigerating apparatus in which the refrigerant tube passing through the interior of the heat exchanger has a tilted structure to increase heat exchange efficiency.

According to an aspect of the present invention, there is provided a refrigeration system including a main refrigerant pipe and a refrigerant pipe, the main refrigerant pipe being connected to the main refrigerant pipe through a freezing cycle including an evaporator, a compressor, a condenser, Or refrigerator,

Wherein a main refrigerant pipe for controlling the flow of the refrigerant is provided on the main refrigerant pipe between the receiver and the expansion valve and a branched refrigerant pipe bypassing the main refrigerant pipe in both lateral directions is formed between the main refrigerant pipe and the compressor, Temperature high-pressure liquid refrigerant flowing through the main refrigerant pipe flows through the branch refrigerant pipe in accordance with the temperature measurement, and performs heat exchange with the low-temperature and low-pressure state refrigerant passing through the evaporator Temperature low-pressure low-pressure gas refrigerant in which the high-temperature and high-pressure supercooling liquid refrigerant, which has reduced the degree of drying, is supplied to the expansion valve and the liquid component evaporated, is supplied to the compressor Saving refrigerator / freezer device with reduced energy consumption.

According to a preferred embodiment of the present invention, the branch refrigerant tube is configured to control the flow of the refrigerant passing through the inside of the heat exchanger by providing an auxiliary solenoid valve at one point of the branch refrigerant tube at the front end of the heat exchanger, A check valve is provided at one point to control the flow of the refrigerant backward through the expansion valve to the heat exchanger.

In a preferred embodiment of the present invention, the branch refrigerant tube at the downstream end of the heat exchanger may be provided with a first temperature sensor at the front end of the check valve to measure the supercooling degree of the refrigerant before being supplied to the expansion valve by temperature measurement.

In a preferred embodiment, the second temperature sensor is installed in the heat exchanger, and the refrigerant discharged from the evaporator flows along the main refrigerant pipe, flows into the heat exchanger, and then measures the temperature of the heat exchanged state with the refrigerant flowing through the branch refrigerant pipe So as to measure the superheating degree of the intake gas.

In a preferred embodiment of the present invention, the branch exchanger is provided with a branch refrigerant tube to which a refrigerant of a high temperature and a high pressure is supplied is inclined from the bottom of one end of the main body of the heat exchanger toward the top of the other end, In the state where the low-pressure gaseous refrigerant is first introduced, the lower space of the branch refrigerant tube passes through a large area, and then the lower space is gradually exhausted through a narrow area to increase the heat exchange efficiency.

In a preferred embodiment, the branch refrigerant tube installed in the inner section of the heat exchanger may be formed in a coil shape to increase the thermal contact area.

In a preferred embodiment, a plurality of heat exchange fins are formed on the outer surface of the branch refrigerant tube passing through the heat exchanger so as to be protruded and arranged so that more heat exchange occurs.

In a preferred embodiment, a plurality of heat exchange fins are formed on the inner surface of the branch refrigerant tube passing through the inside of the heat exchanger so as to protrude from the inner surface of the branch refrigerant tube, thereby increasing the resistance and reducing the flow rate of the refrigerant.

In a preferred embodiment, a plurality of heat exchange fins may be formed on both the outer and inner surfaces of the branch refrigerant tube located inside the heat exchanger so as to protrude and arrange the heat exchanger.

According to the present invention having the above-described features, a heat exchanger is installed between an evaporator and a compressor in a general refrigeration cycle structure, and a high-temperature and high-pressure liquid refrigerant condensed and liquefied in a condenser is exchanged with a low-temperature and low-pressure refrigerant gas passing through an evaporator, It is advantageous to improve the overall refrigeration capacity by reducing the amount of flash gas generated due to decrease in the degree of drying at the time of passage and increasing the refrigeration power in the evaporator.

In addition, since the refrigerant flowing into the compressor is contained in the refrigerant, it is not necessary to provide a separate liquid separator while preventing the liquid hammer ring, and thus it is possible to save the manufacturing cost and increase the temperature of the suction gas, It is a useful invention having an advantage that various adverse effects such as deterioration, carbonization and decomposition of a compressor can be prevented, and it is a highly anticipated use in industry.

1 is a view illustrating a refrigeration apparatus according to an embodiment of the present invention,
FIG. 2 is a view showing a structure of a heat exchanger according to an embodiment of the present invention,
FIG. 3 is an exemplary view showing a Mollier diagram according to an embodiment of the present invention,
FIG. 4 is a view showing a conventional refrigeration apparatus,
FIG. 5 is an exemplary view showing a Mollier diagram of a conventional refrigerator in general.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. In the following description of the present invention, a detailed description of known functions and configurations incorporated herein will be omitted when it may make the subject matter of the present invention rather unclear.

FIG. 1 is a view illustrating a refrigeration apparatus according to an embodiment of the present invention, and FIG. 2 is a view illustrating a structure of a heat exchanger according to an embodiment of the present invention.

The basic structure of the refrigeration apparatus of the present invention as shown in the figure includes an evaporator 100, a compressor 200, a condenser 300, a receiver 310 and an expansion valve 400 and is connected by a main refrigerant pipe And is a refrigeration or refrigeration apparatus equipped with a freezing or refrigeration cycle of a refrigerant circulating in a closed state during normal operation. The refrigerator or the refrigerator according to the present invention may be constructed by varying the size of the freezer or the refrigerator in which the evaporator is installed depending on the purpose.

The refrigerant circulating in the refrigerating or refrigerating apparatus having the above-described configuration passes through the expansion valve 400 and the refrigerant in the low-temperature low-pressure liquid state passes through the evaporator 100 and is heat-exchanged with the air inside the freezer (or the refrigerator) Temperature low-pressure gas is supplied to the compressor 200. In the compressor, the supplied low-temperature low-pressure gaseous refrigerant is compressed to a high-temperature high-pressure gaseous state The compressed high-temperature and high-pressure gas is separated from the oil via a oil separator (not shown), is latched at high temperature and high pressure in the condenser 300, stored in the liquid state in the receiver 310, The refrigerant passed through the expansion valve 400 becomes a low-temperature low-pressure liquid. Thereafter, the freezing cycle is repeated.

The refrigerator or refrigerator having the above-described general refrigeration or refrigeration cycle further includes the following components. The larger the refrigerator or the freezer having such a configuration, the more energy saving effect is obtained .

In particular, the present invention differs from a general refrigeration or refrigeration apparatus in that a liquid separator is omitted and a refrigerant introduced into an expansion valve is supplied in a supercooled state to be supplied to the evaporator in a state of reduced drying, The low-temperature low-pressure gaseous refrigerant supplied to the low-temperature low-pressure gaseous refrigerant is evaporated and then supplied. For this purpose, the present invention is characterized in that a main electromagnet valve 1 for controlling the flow of the refrigerant is installed on the main refrigerant pipe 7 between the receiver (310) and the expansion valve (400) And a branch refrigerant pipe 8 is formed in the main refrigerant pipe 7 so as to bypass the main refrigerant pipe 7 in the both sides of the main refrigerant pipe 7. The branched refrigerant pipe is connected to the heat exchanger provided in the main refrigerant pipe 7 between the evaporator 100 and the compressor 200 (2). At this time, the heat-exchanged refrigerant is recovered by the main refrigerant pipe 7 passing through the kettle valve and supplied to the expansion valve.

Further, the branch refrigerant pipe (8) is arranged to control the flow of the refrigerant passing through the inside of the heat exchanger by providing an auxiliary solenoid valve (3) at one point of the branch refrigerant tube at the front end of the heat exchanger (2) 1), a check valve 4 is provided at one point of the downstream branch refrigerant pipe to control the flow of the refrigerant backward through the expansion valve to the heat exchanger.

Further, a first temperature sensor 5 is provided in the branch refrigerant tube at the downstream end of the heat exchanger 2 to measure the supercooling degree of the refrigerant before being supplied to the expansion valve by temperature measurement .

In addition, a second temperature sensor 6 is installed inside the heat exchanger 2 so that the refrigerant discharged from the evaporator flows along the main refrigerant pipe, flows into the heat exchanger, and is then heat-exchanged with the refrigerant flowing through the branch refrigerant pipe So as to measure the superheating degree of the intake gas.

The main valve 1 and the auxiliary solenoid valve 3 are opened or closed by a control unit not shown according to the temperatures of the first temperature sensor 5 and the second temperature sensor 6 to measure the supercooling degree and the superheating degree And is opened / closed to flow the refrigerant flow to the main refrigerant pipe (7) or the branch refrigerant pipe (8) according to the result.

The heat exchanger 2 is connected to the branch refrigerant pipe 8 in the inner section where the refrigerant flowing in the branch refrigerant pipe 8 and the refrigerant flowing into the heat exchanger main body are heat- (8) may be formed in a coil shape to increase the thermal contact area.

Further, the heat exchanger (2) is connected to the branch refrigerant pipe (8) through a branch refrigerant pipe (8) in which the refrigerant flowing in the branch refrigerant pipe (8) and the refrigerant flowing into the heat exchanger main body The tube (8) is inclined from the bottom of one end of the main body of the heat exchanger to the top of the other end so that the refrigerant in the high temperature and high pressure state flows from the lower side to the upper side of the other side in an inclined form while passing through the heat exchanger.

With the above configuration, in a state where the low-temperature low-pressure gaseous refrigerant discharged from the main refrigerant tube 7 flowing into the space inside the main body of the heat exchanger 2 is first introduced, the space below the branch refrigerant tube 8 And then the lower space is gradually discharged through a narrow area.

In addition, when the gas component and the liquid component are mixed in the above-described manner, the refrigerant having the gas component and the liquid component is separated from each other by the density difference in the wide space and the liquid component is separated from the upper portion by the gas component. The liquid refrigerant absorbs more heat by the contact with the branch refrigerant pipe through which the liquid refrigerant flows, and the evaporation efficiency is increased.

Therefore, in the heat exchanger having the above structure, the low-temperature low-pressure liquid refrigerant contained in the low-temperature low-pressure gaseous refrigerant flows to the rear end along the lower surface of the heat exchanger due to the difference in weight, The low-temperature and low-pressure state gas refrigerant is discharged as it is gasified by increasing the area of heat exchange with the heat at the high temperature in contact with the tube 8. As a result, the amount of the liquid state refrigerant supplied to the compressor is reduced and the problems such as the liquid hammer ring are prevented. At this time, the branch refrigerant pipe (8) installed in the inner section of the heat exchanger (2) may be formed in a coil shape to increase the thermal contact area.

In the meantime, the present invention is not limited to the above-described structure in which the branch refrigerant tube is inclined, but also a plurality of heat exchange fins 81 are formed so as to protrude from the outer surface of the branch refrigerant tube located inside the heat exchanger, .

And a plurality of heat exchangers are provided on the inner surface of the branch refrigerant tube located inside the heat exchanger so that more heat is supplied to the low-temperature and low-pressure refrigerant by reducing the speed of the high-temperature and high-pressure liquid refrigerant supplied through the branch refrigerant tube, The pins 81 may be formed so as to be protruded to increase the resistance to reduce the flow rate of the refrigerant, thereby further increasing the heat exchange.

In addition, a plurality of heat exchange fins 81 may be formed on both the outer and inner surfaces of the branch refrigerant tube located inside the heat exchanger so as to protrude and arrange the heat exchanger.

The operation through the control flow according to the phase change of the refrigerant flowing in the refrigerating or freezing apparatus having the above-described structure of the present invention will be described below.

In the normal operation in which the first operation is started, the kettle valve is opened, the auxiliary solenoid valve is closed, and the refrigerant is operated through the main refrigerant tube in a usual freezing or refrigeration cycle.

During such normal operation, the temperature of the first temperature sensor 5 provided in the branch refrigerant pipe 8 is measured to measure the supercooling degree of the refrigerant supplied to the expansion valve 400, or the temperature of the second temperature sensor 6 The degree of superheat of the intake gas flowing into the compressor 200 is measured. If it is determined that the degree of superheat of the intake gas is low even if the supercooling degree is low, the kettle valve 1 is closed by the control of the control unit The valve 3 is opened to allow the flow of the liquid refrigerant in the high temperature and high pressure state that has flowed from the receiver 110 to the expansion valve 400 through the main refrigerant pipe 7 to the main refrigerant pipe connected to the compressor through the branch refrigerant pipe 8 Exchanges heat via the heat exchanger 2 provided in the expansion valve 7 and then supplies the refrigerant to the main refrigerant pipe 7 at the upstream end of the expansion valve to provide a supercooling degree to the refrigerant supplied to the expansion valve 400, ) Reduce the amount of gas generated to reduce the dryness. If the degree of drying of the refrigerant supplied to the expansion valve is reduced, the refrigerating capacity of the evaporator is increased. Also, the coefficient of performance is increased and the amount of compression is decreased, resulting in remarkable energy saving effect.

On the other hand, some of the low-temperature low-pressure liquid refrigerant contained in the low-temperature and low-pressure gas refrigerant which can not evaporate in the evaporator 100 is supplied to the heat exchanger 2 provided in the main refrigerant pipe 7 between the evaporator and the compressor, Temperature high-pressure liquid refrigerant in the branch refrigerant tube is heated to be transformed into a low-temperature and low-pressure state gas.

Accordingly, the low-temperature and low-pressure liquid refrigerant, which is partially mixed with the low-temperature and low-pressure gas refrigerant supplied to the compressor in the refrigerating or refrigerating apparatus of the conventional structure, is an incompressible fluid, which causes the liquid hamming phenomenon in the compressor. Will not appear.

That is, according to the present invention, the liquid refrigerant of high temperature and high pressure is exchanged between the liquid refrigerant of high temperature and high pressure and the liquid refrigerant of low temperature and low pressure through the heat exchanger, so that the liquid refrigerant of high temperature and high pressure provides the supercooling degree and the low temperature and low pressure liquid refrigerant is evaporated to exhibit high efficiency of refrigerating power and high efficiency .

The thermodynamic state of the refrigerant in each refrigeration cycle of the refrigerating apparatus of the present invention according to FIGS. 1 and 2 is shown in the Mollier diagram of FIG. 3 based on pressure and enthalpy.

It can be seen that the refrigeration cycle of the present invention proceeds from G to b to c to d to F to G in the figure. In the figure, the enthalpy at the point converted to the compression process during the evaporation process is 150 Kcal / kg, the enthalpy at the point converted to the condensation process during the compression process is 163 Kcal / kg, Lt; RTI ID = 0.0 > 110 Kcal / kg. ≪ / RTI > Particularly, the point F is a temperature corresponding to the temperature of the branch refrigerant pipe past the check valve of FIG. In contrast, the conventional temperature at the point E is about 40 占 폚. The refrigeration force and the coefficient of performance of the refrigeration apparatus having the refrigeration cycle according to an embodiment of the present invention are as follows.

Refrigeration force (Kcal / kg) = 150 - 110 = 40

The coefficient of performance (Cop) = 150 - 110/163 - 150 = 3.1

Dryness (x) = 0.2 (gas component 20%, liquid component 80%)

As described above, the refrigeration power of the present invention is 40 Kcal / kg, which is higher than the conventional 35 Kcal / kg. That is, when comparing the conventional freezing / refrigerating apparatus shown in FIG. 5 with the freezing / refrigerating apparatus of the present invention,

Refrigeration force (Kcal / kg) = 40/35 x 100 = 114.3%

(Cop) = 3.1 / 2.69 x 100 = 115.3%

Drying rate = 0.2 /0.3 × 100 = 66.6%. Thus, it can be seen that the improvement of the refrigeration power and the coefficient of performance is a remarkable increase in energy efficiency in the refrigeration field.

It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined in the appended claims and their equivalents. Of course, such modifications are within the scope of the claims.

(1): kettle valve (2): heat exchanger
(3): Auxiliary solenoid valve (4): Check valve
(5): first temperature sensor (6): second temperature sensor
(7): Main refrigerant tube (8): Branch refrigerant tube
(81): Heat exchange fin (100): Evaporator
(200): compressor (300): condenser
(310): Receiver (400): Expansion valve
(500): Freezer

Claims (9)

A refrigeration cycle in which the refrigerant flowing through the main refrigerant pipe is circulated through the evaporator, the compressor, the condenser, the receiver, and the expansion valve is provided to provide a kettle valve for controlling the flow of the refrigerant on the main refrigerant tube between the receiver and the expansion valve And a branch refrigerant tube bypassing the main refrigerant tubes in both lateral directions with the main electric valve interposed therebetween so as to pass through the inside of the heat exchanger provided in the main refrigerant tube between the evaporator and the compressor, Temperature high-pressure liquid refrigerant flowing through the pipe through the branch refrigerant pipe, heat-exchanges the refrigerant with the low-temperature low-pressure state refrigerant passing through the evaporator, and returns the kettle valve to the main refrigerant pipe through the high-temperature high-pressure state supercooling liquid refrigerant Is supplied to the expansion valve, and the low-temperature low-pressure state gas refrigerant in which the liquid component is evaporated is supplied to the compressor Or in the cold storage device,
The branch refrigerant tube is configured to control the flow of refrigerant passing through the heat exchanger by providing an auxiliary solenoid valve at a point of the branch refrigerant tube at the front end of the heat exchanger, So that the refrigerant flows back toward the heat exchanger through the expansion valve,
A first temperature sensor is provided at a front end of the check valve in the branch refrigerant tube passing through the heat exchanger to measure a supercooling degree of the refrigerant before being supplied to the expansion valve by temperature measurement, A sensor is installed and refrigerant discharged from the evaporator flows along the main refrigerant pipe, flows into the heat exchanger, and measures the temperature in a state of exchanging heat with the refrigerant flowing through the branch refrigerant pipe, thereby measuring the superheating degree of the suction gas.
The branch refrigerant tube to which the refrigerant of the high temperature and high pressure state is supplied is inclined from the bottom of one end of the main body of the heat exchanger to the upper side of the other end so that the refrigerant of high temperature and high pressure flows to the upper side of the other side while passing through the heat exchanger The low-temperature low-pressure gaseous refrigerant discharged from the main refrigerant tube flowing into the internal space of the heat exchanger main body flows through the wide space at the lower side of the branch refrigerant tube in the first introduced state, The liquid component separates and flows downward, and gradually passes through the narrow space of the lower space, and the liquid component of the lower part is heat-exchanged with the branch refrigerant pipe flowing in the high-temperature and high-pressure liquid refrigerant flowing at one side of the heat exchanger, And then discharging the energy-saving refrigerating / refrigeration unit .
delete delete delete delete The method according to claim 1,
Wherein a branch refrigerant tube installed in an inner section of the heat exchanger is formed in a coil shape to increase a thermal contact area.
The method according to claim 1,
Wherein a plurality of heat exchange fins are formed so as to protrude from the outer surface of the branch refrigerant tube passing through the inside of the heat exchanger so that more heat exchange occurs.
The method according to claim 1,
Wherein a plurality of heat exchange fins are protruded and arranged on an inner surface of the branch refrigerant pipe passing through the inside of the heat exchanger, thereby increasing the resistance and reducing the flow rate of the refrigerant, thereby causing more heat exchange. · Refrigeration equipment.
The method according to claim 1,
Wherein a plurality of heat exchange fins are formed on both outer and inner surfaces of the branch refrigerant tube located inside the heat exchanger so as to be protruded and arranged to perform heat exchange in a complex manner.
KR1020150074765A 2015-05-28 2015-05-28 Energy saving freezer and refrigerator with reduced dryness KR101610252B1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113030165A (en) * 2021-03-09 2021-06-25 西安交通大学 Rectangular experiment section for high-temperature gas isothermal wall surface cooling experiment

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Publication number Priority date Publication date Assignee Title
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