WO2017123042A1 - Congélateur - Google Patents

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Publication number
WO2017123042A1
WO2017123042A1 PCT/KR2017/000463 KR2017000463W WO2017123042A1 WO 2017123042 A1 WO2017123042 A1 WO 2017123042A1 KR 2017000463 W KR2017000463 W KR 2017000463W WO 2017123042 A1 WO2017123042 A1 WO 2017123042A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
refrigerant
evaporator
compressor
suction
Prior art date
Application number
PCT/KR2017/000463
Other languages
English (en)
Korean (ko)
Inventor
박용주
변강수
송현수
이상균
Original Assignee
엘지전자 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR1020160005172A external-priority patent/KR102446555B1/ko
Priority claimed from KR1020160080123A external-priority patent/KR102502289B1/ko
Application filed by 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Priority to US16/069,952 priority Critical patent/US10782048B2/en
Priority to DE112017000376.8T priority patent/DE112017000376T5/de
Publication of WO2017123042A1 publication Critical patent/WO2017123042A1/fr

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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
    • F25B31/00—Compressor arrangements
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders

Definitions

  • Embodiments of the present invention relate to a deep freezer.
  • a deep freezer is understood as a device that drives a refrigeration cycle to form a storage compartment in a cryogenic environment of -60 ° C to -80 ° C or less.
  • a low boiling point refrigerant may be used.
  • the discharge pressure of the compressor is increased, thereby reducing the reliability of the compressor.
  • two or more mixed refrigerants having different boiling points may be used in the refrigerating cycle for implementing the temperature.
  • a mixed refrigerant that does not change temperature in a quasi-equilibrium state when liquefaction or vaporization occurs between a liquid phase and a gas under a predetermined pressure that is, an azeortropic refrigerant mixture and a temperature in which the temperature is changed during the liquefaction or vaporization process
  • Non-azeortropic refrigerant mixtures are included.
  • the azeotropic mixed refrigerant exists only in a specific component ratio and exhibits thermodynamic properties such as pure substances.
  • the azeotropic mixed refrigerant may vary in evaporation pressure or temperature depending on its composition.
  • the azeotropic mixed refrigerant has a disadvantage in that it is difficult to implement a deep temperature (extreme cryogenic), it may be preferable to use the azeotropic mixed refrigerant in order to implement a deep temperature.
  • a compressor used in a deep freezer may use a commercial compressor having a large operating pressure range, that is, a high discharge pressure value.
  • the commercial compressor has a problem in that the operation noise for the deep freezer is lowered due to the large operation noise.
  • the refrigerating cycle disclosed in the prior document the refrigerant discharged from the compressor is condensed in the condenser to perform heat exchange with the evaporative refrigerant, it is configured to implement the temperature by the heat exchange.
  • the dryness of the refrigerant is increased in the process of expanding in the expansion device after the heat exchange, thereby reducing the ratio of the liquid refrigerant in the refrigerant flowing into the evaporator, thereby decreasing the cooling power.
  • Embodiments of the present invention have been proposed to solve the above problems, and an object thereof is to provide a deep freezer that can implement a desired cryogenic environment.
  • an embodiment of the present invention is to provide a deep freezer that can lower the condensation pressure of the refrigeration cycle.
  • an embodiment of the present invention is to provide a deep freezer that can reduce the noise generated in the compressor to increase the reliability of the compressor.
  • the deep-temperature freezer according to the embodiment of the present invention includes a plurality of heat exchangers installed in the suction pipe and performing heat exchange of the mixed refrigerant sucked into the compressor.
  • the heat exchanger includes a first heat exchanger, the first heat exchanger, the first heat exchanger for guiding the flow of the mixed refrigerant sucked into the compressor; And a condensation heat exchanger configured to perform heat exchange with the first suction heat exchanger and to guide the flow of the condensation pipe.
  • the length of the first suction heat exchange or the condensation heat exchange unit is characterized in that formed in the range of 3.5 ⁇ 5m.
  • the pipe diameter of the condensation heat exchange part is larger than the pipe diameter of the expansion device.
  • the pipe diameter of the condensation heat exchange part is formed within the range of 3.5 to 4.5 times the pipe diameter of the expansion device.
  • the heat exchanger includes a second heat exchanger, and the second heat exchanger includes: a second suction heat exchanger provided at one side of the first suction heat exchanger to guide the flow of the mixed refrigerant sucked into the compressor; And the expansion device performing heat exchange with the second suction heat exchange unit.
  • the first suction heat exchange unit and the condensation pipe, or the second suction heat exchange unit and the expansion device are in contact with each other to perform heat exchange.
  • the first suction heat exchange unit and the condensation pipe, or the second suction heat exchange unit, and the expansion device may be coupled by soldering.
  • a heat exchanger connection pipe disposed between the first and second heat exchangers to prevent heat exchange between the expansion device and the condensation heat exchange unit, wherein the first heat exchange unit and the second heat exchange unit are installed in the heat exchanger. Characterized in that spaced apart from each other by a connection pipe.
  • the first heat exchanger is installed at the outlet side of the second heat exchanger based on the flow direction of the refrigerant flowing through the suction pipe.
  • the second heat exchanger is installed at the outlet side of the first heat exchanger based on the flow direction of the refrigerant flowing through the condensation pipe.
  • the evaporator includes a first evaporator and a second evaporator connected in series with each other, and the second evaporator is installed at an outlet side of the first evaporator.
  • the evaporator includes a first evaporator and a second evaporator connected in parallel with each other, and the expansion device includes a first expansion device installed at an inlet side of the first evaporator and an inlet side of the second evaporator. 2 expansion devices are included.
  • the first and second expansion devices and the suction pipe are coupled to each other to exchange heat.
  • the evaporator, the first evaporator is installed on the outlet side of the expansion device; A second evaporator connected in series with the outlet side of the first evaporator; And a third evaporator connected in series to the outlet side of the second evaporator.
  • each independent refrigeration cycle comprising the compressor, condenser, expansion device, evaporator and a plurality of heat exchangers.
  • a deep freezer includes a compressor for compressing a mixed refrigerant, and the mixed refrigerant includes any one of butane (N-Butane), 1-butene (1-Butene), and isobutane (Isobutane).
  • the low temperature refrigerant composed of the selected high temperature refrigerant and ethylene (Ethylene) is included.
  • the mixed refrigerant includes butane (N-Butane) and ethylene (Ethylene).
  • the butane (N-Butane) is determined in the range of 80% to 85% by weight, and the ethylene is determined in the range of 15% to 20% by weight.
  • the compressor is operated in a set pressure range, and the set pressure range includes a range in which the maximum discharge pressure of the compressor is 25 bar or less.
  • the set pressure range includes a range in which the minimum suction pressure of the compressor is 1 bar or more.
  • the compressor is operated within a set temperature range, and the set temperature range includes a range in which the maximum discharge temperature of the compressor is 120 ° C. or less.
  • the deep freezer includes a storage compartment having a temperature value of -60 ° C or lower.
  • the compressor includes a domestic compressor operated under pressure conditions of at least 1 bar of the minimum suction pressure and of 25 bar or less of the maximum discharge pressure.
  • a condensation pipe extending from the outlet side of the condenser to the expansion device to guide the flow of the adsorption refrigerant;
  • a suction pipe extending from the outlet side of the evaporator to the compressor to guide suction of the mixed refrigerant into the compressor;
  • a plurality of heat exchangers installed in the suction pipe and performing heat exchange of the mixed refrigerant sucked into the compressor.
  • the refrigerant condensed in the condenser passes through a plurality of heat exchangers before entering the evaporator, thereby lowering the condensation pressure of the refrigeration cycle and preventing rise in dryness when the condensed refrigerant passes through the expansion device.
  • the effect is that it can.
  • the plurality of heat exchangers include a first heat exchanger for performing heat exchange between the refrigerant passing through the condenser and the suction refrigerant sucked into the compressor, the condensation pressure of the refrigeration cycle is increased during the heat exchange process in the first heat exchanger. Can be lowered. As a result, there is an advantage that it is possible to use a household compressor having a low discharge pressure and low noise, which is used in a general refrigerator.
  • the temperature of the suction refrigerant is increased to prevent the introduction of the liquid refrigerant into the compressor, thereby improving the operating reliability of the compressor.
  • the plurality of heat exchangers may include a second heat exchanger that performs heat exchange between the refrigerant passing through the expansion device after being heat exchanged in the first heat exchanger and the suction refrigerant sucked into the compressor, and thus the refrigerant may be removed from the expansion device. It is possible to prevent the increase of dryness in the process of decompression.
  • the ratio of the liquid refrigerant in the refrigerant flowing into the evaporator has an advantage that the heat of evaporation, that is, the cooling power can be improved.
  • the diameter of the condensation heat exchanger constituting the first heat exchanger is larger than the diameter of the expansion device constituting the second heat exchanger, condensation may be easily performed while the refrigerant passes through the first heat exchanger. The effect is that the condensation temperature and condensation pressure can be lowered.
  • the length of the first heat exchanger is proposed as an optimum range, heat exchange can be performed, and thus, the refrigerant cycle characteristics can satisfy the operating conditions of the domestic compressor and improve the operation reliability of the compressor.
  • first heat exchanger may be configured by a combination of a condensation pipe and a suction pipe
  • second heat exchanger may be configured by a combination of a capillary tube and a suction pipe, thereby improving heat exchange efficiency
  • condensation refrigerant passing through the condenser may be introduced into the second heat exchanger after being heat exchanged in the first heat exchanger, the condensation pressure may be lowered first and dryness may be prevented in the expansion process.
  • the weight ratio of the azeotropic mixed refrigerant can be optimally proposed, it is possible to implement a desired cryogenic environment and to satisfy an appropriate discharge pressure of the domestic compressor.
  • FIG. 1 is a view showing a refrigeration cycle provided in a deep freezer according to a first embodiment of the present invention.
  • FIG. 2 is a view showing the configuration of the first and second heat exchangers according to the first embodiment of the present invention.
  • FIG. 3 is a P-h diagram for a deep freezer according to a first embodiment of the present invention.
  • FIG. 5 is an experimental graph showing a plurality of result values that vary depending on the amount of refrigerant of the azeotropic mixed refrigerant according to the first embodiment of the present invention.
  • FIG. 6 is a view showing a refrigeration cycle provided in the freezer temperature according to the second embodiment of the present invention.
  • FIG. 7 is a view showing a refrigeration cycle provided in the freezer temperature according to the third embodiment of the present invention.
  • FIG. 8 is a view showing a refrigerating cycle provided in a deep-temperature freezer according to a fourth embodiment of the present invention.
  • FIG. 9 is a view showing a refrigeration cycle provided in a deep-temperature freezer according to a fifth embodiment of the present invention.
  • FIG. 1 is a view showing a refrigerating cycle provided in a deep-temperature freezer according to a first embodiment of the present invention
  • Figure 2 is a view showing the configuration of the first and second heat exchangers according to the first embodiment of the present invention
  • 3 is a pH diagram for the temperature freezer according to the first embodiment of the present invention
  • Figure 4 is an experimental graph showing the optimum range of the length of the first heat exchanger according to the first embodiment of the present invention
  • Figure 5 Is an experimental graph showing a number of result values that vary depending on the amount of refrigerant in the azeotropic mixed refrigerant according to the first embodiment of the present invention.
  • a refrigeration cycle in which compression, condensation, expansion, and evaporation of a refrigerant are repeated may be operated.
  • a compressor 110 capable of compressing the refrigerant is included.
  • the compressor 110 may include a household compressor used in a general household refrigerator.
  • the temperature or pressure operating range of the compressor 110 is as follows.
  • the compressor 110 may be configured such that the maximum discharge pressure is 25 bar or less, the maximum discharge temperature is 120 ° C. or less, and the minimum suction pressure is 1 bar or less.
  • Household compressor 110 having such a temperature or pressure range has the advantage that the operation noise is generated very little.
  • the refrigerant sucked into the compressor 110 includes a mixed refrigerant.
  • the mixed refrigerant includes a first refrigerant having a first boiling point and a second refrigerant having a second boiling point lower than the first boiling point.
  • the first refrigerant may be referred to as a "high temperature refrigerant”
  • the second refrigerant may be referred to as a "low temperature refrigerant”.
  • an evaporation temperature i.e., a cryogenic temperature, required in the deep freezer may be realized, and the pressure of the refrigerant discharged from the compressor 110 may be formed within a predetermined range.
  • the core temperature may be realized by the characteristics of the low temperature refrigerant.
  • the low temperature refrigerant since the low temperature refrigerant has a relatively high discharge pressure when compressed in the compressor 110, the low temperature refrigerant may adversely affect the reliability of the compressor, particularly the domestic compressor 110 applied to the present embodiment. Therefore, in order to lower the discharge pressure, a high temperature refrigerant having a relatively low discharge pressure may be mixed.
  • the present embodiment proposes a ratio of the mixed refrigerant, that is, an appropriate ratio of the high temperature coolant and the low temperature coolant, which may correspond to the operating pressure or the operating temperature range of the domestic compressor 110.
  • isopentane, 1,2-butadiene, butane (N-Butane), 1-butene or 1-butene isobutane is included in the high temperature refrigerant. May be included. Physical properties of the high temperature refrigerant are shown in Table 1 below.
  • the evaporation temperature tends to be somewhat high. Accordingly, when the isopentane and 1,2-butadiene are used as the high temperature refrigerant according to the present embodiment, even when mixed with the low temperature refrigerant, it is difficult to realize a deep temperature. This happens.
  • the evaporation temperature has a value of 0 °C or less. Therefore, any one of butane (N-Butane), 1-butene (1-Butene) and isobutane (Isobutane) can be used as a refrigerant for high temperature according to the present embodiment in a broad sense.
  • the evaporation temperature is slightly lower, and when mixed with the low temperature refrigerant, a deep temperature may be realized, but the discharge pressure of the compressor may be somewhat higher. Problems may arise. Therefore, preferably, as the high temperature refrigerant according to the present embodiment, butane (N-Butane) having an evaporation temperature close to 0 ° C based on 1 bar is used.
  • the low temperature refrigerant may include ethane or ethylene. Physical properties of the low temperature refrigerant are shown in Table 2 below.
  • the evaporation temperature tends to be somewhat high. Therefore, when using the ethane (Ethane) as the low-temperature refrigerant according to this embodiment, there is a problem that the implementation of the deep temperature is limited.
  • the low temperature refrigerant according to the present embodiment is characterized by using ethylene having an evaporation temperature of less than -100 ° C based on 1 bar.
  • the butane N-Butane
  • the ethylene Ethylene
  • the maximum discharge pressure, minimum suction pressure and maximum discharge temperature of the compressor are increased when the weight% of butane (N-Butane) is relatively increased in the mixed refrigerant of butane (N-Butane) and ethylene (Ethylene). Decreases, and the temperature performance, that is, the temperature value of the storage compartment implemented in the deep freezer, increases.
  • the maximum discharge pressure must be 25 bar or less, the maximum discharge temperature is 120 ° C. or less, and the minimum suction pressure must be 1 bar or more.
  • the ratio of butane (N-Butane) and ethylene (Ethylene) satisfying these conditions forms a weight percentage ratio of 80: 20 ⁇ 85: 15. And within such a weight% range, the temperature of the storage compartment which can exhibit the performance required for a deep freezer, for example, a value of -60 degrees C or less can be formed.
  • the maximum discharge pressure, minimum suction pressure and maximum discharge temperature of the compressor are increased when the weight% of butane (N-Butane) is relatively increased in the mixed refrigerant of butane (N-Butane) and ethylene (Ethylene). Decreases, and the temperature performance, that is, the temperature value of the storage compartment implemented in the deep freezer, increases.
  • the maximum discharge pressure must be 25 bar or less, the maximum discharge temperature is 120 ° C. or less, and the minimum suction pressure must be 1 bar or more.
  • the ratio of butane (N-Butane) and ethylene (Ethylene) satisfying these conditions forms a weight percentage ratio of 80: 20 ⁇ 85: 15. And within such a weight% range, the temperature of the storage compartment which can exhibit the performance required for a deep freezer, for example, a value of -60 degrees C or less can be formed.
  • the ratio of butane (N-Butane) and ethylene (Ethylene) is a weight of 80: 20 ⁇ 85: 15 Refrigerants mixed to form% percentage values can be used.
  • FIG. 5 shows a result of experiments in which a mixed refrigerant is formed such that the ratio of butane (N-Butane) and ethylene is 83:17, and the storage chamber having a predetermined volume is cooled while increasing the amount of refrigerant. .
  • the suction pipe temperature tends to decrease little by little, the temperature of the storage compartment also decreases, and the amount of energy consumed gradually increases.
  • the amount of the mixed refrigerant needs to be filled at least 80 g.
  • the amount of the mixed refrigerant may vary depending on the volume of the storage compartment.
  • FIG. 3 shows a Ph diagram, and the portion indicated by a dotted line indicates a refrigeration cycle in which a plurality of heat exchangers 210 and 250 according to the present embodiment are not provided as a prior art, and the portion indicated by a solid line is configured according to the present embodiment.
  • the P-h diagram shows a number of isotherms.
  • the isotherm includes T2 (T2 '), T3, T4, T5, and T7.
  • the temperature value according to the isotherm may satisfy the following relation, that is, T2 (T2 ')> T7> T3> T5> T4.
  • T2 (T2 ') may be formed in the range of 35 ⁇ 40 °C, T7 is 30 ⁇ 35 °C, T3 is 8 ⁇ 13 °C, T5 is about -60 °C, T4 is about -80 °C.
  • the deep-temperature freezer 10 further includes a condenser 120 which is installed at the outlet side of the compressor 110 and condenses the mixed refrigerant discharged from the compressor 110. .
  • the deep-temperature freezer 10 includes a dryer 130 installed at an outlet side of the condenser 120 to filter out water or foreign substances from the refrigerant condensed in the condenser 120.
  • the deep-temperature freezer 10 further includes an expansion device 140 installed at the outlet side of the dryer 130 to reduce the refrigerant condensed in the condenser 120.
  • the expansion device 140 may include a capillary tube.
  • the deep freezer 10 further includes a condensation pipe 161 extending from the outlet side of the condenser 120 to the expansion device 140.
  • the dryer 130 may be installed in the condensation pipe 161.
  • the deep-temperature freezer 10 further includes an evaporator 150 installed at an outlet side of the expansion device 140 to evaporate the refrigerant decompressed in the expansion device 140.
  • the deep freezer 10 further includes a suction pipe 165 extending from the outlet side of the evaporator 150 to the suction side of the compressor 110.
  • Cooling air generated while the mixed refrigerant passes through the compressor 110, the condenser 120, the expansion device 140, and the evaporator 150 may be supplied to the storage compartment provided in the deep freezer 10.
  • the deep-temperature freezer 10 further includes a plurality of heat exchangers 210 and 250 for improving the operating efficiency of the deep-freezer 10.
  • the plurality of heat exchangers 210 and 250 include a first heat exchanger 210 for performing heat exchange between the refrigerant flowing through the condensation pipe 161 and the refrigerant flowing through the suction pipe 165.
  • the first heat exchanger 210 may include a first suction heat exchanger 211 and a condensation heat exchanger 213 that performs heat exchange with the first suction heat exchanger 211.
  • the first suction heat exchanger 211 may constitute at least a portion of the suction pipe 165
  • the condensation heat exchanger 213 may constitute at least a portion of the condensation pipe 161.
  • the first suction heat exchanger 211 and the condensation heat exchanger 213 may be configured to contact each other.
  • the first suction heat exchanger 211 and the condensation heat exchanger 213 may be coupled by soldering.
  • heat exchange is performed between the first suction heat exchanger 211 and the condensation heat exchanger 213, a low temperature refrigerant flowing through the first suction heat exchanger 211 flows through the condensation heat exchanger 213.
  • the refrigerant of can be cooled.
  • the condensation pressure of the refrigerating cycle is lowered, whereby the discharge pressure of the compressor 110 can be reduced.
  • operation reliability of the domestic compressor 110 may be improved and noise may be reduced as described above.
  • the ratio of the liquid refrigerant contained in the refrigerant, that is, the ineffective cooling power may be reduced.
  • inflow of the liquid refrigerant into the compressor 110 may be prevented.
  • the state of the refrigerant (point 1) compressed in the compressor 110 represents point 2 after passing through the condenser 120. Then, the refrigerant is condensed while passing through the condensation heat exchanger 213 (heat amount Q1), and as a result, the condensation temperature is lowered from T2 to T3 and the condensation pressure is formed to Pd.
  • the refrigerant compressed in the compressor condenses only in the condenser.
  • the state of the compressed refrigerant represents point 1 '
  • the state of the refrigerant represents point 2'. That is, compared with the present invention, the condensation pressure indicates Pd 'higher than the Pd, and the condensation temperature indicates T2' higher than the T3.
  • T2 ' has the same temperature value as T2.
  • the refrigerant passing through the condenser 120 is heat-exchanged in the first heat exchanger 210, whereby the condensation pressure Pd is lowered by ⁇ P than the conventional condensing pressure beam Pd ', and the condensation temperature T3. It can be seen that the lower than the condensation temperature (T2 ') of the prior art.
  • the refrigerant passing through the first suction heat exchange part 211 may undergo a process of endotherming and evaporating from the refrigerant passing through the condensation heat exchange part 213 (point 6-> 7, heat quantity Q1 ').
  • the ineffective cold power is a cold power of a refrigerant having a temperature higher than the temperature of cold air to be supplied to the deep storage compartment, for example, -60 ° C. or more, and is understood to be useless cold power that is difficult to be supplied to the deep storage compartment. That is, in the P-h diagram, since the temperature of T5 is about -60 ° C, it can be understood that the cooling force of the refrigerant forming the temperature of T5 to T7 is an ineffective cooling force.
  • some of the ineffective cooling force may be used to cool the condensation heat exchanger 213 of the first heat exchanger 210 through the first suction heat exchanger 211.
  • the specific gravity of the liquid refrigerant may decrease while the refrigerant passing through the first suction heat exchange unit 211 is evaporated.
  • the plurality of heat exchangers 210 and 250 include a second heat exchanger 250 for performing heat exchange between the refrigerant flowing through the expansion device 140 and the refrigerant flowing through the suction pipe 165.
  • the first heat exchanger 210 may be installed at the outlet side of the second heat exchanger 250 based on the flow direction of the refrigerant flowing through the suction pipe 165.
  • the second heat exchanger 250 may be installed at the outlet side of the first heat exchanger 210 based on the flow direction of the refrigerant flowing through the condensation pipe 161.
  • the second heat exchanger 250 includes an expansion for performing heat exchange with the second suction heat exchanger 251 and the second suction heat exchanger 251 provided on one side of the first suction heat exchanger 211.
  • Device 140 may be included.
  • the second suction heat exchanger 251 may constitute at least a portion of the suction pipe 165.
  • the second suction heat exchanger 251 and the expansion device 140 may be configured to contact each other.
  • the second suction heat exchanger 251 and the expansion device 140 may be coupled by soldering.
  • the pressure and temperature of the refrigerant may be lowered, and the ratio of the gaseous refrigerant in the refrigerant may be increased.
  • the gaseous refrigerant has a bad effect on the evaporation performance of the evaporator 150, and if the proportion of the gaseous refrigerant is increased, the proportion of the liquid refrigerant that can be evaporated decreases, so that the evaporation performance may be deteriorated.
  • the ratio of the liquid refrigerant at the inlet side of the evaporator 150 may be increased, thereby improving the evaporation performance. Appears.
  • the first heat exchanger 210 may be installed at the outlet side of the second heat exchanger 250 based on the refrigerant flow direction in the suction pipe 165.
  • the first suction heat exchanger 211 may be installed at an outlet side of the second suction heat exchanger 251.
  • the refrigerant passing through the evaporator 150 is heat-exchanged in the second heat exchanger 250 and then heat-exchanged in the first heat exchanger 210, thereby increasing the dryness and reducing the ineffective cooling power.
  • the suction temperature may increase as the dryness increases, and as the suction temperature increases, the suction temperature condition of the household compressor 110 may be easily met.
  • the refrigerant passing through the first heat exchanger 210 exchanges heat with the second suction heat exchanger 251 while passing through the expansion device 140 (heat quantity Q2), and as a result, the refrigerant.
  • the temperature of is lowered from T3 to T4, and the pressure of the refrigerant can be lowered from Pd to Ps (the state of the refrigerant moves from point 3 to 4).
  • the state of the refrigerant moves from point 3 to 4.
  • the refrigerant heat-exchanged in the first heat exchanger 210 is further heat-exchanged in the second heat exchanger 250, the pressure and temperature of the refrigerant may be lowered.
  • the refrigerant passing through the expansion device 140 of the second heat exchanger 250 is introduced into the evaporator 150 and evaporated. After the refrigerant passes through the evaporator 150, the state changes from point 4 to 5.
  • the temperature T4 at point 4 is about -80 ° C and the temperature T5 at point 5 represents about -60 ° C.
  • the refrigerant cooling force in the sections 4 to 5 can serve as an effective cooling force sufficient to cool the cold air to be supplied to the storage compartment of the deep freezer.
  • the refrigerant passing through the evaporator 150 passes through the second suction heat exchanger 251 of the second heat exchanger 250, and is endothermic to evaporate from the refrigerant passing through the expansion device 140 (point 5 -> 6, calories Q2 ').
  • the coolant cooling power in the sections 5 to 6 is a cooling force corresponding to a temperature of -60 ° C or higher, and acts as an ineffective cooling force.
  • the calorific value Q2 ′ may be used to cool the expansion device 140 of the second heat exchanger 250 through the second suction heat exchanger 251. In this process, while the refrigerant passing through the second suction heat exchange unit 251 is evaporated, the specific gravity of the liquid refrigerant may decrease.
  • the Q1 'and Q2' are ineffective cooling power, but are used to cool the condensation heat exchanger 213 of the first heat exchanger 210 and the expansion device 140 of the second heat exchanger 250. Can be.
  • the refrigerant passing through the first and second suction heat exchangers 211 and 251 may reduce the specific gravity of the liquid refrigerant while evaporating.
  • the deep-temperature freezer 10 further includes a heat exchanger connection pipe 260 disposed between the first heat exchanger 210 and the second heat exchanger 250.
  • the heat exchanger connection pipe 260 constitutes a part of the condensation pipe 161 and may be configured to connect the first heat exchanger 210 and the second heat exchanger 250.
  • first heat exchanger 210 and the second heat exchanger 250 are spaced apart from each other by the heat exchanger connection pipe 260, heat exchange is prevented between the first and second heat exchangers 210 and 250. Can be. That is, heat exchange may be prevented between the condensation heat exchanger 213 and the expansion device 140.
  • the heat exchanger connection pipe 260 is disposed between the first and second heat exchangers 210 and 250 to solve this problem.
  • the length of the first heat exchanger 210 increases, that is, as the amount of heat exchange in the first heat exchanger 210 increases, the endotherm of the refrigerant sucked into the compressor 110 increases, so that the temperature of the compressor 110 increases. The suction temperature will increase. Then, the energy consumption according to the operation of the deep-temperature freezer 10 is reduced.
  • the suction temperature Ts of the compressor 110 may satisfy the following equation with respect to the ambient temperature (room temperature, To).
  • the suction temperature Ts of the compressor 110 may satisfy the above equation. .
  • the length of the first heat exchanger 210 to satisfy the suction temperature Ts of the compressor 110 may be about 3.5 to 5 m. That is, when the length condition of the first heat exchanger 210 is satisfied, the operation condition of the domestic compressor 110 according to the present embodiment may be satisfied, and the operation reliability of the compressor may be improved.
  • the pipe diameter of the condensation heat exchanger 213 may be larger than the pipe diameter of the expansion device 140.
  • the pipe diameter of the condensation heat exchanger 213 may be formed in the range of 3.5 to 4.5 times the pipe diameter of the expansion device (140).
  • the pipe diameter of the condensation heat exchanger 213 may be 3.5 mm, and the pipe diameter of the expansion device 140 may be 0.8 mm.
  • the refrigerant passing through the condensation heat exchanger 213 should be condensed.
  • the refrigerant passing through the expansion device 140 should be reduced in pressure.
  • the dryness of the exit state (point 4) of the expansion device 140 is formed higher than the dryness of the inlet state (point 3). That is, in the process of passing the refrigerant through the expansion device 140, vaporization is performed with decompression.
  • the pipe diameter may be reduced to increase the flow rate of the refrigerant, and thus the pressure of the refrigerant may be reduced.
  • the condensation heat exchanger 213 acts as a resistance to the refrigerant, so that the refrigerant flow rate decreases and the refrigerant pressure decreases, while the refrigerant condensation May be limited.
  • the pipe diameter of the condensation heat exchange part 213 is sufficiently larger than the pipe diameter of the expansion device 140 so that the condensation heat exchange part 213 does not act as a resistance to the refrigerant. It is characterized by.
  • a relatively bulky gaseous refrigerant may easily flow through the condensation heat exchanger 213 and may be sufficiently condensed while heat exchange is performed in the first heat exchanger 210.
  • FIG. 6 is a view showing a refrigeration cycle provided in the freezer temperature according to the second embodiment of the present invention.
  • the deep-temperature freezer 10a includes the compressor 110, the condenser 120, the dryer 130, the expansion device 140, and the condenser 120.
  • Condensation pipe 161 extending to the expansion device 140 is included.
  • the deep-temperature freezer 10a exchanges heat between the refrigerant passing through the first heat exchanger 210 and the expansion device 140 to perform heat exchange between the condensation refrigerant and the suction refrigerant to the compressor 110 and the suction refrigerant. Further included is a second heat exchanger 250 to perform the.
  • the deep freezer 10a further includes a plurality of evaporators 151 and 152 for evaporating the refrigerant depressurized by the expansion device 140.
  • the plurality of evaporators 151 and 152 may include a first evaporator 151 installed at an outlet side of the expansion device 140 and a second evaporator 152 installed at an outlet side of the first evaporator 151. .
  • the first and second evaporators 151 and 152 may be connected in series.
  • the deep freezer 10a may include a plurality of storage compartments corresponding to the plurality of evaporators 151 and 152.
  • the plurality of storage rooms may include a cryogenic storage room of about ⁇ 60 ° C. or less and a freezer of about ⁇ 20 ° C.
  • the cold air generated by the first evaporator 151 may be supplied to the cryogenic storage chamber, and the cold air generated by the second evaporator 152 may be supplied to the freezing chamber.
  • the second heat exchanger 250 may be installed at the outlet side of the second evaporator 152, and the first heat exchanger 210 may be installed at the outlet side of the second heat exchanger 250.
  • the refrigerant evaporated in the second evaporator 152 is endothermic while passing through the second heat exchanger 250 and the first heat exchanger 210. Accordingly, the temperature of the refrigerant sucked into the compressor 110 increases and the dryness is increased. May be raised.
  • FIG. 7 is a view showing a refrigeration cycle provided in the freezer temperature according to the third embodiment of the present invention.
  • the deep freezer 10b includes the compressor 110, the condenser 120, the dryer 130, the expansion device 140, and the condenser 120.
  • Condensation pipe 161 extending to the expansion device 140 is included.
  • the expansion device 140 includes two expansion devices.
  • the two expansion devices are connected in parallel with the first expansion device 141 and the first expansion device 141 through which at least a portion of the refrigerant flowing through the condensation pipe 161 may flow, and the condensation pipe ( A second expansion device 143 is included through which another portion of the refrigerant flowing in 161 can flow.
  • a valve device for introducing a refrigerant flowing through the condensation pipe 161 into at least one expansion device 143 of the first expansion device 141 and the second expansion device 143. 170 may be installed.
  • the valve device 170 may include a three-way valve.
  • the condensation pipe 161 is connected to the inlet of the three-way valve, and the first and second expansion devices 141 and 143 may be connected to the two outlets of the three-way valve, respectively.
  • the deep freezer 10b includes a first evaporator 151a connected to an outlet side of the first expansion device 141 and a second evaporator 152a connected to an outlet side of the second expansion device 143. More included.
  • a first evaporation pipe 181 extending from the first outlet of the valve device 170 to the first evaporator 151a and a second outlet of the valve device 170 are provided.
  • a second evaporation pipe 183 extending from the portion to the second evaporator 152a is further included.
  • the first evaporation pipe 181 and the second evaporation pipe 183 may be laminated at the lamination part 185.
  • the lamination part 185 may be one point of the first evaporation pipe 181 or the second evaporation pipe 183.
  • the first evaporator 151a and the second evaporator 152a may be connected in parallel.
  • the first evaporating pipe 181 may be provided with a check valve 158 for guiding the one-way flow of the refrigerant in the first evaporating pipe 181.
  • a check valve 158 By the check valve 158, the flow of cold water from the lamination part 185 toward the first evaporator 151a may be restricted. As a result, the refrigerant passing through the second evaporator 152a may be prevented from entering the first evaporator 151a through the lamination part 185.
  • At least one of the first and second evaporators 151a and 152a may be operated under the control of the valve device 170.
  • the first outlet of the two outlets of the valve device 170 is opened and the second outlet is closed, only the refrigerant flow from the valve device 170 to the first evaporator 151a may be generated.
  • the deep freezer 10b may include a plurality of storage compartments corresponding to the plurality of evaporators 151a and 152a.
  • the plurality of storage compartments may include two cryogenic storage compartments of -60 ° C or less.
  • the plurality of storage rooms may include a cryogenic storage room of about ⁇ 60 ° C. or less and a freezer of about ⁇ 20 ° C.
  • the refrigerant passing through the first evaporator 151a or the second evaporator 152a may pass through the second heat exchanger 250a.
  • the second heat exchanger 250a includes at least a portion of the first expansion device 141, the second expansion device 143, and the suction pipe 165, that is, the second suction heat exchanger 251 described in the first embodiment. ) May be included.
  • the first and second expansion devices 141 and 143 and the second suction heat exchanger 251 may be disposed to contact each other.
  • the first and second expansion devices 141 and 143 and the second suction heat exchanger 251 may be coupled by soldering.
  • a first heat exchanger 210a may be installed at the outlet side of the second heat exchanger 250a.
  • the first heat exchanger 210a includes at least a portion of the condensation pipe 161, that is, at least a portion of the condensation heat exchanger 213 and the suction pipe 165 described in the first embodiment, that is, the first suction.
  • the heat exchanger 211 may be included. Description of the operation of the first heat exchanger 210a and the second heat exchanger 250a uses the description of the first embodiment.
  • FIG. 8 is a view showing a refrigerating cycle provided in a deep-temperature freezer according to a fourth embodiment of the present invention.
  • the deep freezer 10c includes the compressor 110, the condenser 120, the dryer 130, the expansion device 140, and the condenser 120.
  • Condensation pipe 161 extending to the expansion device 140 is included.
  • a heat exchange between the refrigerant passing through the first heat exchanger (210) and the expansion device (140) for performing heat exchange between the condensation refrigerant and the suction refrigerant to the compressor (110) and the suction refrigerant is performed. Further included is a second heat exchanger 250 to perform the.
  • the deep freezer 10c further includes a plurality of evaporators 151b, 152b, and 153b for evaporating the refrigerant decompressed in the expansion device 140.
  • the plurality of evaporators 151b, 152b and 153b may include a first evaporator 151b provided at an outlet side of the expansion device 140 and a second evaporator provided at an outlet side of the first evaporator 151b ( 152b) and a third evaporator 153b installed at the outlet side of the second evaporator 152b.
  • the first, second, and third evaporators 151b, 152b, and 153b may be connected in series.
  • the deep freezer 10c may include a plurality of storage compartments corresponding to the plurality of evaporators 151b, 152b, and 153b.
  • the plurality of storage rooms may include a cryogenic storage room of -60 ° C or less, a freezer of about -20 ° C, and a refrigerating room of 0 to 5 ° C.
  • the cold air generated by the first evaporator 151b may be supplied to the cryogenic storage chamber
  • the cold air generated by the second evaporator 152b may be supplied to the freezing chamber
  • the third evaporator 153b The cold air generated in) may be supplied to the refrigerating compartment.
  • the second heat exchanger 250 may be installed at the outlet side of the third evaporator 153b, and the first heat exchanger 210 may be installed at the outlet side of the second heat exchanger 250.
  • the refrigerant evaporated in the second evaporator 152 is endothermic while passing through the second heat exchanger 250 and the first heat exchanger 210. Accordingly, the temperature of the refrigerant sucked into the compressor 110 increases and the dryness is increased. May be raised.
  • the related description uses the description of the first embodiment.
  • FIG. 9 is a view showing a refrigeration cycle provided in a deep-temperature freezer according to a fifth embodiment of the present invention.
  • the deep-temperature freezer 10d according to the fifth embodiment of the present invention includes two independent refrigeration cycles.
  • the configurations of the two independent refrigeration cycles are identical to each other.
  • the two refrigeration cycles include a first refrigeration cycle.
  • the first refrigeration cycle the first compressor (110a), the first condenser (120a), the first dryer (130a), the first expansion device (140a), the first condensation pipe (161a), the first evaporator ( 150a), a first suction pipe 165a, a second heat exchanger 250b, and a first heat exchanger 210b. Description of these configurations and operations is the same as that of the first embodiment.
  • the two refrigeration cycles include a second refrigeration cycle.
  • the first refrigeration cycle the second compressor 110b, the second condenser 120b, the second dryer 130b, the second expansion device 140b, the second condensation pipe 161b, the second evaporator ( 150b), a second suction pipe 165b, a fourth heat exchanger 250c, and a third heat exchanger 210c. Description of these configurations and operations is the same as that of the first embodiment.
  • two refrigeration cycles independent of each other may be operated to cool the plurality of storage compartments provided in the deep freezer 10d.
  • the plurality of storage compartments may include two cryogenic storage compartments of -60 ° C or less.
  • the cold air generated in the first refrigeration cycle may cool the first cryogenic storage chamber, and the cold air generated in the second refrigeration cycle may cool the second cryogenic storage chamber.
  • the refrigerant condensed in the condenser passes through a plurality of heat exchangers before entering the evaporator, thereby lowering the condensation pressure of the refrigeration cycle and preventing rise in dryness when the condensed refrigerant passes through the expansion device.
  • the industrial applicability is remarkable.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

Un mode de réalisation de l'invention concerne un congélateur. Un congélateur selon un mode de réalisation de la présente invention comprend une pluralité d'échangeurs de chaleur installés dans un tuyau d'entrée et réalisant un échange de chaleur d'un fluide frigorigène mixte aspiré dans un compresseur. Le fluide frigorigène mixte comprend : un fluide frigorigène haute température qui est sélectionné parmi le butane (N-butane), le 1-butène et l'isobutane ; et un fluide frigorigène basse température constitué d'éthylène.
PCT/KR2017/000463 2016-01-15 2017-01-13 Congélateur WO2017123042A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US16/069,952 US10782048B2 (en) 2016-01-15 2017-01-13 Deep freezer
DE112017000376.8T DE112017000376T5 (de) 2016-01-15 2017-01-13 Tiefkühlschrank

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
KR10-2016-0005172 2016-01-15
KR20160005161 2016-01-15
KR1020160005172A KR102446555B1 (ko) 2016-01-15 2016-01-15 심온 냉동고
KR10-2016-0005161 2016-01-15
KR10-2016-0080123 2016-06-27
KR1020160080123A KR102502289B1 (ko) 2016-01-15 2016-06-27 심온 냉동고

Publications (1)

Publication Number Publication Date
WO2017123042A1 true WO2017123042A1 (fr) 2017-07-20

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PCT/KR2017/000463 WO2017123042A1 (fr) 2016-01-15 2017-01-13 Congélateur

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WO (1) WO2017123042A1 (fr)

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CN111811154A (zh) * 2020-07-21 2020-10-23 闻婧 一种空调热交换系统
CN113432326A (zh) * 2020-03-23 2021-09-24 青岛海尔智能技术研发有限公司 复叠式压缩制冷系统以及具有其的制冷设备
CN114207363A (zh) * 2019-08-21 2022-03-18 Lg电子株式会社 使用非共沸混合制冷剂的制冷系统

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KR100756880B1 (ko) * 2006-04-14 2007-09-07 주식회사 대우일렉트로닉스 냉장고의 냉각장치
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Publication number Priority date Publication date Assignee Title
CN114207363A (zh) * 2019-08-21 2022-03-18 Lg电子株式会社 使用非共沸混合制冷剂的制冷系统
CN113432326A (zh) * 2020-03-23 2021-09-24 青岛海尔智能技术研发有限公司 复叠式压缩制冷系统以及具有其的制冷设备
CN111811154A (zh) * 2020-07-21 2020-10-23 闻婧 一种空调热交换系统

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