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WO2006137269A1 - Chambre de refroidissement de sterling - Google Patents

Chambre de refroidissement de sterling Download PDF

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Publication number
WO2006137269A1
WO2006137269A1 PCT/JP2006/311478 JP2006311478W WO2006137269A1 WO 2006137269 A1 WO2006137269 A1 WO 2006137269A1 JP 2006311478 W JP2006311478 W JP 2006311478W WO 2006137269 A1 WO2006137269 A1 WO 2006137269A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
pipe
heat medium
circulation circuit
heat exchanger
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2006/311478
Other languages
English (en)
Japanese (ja)
Inventor
Hengliang Zhang
Keiji Fujiwara
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sharp Corp
Original Assignee
Sharp Corp
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 JP2005183808A external-priority patent/JP4001607B2/ja
Application filed by Sharp Corp filed Critical Sharp Corp
Priority to US11/916,837 priority Critical patent/US20100018224A1/en
Publication of WO2006137269A1 publication Critical patent/WO2006137269A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D23/00—General constructional features
    • F25D23/003—General constructional features for cooling refrigerating machinery
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators

Definitions

  • the present invention relates to a Stirling cooler, and more particularly to a Stirling cooler that effectively uses heat of a heat dissipating part of a Stirling refrigerator to prevent dew condensation and evaporate defrost water.
  • Examples of the application of heat exchange by a reverse Stirling cycle to a refrigerator include those described in Japanese Patent Publication No. 2003-50073.
  • a Stirling refrigeration system is disclosed in which a carrier medium is enclosed in a low-temperature side circulation circuit.
  • the heat in the high temperature part is dissipated from the high temperature side heat exchange cycle (heat dissipation system).
  • the high temperature side heat exchange cycle includes a high temperature side evaporator and a high temperature side condenser connected by piping, and heat is transferred and released by the thermosiphon principle.
  • Patent Document 1 Japanese Patent Laid-Open No. 2003-50073
  • a forced circulation circuit may be formed in addition to the thermosiphon circuit described above, which includes a circulation pump and is supplied with high-temperature side evaporator-powered refrigerant. .
  • the heat of the refrigerant flowing in the forced circulation circuit is used, for example, to prevent dew condensation in the refrigerator.
  • the present invention has been made in view of the above problems, and an object of the present invention is to suppress generation of a cavity in a pump that forcibly circulates a tertiary refrigerant, and to provide a tertiary refrigerant circulation circuit. It should be used to prevent dew formation.
  • the present invention provides a Stirling refrigerator having a heat radiating portion and a heat absorbing portion, a cooling chamber cooled by the cold heat of the heat absorbing portion, a secondary refrigerant circulation circuit for cooling the heat radiating portion, And a tertiary refrigerant circulation circuit for exchanging heat with the next refrigerant circulation circuit.
  • the secondary refrigerant further includes a circulation pump that carries the tertiary refrigerant that has exchanged heat with the secondary refrigerant in the circulation circuit to the heating target portion.
  • the heating target section includes at least one of an opening of the Stirling cooler and a drain water heating section.
  • the internal pressure of the tertiary refrigerant circulation circuit is set higher than atmospheric pressure or atmospheric pressure.
  • the secondary refrigerant circulation circuit includes an evaporator that cools the heat radiating portion, a heat exchanger that performs heat exchange between the secondary refrigerant and the tertiary refrigerant, and a condenser that cools the secondary refrigerant.
  • a heat exchanger is arranged downstream of the condenser in the flow direction of the secondary refrigerant, and a condenser is arranged further downstream.
  • heat exchange between the secondary refrigerant circulation circuit and the tertiary refrigerant circulation circuit is performed by a double-pipe heat exchange.
  • the flow direction of the secondary refrigerant and the flow direction of the tertiary refrigerant in the double tube heat exchanger are opposite to each other.
  • An evaporator for evaporating the secondary refrigerant and cooling the heat dissipating part is further provided, and the heat exchange is arranged in the evaporator.
  • the tertiary refrigerant circulation circuit through which the tertiary refrigerant circulates is a secondary refrigerant circulation circuit force independent circulation circuit connected to the high-temperature side evaporator, so that the tertiary refrigerant is forcedly circulated. It is possible to suppress the generation of cavity in the pump, and it is possible to prevent the occurrence of dew etc. by using forced circulation.
  • FIG. 1 is a perspective view showing a schematic configuration of a Stirling cooler according to Embodiment 1 of the present invention.
  • FIG. 2 is a piping system diagram of the Stirling refrigerator according to the first embodiment.
  • FIG. 3 is a perspective view of a Stirling cooler according to the second embodiment.
  • FIG. 4 is a rear view of the Stirling refrigerator shown in FIG.
  • FIG. 5 is a side sectional view of the Stirling cooler shown in FIG. 3.
  • FIG. 6 is a piping system diagram of the Stirling refrigerator according to the third embodiment.
  • FIG. 7 is a piping system diagram of the Stirling refrigerator according to the fourth embodiment.
  • FIG. 8 is a perspective view of the vicinity of a heat radiation part of a Stirling cooler according to a fifth embodiment.
  • FIG. 9 is a perspective view of the vicinity of a heat radiating portion of a Stirling cooler according to a sixth embodiment.
  • FIG. 10 is a circuit diagram showing a schematic configuration of a Stirling cooler according to the seventh embodiment.
  • FIG. 11 is a plan view showing another example of the heat exchanger.
  • FIG. 12 is a plan view showing still another example of heat exchange.
  • FIG. 1 is a perspective view showing a schematic configuration of a Stirling cooler 100 according to Embodiment 1 of the present invention.
  • the Stirling cooler 100 includes a refrigerated object (cooled object). ) In the refrigeration room (cooling room) 10, the freezing room (cooling room) 11 that houses the object to be frozen (cooling object) and is arranged in the lower stage of the cold room 10, the freezing room 11, and the cold room 10 And a cabinet (partition wall) 12 made of a heat insulating material and a Stirling refrigerator 13 including a heat radiating portion 13a and a heat absorbing portion 13b.
  • a cabinet partition wall
  • the Stirling refrigerator 100 includes a secondary refrigerant circulation circuit 14 in which the heat medium (secondary refrigerant) A naturally circulates, an evaporator 15 in which the heat medium A evaporates and cools the heat radiation part 13a, and a heat medium (tertiary refrigerant).
  • (Refrigerant) includes a tertiary refrigerant circulation circuit 28 forcibly circulating B, a heat exchanger 16, and a piezoelectric pump (circulation pump) 17 for forcibly circulating the heat medium B.
  • the Stirling refrigerator 100 stores drain water generated by defrosting and includes a drain pan (storage unit) 18 disposed on the bottom side of the Stirling refrigerator 100.
  • the Stirling refrigerator 13, the heat exchanger 16, and the condenser 34 are disposed in a machine room 35 disposed substantially in the center of the Stirling refrigerator 100.
  • the heat exchanger 16 is disposed above the Stirling refrigerator 13, and the condenser 34 is also disposed above the Stirling refrigerator 13.
  • the secondary refrigerant circulation circuit 14 is in heat exchange with the upper end portion side of the evaporator 15.
  • the secondary refrigerant circulation circuit 14 connects the upper end portion side of the evaporator 15 and the upper surface side of the condenser 34, and the gas pipe that circulates the gaseous heat medium A generated in the evaporator 15. 32, a liquid pipe 31 that connects the lower end side of the evaporator 15 and the lower surface side of the condenser 34, a heat exchanger 16, and a condenser 34.
  • the heat medium ⁇ that circulates in the secondary refrigerant circulation circuit 14 and the heat medium B that circulates in the tertiary refrigerant circulation circuit 28 are water or a mixture of water and alcohol and are frozen. It is difficult. Further, the inside of the secondary refrigerant circulation circuit 14 is set to be lower than the atmospheric pressure, so that the heat medium A is easily evaporated in the evaporator 15 at the temperature of the heat radiating portion 13a.
  • the tertiary refrigerant circulation circuit 28 connects the lower surface side of the heat exchange and the piezoelectric pump 17, and a high-temperature pipe 27 extending downward, and a drain water heating unit 21 that heats the drain water in the drain pan 18. And dew condensation prevention pipes 19a to 19c, 20a to 20d, and a cryogenic pipe 26. Further, the tertiary refrigerant circulation circuit 28 includes a heat exchanger 16 disposed above the Stirling refrigerator 13.
  • the piezoelectric pump 17 is disposed on the back side of the Stirling cooler 100, and a drain water heating unit 21 is disposed on the downstream side.
  • the drain water heating unit 21 is disposed on the bottom side of the Stirling cooler 100.
  • the drain water heating unit 21 is arranged in a meandering shape on the lower surface of the Stirling cooler 100.
  • a dew prevention pipe 19a is arranged on the downstream side of the drain water heater 21, a dew prevention pipe 19a is arranged.
  • This dew-prevention pipe 19a is arranged on the side of the front opening of the freezer compartment 11 and is The bottom side force of the ring cooler 100 extends toward the top side.
  • a dew prevention pipe 20a is provided on the downstream side of the dew prevention pipe 19a.
  • the dew prevention pipe 20a is disposed on the side portion of the front opening of the refrigerator compartment 10, and extends from the substantially central portion of the Stirling cooler 100 toward the upper surface.
  • a dew prevention pipe 20b is disposed downstream of the dew prevention pipe 20a.
  • the dew prevention pipe 20b is disposed on the upper side of the front opening of the refrigerator compartment 10, and the dew prevention pipe 20c is disposed on the downstream side of the dew prevention pipe 20b.
  • the dew prevention pipe 20c is disposed to face the dew prevention pipe 20a, and is disposed on the side portion of the front opening of the refrigerator compartment 10.
  • a dew prevention pipe 20d is disposed downstream of the dew prevention pipe 20c. This dew prevention pipe 20d is arranged at the lower side of the front opening of the refrigerator compartment 10, and a dew prevention pipe 19b is arranged downstream of the dew prevention pipe 20d.
  • the dew prevention pipe 19b is disposed on the upper side of the front opening of the freezer compartment 11, and the dew prevention pipe 19c is disposed on the downstream side of the dew prevention pipe 19b.
  • This dew condensation prevention pipe 19c is disposed opposite to the dew condensation prevention pipe 19a, and is disposed on the side portion of the front opening of the freezer compartment 11.
  • the heating target portion of the tertiary refrigerant circulation circuit 28 is the upper surface of the drain pan 18 and the door packing contact portion that is the front opening of the refrigerator compartment 10 and the freezer compartment 11. ing.
  • a cryogenic pipe 26 is disposed downstream of the dew prevention pipe 19c. The cryogenic pipe 26 extends from the lower side of the front opening of the freezer compartment 11 toward the rear side of the Stirling refrigerator 100, and from the bottom side of the Stirling refrigerator 100 to the upper surface of the Stirling refrigerator 100. It extends towards the side. The upper end portion of the cryogenic tube 26 is connected to the upper surface side of the heat exchange.
  • the internal pressure in the tertiary refrigerant circulation circuit 28 is set to atmospheric pressure or higher than atmospheric pressure, for example, 1013 hPa or more.
  • FIG. 2 is a piping system diagram of the Stirling cooler 100 according to the first embodiment.
  • the Stirling cooler 100 is provided in the heat absorbing part 13b that generates cold.
  • the primary refrigerant circulation circuit 44 includes a low temperature side condenser 42, a cooler 40, and a pipe 43 through which the heat medium C circulates between the low temperature side condenser 42 and the cooler 40.
  • the cooler 40 Is provided with a fan 41 for supplying cold air generated by the cooler 40 to the freezer compartment or the refrigerator compartment.
  • the heat exchanger 16 is formed in a hollow shape, and is filled with the heat medium B and a non-oxidizing gas.
  • the non-oxidizing gas (non-oxidizing atmosphere) filled in the heat exchanger 16 include nitrogen, methane, and ethane. Further, the non-oxidizing gas is not limited to these gases, and any gas that does not easily oxidize the wall surface of the heat exchanger 16 may be used.
  • the pipe line of the secondary refrigerant circulation circuit 14 is arranged in a meandering shape. For this reason, a large area for heat exchange between the heat medium A and the heat medium B is ensured.
  • the heat medium A evaporates in the evaporator 15 due to the temperature of the heat radiating portion 13a.
  • the heat medium A evaporates well, and the heat radiating portion 13a is cooled well.
  • the gaseous heat medium A flows through the gas pipe 30 or the gas pipe 32 and is supplied to the condenser 34 or the heat exchanger 16.
  • the gaseous heat medium A supplied to the condenser 34 is cooled in the condenser 34 to become a liquid, flows through the liquid pipe 31, and returns to the evaporator 15.
  • the gaseous heat medium A supplied into the heat exchanger 16 is cooled by exchanging heat with the heat medium B, becomes liquid, flows through the liquid pipe 33, and enters the evaporator 15. Returned. That is, the heat medium A naturally circulates in the secondary refrigerant circulation circuit 14.
  • the heat medium B is heated by the heat medium A in the heat exchanger 16.
  • the heat medium B evaporates 1, and the gaseous heat medium B in the tertiary refrigerant circulation circuit 28 Is becoming difficult to occur.
  • the high-temperature heat medium B heated in the heat exchanger 16 flows through the high-temperature pipe 27 and is discharged by the piezoelectric pump 17.
  • the heat medium B discharged by the piezoelectric pump 17 first heats and evaporates the drain water stored in the drain pan 18 in the drain water heating unit 21. Then, the dew condensation prevention pipes 19a to 19c and 20a to 20d are circulated, and the vicinity of the door packing contact portion (heating target portion) of the refrigerator compartment 10 and the freezer compartment 11 is heated to suppress the occurrence of dew condensation. And circulates in the cryogenic pipe 26 Then, it is returned to the heat exchanger 16. Thus, the heat medium B is forcedly circulated in the tertiary refrigerant circulation circuit 28 by the piezoelectric pump 17.
  • the secondary refrigerant circulation circuit 14 and the tertiary refrigerant circulation circuit 28 that communicate with the evaporator 15 have separate and independent configurations, and the mutual influence is suppressed to a small level. Further, since the internal pressure in the tertiary refrigerant circulation circuit 28 is set to be equal to or higher than the atmospheric pressure, it is difficult for the gaseous heat medium B to be generated in the tertiary refrigerant circulation circuit 28.
  • the tertiary refrigerant circulation circuit 28 since the tertiary refrigerant circulation circuit 28 is not in communication with the evaporator 15, the gaseous heat medium B is generated, and the internal pressure in the tertiary refrigerant circulation circuit 28 is set to be equal to or higher than the atmospheric pressure. Therefore, the circulating heat medium B is unlikely to become gaseous. For this reason, it is difficult for the gaseous heat medium B to be supplied into the piezoelectric pump 17, and the generation of the cavity can be suppressed.
  • the internal pressure in the tertiary refrigerant circulation circuit 28 is set to be equal to or higher than the atmospheric pressure, even when bubbles are formed in the piezoelectric element, the piezoelectric element vibrates satisfactorily so that the bubbles do not easily increase. Therefore, the operation efficiency of the piezoelectric pump 17 can be ensured. Furthermore, since the heat medium A in the secondary refrigerant circulation circuit 14 is also cooled in the heat exchanger 16, the condenser 34 can be configured compactly. In addition, it is possible to suppress an excessive pressure from being applied to the pipe line of the tertiary refrigerant circulation circuit 28 by contraction of the gas filled in the heat exchanger 16. Further, since the gas filled in the heat exchanger contracts or expands, the heat medium B can stably circulate in the tertiary refrigerant circulation circuit 28, and the Stirling refrigerator 100 can be operated stably. it can.
  • FIG. 3 is a perspective view of the Stirling cooler 200 according to the second embodiment.
  • the heat exchange ⁇ 51 and the condenser 52 are on the back side of the Stirling cooler 200. It is arranged in.
  • the suction tank 53 is disposed on the rear side of the Stirling cooler 200 and on one side.
  • the suction tank 53 is formed in a columnar shape, extends from the upper surface side to the lower surface side of the Stirling cooler 200, and is embedded in the cabinet 12 that also has a heat insulating material force.
  • the diameter of the suction tank 53 is a high temperature connected to the upper end of the suction tank 53. It is formed larger than the tube 27 grade.
  • the lower end portion of the suction tank 53 is located on the bottom side of the stalling cooler 200, and the piezoelectric pump 17 is connected to the lower end portion of the suction tank 53.
  • the suction tank 53 is filled with a non-oxidizing gas.
  • a drain water heating unit 21 and dew prevention pipes 19a to 19c and 20a to 20d are connected to the downstream side of the piezoelectric pump 17, and a cryogenic pipe 26 is connected to the most downstream side.
  • the cryogenic tube 26 is connected to the lower end of the heat exchanger 51.
  • the heat exchanger 51 is configured in a flat plate shape, and is disposed on the back side of the Stirling cooler 200 so as to extend in the up-down direction.
  • This heat exchange includes a gas pipe 30 connected to the upper end of the evaporator 15 and a liquid pipe 33 connected to the lower end of the evaporator 15.
  • the condenser 52 includes a pair of head pipes 52a and 52a that are spaced apart from each other, and a parallel pipe 52b that is disposed between the head pipes 52a and 52a and connects the head pipes 52a and 52a.
  • the condenser 52 is also formed in a flat plate shape like the heat exchanger 51.
  • the pair of head pipes 52a the lower end of one head pipe 52a is connected to the gas pipe 30, and the lower end of the other head pipe 52a is connected to the liquid pipe 31.
  • the liquid pipe 31 is connected to the evaporator 15.
  • a plurality of parallel pipes 52b are arranged at equal intervals between the head pipes 52a.
  • FIG. 4 is a rear view of the Stirling refrigerator 200 according to the second embodiment.
  • the heat exchange and the condenser 52 are both above the Stirling refrigerator 13. Is arranged.
  • a plurality of heat radiating fins 52c are arranged on the parallel pipe 52b of the condenser 52.
  • FIG. 5 is a side sectional view of the Stirling cooler 200 according to the second embodiment. As shown in FIG. 5, the heat exchange ⁇ 51 and the condenser 52 shown in FIG.
  • the duct 54 is arranged.
  • the duct 54 is disposed so as to surround at least the heat exchanger 51 and extends upward and downward from the bottom surface side of the Stirling cooler 200 toward the upper surface side.
  • the duct 54 extends in the vertical direction, and the heat exchange 51 shown in FIG. 4 also extends in the vertical direction along the data 54. Therefore, the heat exchange ⁇ 51 and the duct 54 are arranged so as to extend in the vertical direction, so that the heat exchange follows the duct 54. Has been placed. A fan 55 is disposed near the upper end of the duct 54.
  • the configuration other than the above configuration is the same as that of the first embodiment, and the same reference numeral is assigned to the same configuration.
  • the heat medium 51 heated in the evaporator 15 is circulated in the heat exchanger 51 and the condenser 52, whereby the heat exchanger 51 and The air around the condenser 52 is warmed. Since the duct 54 is disposed around the heat exchanger 51 and the condenser 52, an air flow is generated in the duct 54, and the air flows upward from below the duct 54. Furthermore, since the fan 55 pulls the air in the duct 54 outward, an airflow flowing from the lower side to the upper side in the duct 54 is generated satisfactorily. The heat exchanger 51 and the condenser 52 are cooled by the airflow generated in the duct 54.
  • the heat medium circulated in the condenser 52 circulates in the head pipe 52a and circulates in the parallel pipe 52b.
  • a plurality of parallel pipes 52b are arranged, an area where the normal pipe 52b and the airflow flowing through the duct 54 come into contact with each other increases, and the heat medium A flowing through the parallel pipe 52b is cooled.
  • the parallel pipe 52b is provided with a plurality of heat radiation fins 52c, the heat medium A flowing through the parallel pipe 52b is cooled satisfactorily.
  • the suction tank 53 is embedded in the cabinet 12, it is prevented that heat is radiated outside the temperature power of the heat medium B in the suction tank 53.
  • the heat exchanger 51 and the condenser 52 are configured in a flat plate shape, and therefore can be arranged on the back side of the Stirling cooler 200.
  • the suction tank 53 is configured in a column shape and arranged on the back side of the Stirling refrigerator 200, so that the size of the machine room 35 can be made compact, and the size of the refrigerator room 10 and the freezer room 11 can be reduced. Can be secured.
  • a plurality of parallel pipes 52b through which the heat medium A flows are provided in the condenser 52. Since the parallel pipe 52b is provided with a plurality of heat radiation fins 52c, the heat medium A flowing through the condenser 52 can be cooled satisfactorily, and the condenser 52 must be made compact. Can do.
  • the suction tank 53 filled with gas is provided in the tertiary refrigerant circulation circuit 28, the body of the heat medium B in the tertiary refrigerant circulation circuit 28 as in the above embodiment. Even when the product fluctuates or fluctuation occurs in the circulating heat medium B, the heat medium B can be circulated stably by contraction or expansion of the gas in the suction tank 53.
  • FIG. 6 is a piping system diagram of the Stirling refrigerator 300 according to the third embodiment.
  • the evaporator 15 includes the functions of the condenser and the heat exchanger ⁇ .
  • a double-pipe heat exchanger 80 is disposed above the evaporator 15.
  • This double tube heat exchanger 80 includes an outer tube 81 and an inner tube 82 formed in the outer tube 81 and having a smaller diameter than the outer tube 81.
  • a plurality of radiating fins 83 are provided on the outer peripheral surface of the outer tube 81.
  • a secondary refrigerant circulation circuit 14 is connected between the outer pipe 81 and the inner pipe 82, and a tertiary refrigerant circulation circuit 28 is connected to the inner pipe 82. That is, the gas pipe 30 of the secondary refrigerant circulation circuit 14 is connected between the outer pipe 81 and the inner pipe 82 at the upper end of the double pipe heat exchanger 80, and the double pipe heat exchange is performed.
  • the liquid pipe 33 is connected between the outer pipe 81 and the inner pipe 82 at the lower end of the vessel 80.
  • the high-temperature pipe 27 of the tertiary refrigerant circulation circuit 28 is connected to the inner pipe 82 at the upper end portion of the double-pipe heat exchanger 80.
  • a cryogenic pipe 26 is connected to the inner pipe 82.
  • the heat medium circulates between the inner pipe 82 and the outer pipe 81 of the double-pipe heat exchanger 80, and the heat medium B circulates in the inner pipe 82.
  • the distribution direction is opposite to the distribution direction of heat medium B.
  • there is a double tube heat There is a fan 84 that blows air toward 80.
  • the force provided with the radiating fins 83 provided in the double-pipe heat exchanger 80 and the fan 84 and the radiating fins 83 and the fan 84 are not provided.
  • double tube heat exchanger 80 may be embedded in the cabinet. Also, surround the double-pipe heat exchanger 80 with a duct.
  • the gaseous heat medium A generated in the evaporator 15 causes the upper end force of the double-pipe heat exchanger 80 to be double-pipe heat exchange. Supplied to vessel 80.
  • the double-pipe heat exchanger 80 is disposed above the evaporator 15, the gaseous heat medium A generated in the evaporator 15 is satisfactorily generated by the double-pipe heat exchanger 80.
  • the heat medium B is supplied into the double pipe heat exchanger 80 from the lower end side of the double pipe heat exchanger 80.
  • the heated heat medium B flows through the high-temperature pipe 27, passes through the suction tank 53, and is forcedly circulated in the tertiary refrigerant circulation circuit 28 by the piezoelectric pump 17. Then, the dew condensation prevention pipe 19 and the drain water heating section are circulated and returned to the double pipe heat exchanger 80 again. On the other hand, the heat medium A is returned to the evaporator 15 after passing through the double-pipe heat exchanger 80.
  • the Stirling cooler 300 since the double-pipe heat exchanger 80 includes the functions of the heat exchange ⁇ and the condenser, the Stirling cooler 300 main body And The machine room can be made compact. For this reason, ensure the capacity of the refrigerator compartment and freezer compartment. Can be kept. In the case of embedding double-pipe heat exchange in the cabinet, a double-pipe heat exchange 80 that does not reduce the volume of the freezer or cooling chamber formed in the cabinet can be provided. Further, when the outside of the double tube type heat exchanger 80 is provided outside the heat exchanger 80, the heat medium A flowing in the outer tube 81 can be cooled well.
  • FIG. 7 is a piping system diagram of the Stirling cooler according to the fourth embodiment. As shown in FIG. 7, the Stirling cooler 400 according to the present embodiment is located above the evaporator 15. A double-pipe heat exchanger 90, a pipe line 93, and a plurality of heat radiation fins 93a provided on the surface of the pipe line 93 are provided.
  • the evaporator 15 is provided with a gas pipe 94 extending upward, and a connecting portion 94a formed at the upper end of the gas pipe 94 has a double-pipe heat exchange 90. And pipe 93 are connected.
  • the double-pipe heat exchanger 90 includes an outer tube 91 and an inner tube 92 formed in the outer tube 91 and having a smaller diameter than the outer tube 91.
  • a secondary refrigerant circulation circuit 14 is connected between the outer pipe 91 and the inner pipe 92, and a tertiary refrigerant circulation circuit 28 is connected to the inner pipe 92.
  • a connecting portion 90a is provided at the lower end of the double-pipe heat exchanger, and a liquid pipe 96 connected between the outer tube 91 and the inner tube 92 is connected to the connecting portion 90a.
  • the low temperature pipe 26 that supplies the heat medium B into the inner pipe 92 is connected.
  • the gaseous heat medium A generated in the evaporator 15 flows through the gas pipe 94 and is displaced upward.
  • the gaseous heat medium A enters between the outer pipe 91 and the inner pipe 92 of the double-pipe heat exchanger 90 and enters the pipe 93 at the connecting portion 94a.
  • the low temperature heat medium B is supplied into the double tube heat exchanger 90 from the low temperature pipe 26 connected to the connecting portion 90a. Therefore, heat exchange is performed between the heat medium A and the heat medium B in the double tube heat exchanger 90. For this reason, the heat medium A is cooled. Further, the heat medium A flowing in the pipe 93 is radiated to the outside and cooled while flowing in the pipe 93. At this time, the pipe 93 is provided with a plurality of radiating fins 93a. Medium A is well cooled. In this way, the heat medium A is cooled not only in the pipe line 93 but also in the double pipe heat exchanger 90, so that it is not necessary to provide a large number of heat radiation fins 93a provided in the pipe line 93. Wide intervals can be set.
  • the Stirling cooler 400 according to the fourth embodiment since the interval between the radiation fins 93a can be set wide, it is possible to reduce the possibility of dust being clogged between the radiation fins 93a. In this manner, since dust can be prevented from clogging between the heat radiation fins 93a, the heat radiation function of the pipe line 93 can be secured for a long time, and the heat medium A can be cooled well. Note that the Stirling refrigerator 400 according to the fourth embodiment is provided with the double-pipe heat exchange 90 as in the third embodiment, and therefore has the same effect as the third embodiment. Can be obtained.
  • FIG. 8 is a perspective view of the vicinity of the heat dissipating part of the Stirling cooler according to the fifth embodiment.
  • a heating unit 95 communicating with the tertiary refrigerant circulation circuit 28 and an evaporator 15 are provided around the heat radiation unit 13a of the Stirling refrigerator.
  • the heating unit 95 is configured by a pipe 95a spirally wound on the surface of the heat radiating unit 13a configured in a substantially cylindrical shape.
  • the conduit 95a is disposed so as to be close to or in contact with the surface of the heat radiating portion 13a.
  • the evaporator 15 is arranged around the heat radiation part 13a so as to include the heat radiation part 13a and the heating part 95 therein.
  • the evaporator 15 is filled with the heat medium A up to a position above the center.
  • a part of the heating unit 95 is arranged so as to be immersed in the heat medium A in the evaporator 15.
  • a cryogenic pipe 26 is connected to one end of the heating unit 95, and a hot pipe 27 is connected to the other end.
  • the evaporator 15 is formed in a donut shape and is fitted into the heat radiating portion 13a.
  • a gas pipe 30 communicating with a condenser (not shown) and a liquid pipe 31 through which the heat medium A liquefied in the condenser flows are connected to the upper end of the evaporator 15.
  • the heat medium B flowing in the heating unit 95 is directly heated from the heat radiating unit 13a and also from the high-temperature heat medium A in the evaporator 15. Heated. For this reason, while the heat medium B is heated satisfactorily, the heat radiating part 13a and the heat Medium A is cooled. Further, in the portion of the heating unit 95 that is in contact with the gaseous heat medium A, heat is exchanged well with the gaseous heat medium A, and the heat medium B in the heating unit 95 is heated. Is heated well. That is, since the gaseous heat medium A has a larger amount of heat than the liquid heat medium A, in the heating unit 95 disposed above the liquid level of the heat medium A, the heat medium B is a gas.
  • a large amount of heat can be received from the heat medium A in the form of a plate.
  • the heating unit 95 since the heating unit 95 is close to or in contact with the heat radiating unit 13a, it directly receives heat from the heat radiating unit 13a, and the heat medium B flowing through the heating unit 95 is heated well.
  • the heat medium B is satisfactorily heated in the evaporator 15, and therefore, the dew-preventing pipe provided in the tertiary refrigerant circulation circuit 28 is drained in the water heating section. If the dew is generated, the drain water can be heated satisfactorily.
  • FIG. 9 is a perspective view of the vicinity of the heat dissipating part of the Stirling refrigerator according to the sixth embodiment.
  • the hollow is divided around the heat dissipating part 13a of the Stirling refrigerator and divided into two parts.
  • the evaporator 15 is provided with two divided evaporators 15a and 15b.
  • the divided evaporators 15a and 15b are formed in a semicircular shape, and are fitted on both sides of the side surface of the heat radiating portion 13a. That is, the arcuate outer surface on the inner diameter side of the divided evaporators 15a and 15b is in contact with the peripheral surface of the heat radiating portion 13a.
  • the divided evaporators 15a and 15b are filled with the heat medium A from above the central portion.
  • a gas pipe 30 communicating with the condenser and a liquid pipe 31 through which the heat medium A liquefied in the condenser flows are connected to upper ends of the divided evaporators 15a and 15b.
  • the heating unit 95 includes a divided heater 95c arranged in the divided evaporator 15a and a divided heater 95b arranged in the divided evaporator 15b.
  • the divided heaters 95c and 95b are formed in a semicircular shape.
  • the outer surface on the inner diameter side of the divided heaters 95c and 95b is also arranged so as to be separated from the inner surface force on the inner diameter side of the divided evaporators 15a and 15b. For this reason, the surface of the heat dissipation part 13a A heat medium A is filled between the surfaces of the divided evaporators 15a and 15b in contact with the surfaces and the inner diameter side surfaces of the divided heaters 95c and 95b.
  • the upper ends of the divided heaters 95c and 95b are located near the upper ends of the divided evaporators 15a and 15b, and are located above the liquid surface of the heat medium A filled in the divided evaporators 15a and 15b. positioned.
  • the low temperature pipe 26 for supplying the heat medium B into the divided heaters 95c and 95b, and the heated heat medium B are discharged from the divided heaters 95c and 95b.
  • the high-temperature pipe 27 is connected.
  • the hot pipe 27 is connected to the divided heaters 95c and 95b above the liquid level of the heat medium A filled in the divided evaporators 15a and 15b.
  • the heat medium A filled in the divided evaporators 15a and 15b is heated by the heat radiating unit 13a and is in a high temperature state, and a part thereof It is a hot gas. Therefore, the heat medium B in the split heater 95b is heated satisfactorily, while the heat medium A that exchanges heat with the heat medium B is cooled.
  • the heat medium A filled between the inner peripheral surface of the divided heaters 95c and 95b and the peripheral surface of the divided evaporators 15a and 15b cools the heat radiating portion 13a, Heated by the heat dissipating part 13a, the temperature is high. For this reason, the inner peripheral surfaces of the divided heaters 95c and 95b are heated by the high-temperature heat medium A.
  • the divided heaters 95c and 95b extend to the vicinity of the upper ends of the divided evaporators 15a and 15b, and a high-temperature gaseous heat medium A is located near the upper ends of the divided evaporators 15a and 15b. Since it is full, the vicinity of the upper ends of the divided heaters 95c and 95b is heated by the high-temperature gaseous heat medium A.
  • the heat medium B heated in the divided heaters 95c and 95b flows through the high temperature pipe 27 and is discharged from the divided heaters 95c and 95b.
  • the heat medium B flowing through the high-temperature pipe 27 is heated well by the gaseous heat medium A.
  • it circulates in the tertiary refrigerant circulation circuit 28 and circulates through the drain water heating section and the dew condensation prevention pipe to heat the drain water and suppress the occurrence of dew condensation.
  • the heat exchange between the heat medium A and the heat medium B is performed in the same manner as in the fifth embodiment. Therefore, the same functions and effects as in the fifth embodiment are provided. Can be obtained. [0066] (Embodiment 7)
  • FIG. 10 is a circuit diagram showing a schematic configuration of Stirling refrigerator 100 according to the seventh embodiment.
  • the Stirling refrigerator 100 includes a secondary refrigerant circulation circuit 102 through which the heat medium A circulates and a tertiary refrigerant circulation circuit 101 through which the heat medium B circulates.
  • the secondary refrigerant circulation circuit 102 includes an evaporator 112 that cools the heat radiation part 13a of the Stirling refrigerator 13 shown in FIG. 1, a heat exchanger 103 that exchanges heat with the heat medium B of the tertiary refrigerant circulation circuit 101, and a heat And a condenser 123 for cooling the medium A.
  • the heat exchanger 103 is disposed above the evaporator 112, and the condenser 123 is disposed above the heat exchanger 103. Then, the heat medium A circulates from the evaporator 112 through the heat exchanger 103, from the heat exchanger 103 through the condenser 123, and back to the evaporator 112. That is, the heat exchanger 103 is disposed downstream of the evaporator 112 in the flow direction of the heat medium A, and the condenser 123 is disposed downstream of the heat exchanger 103 in the flow direction of the heat medium A. Yes.
  • the evaporator 112 and the heat exchanger 103 are connected by a pipe 124A, and the heat exchanger 103 and the condenser 123 are connected by a pipe 124B.
  • the flow area L2 of the heat medium A in the pipe 124B is formed wider than the flow area L1 of the heat medium A in the pipe 124A.
  • a liquid return pipe 124 C is provided between the lower end portion of the heat exchanger 103 and the evaporator so that the heat medium A liquidized in the heat exchanger 103 returns to the evaporator 112.
  • a pipe 125 is connected between the condenser 123 and the evaporator 112.
  • a fan 126 for cooling the condenser 123 is arranged in the vicinity of the condenser 123.
  • the tertiary refrigerant circulation circuit 101 includes a piezoelectric pump 108 that forcibly circulates the heat medium B, and a dew condensation prevention pipe 110 and drain water heating that are disposed downstream of the piezoelectric pump 108 in the flow direction of the heat medium B.
  • a disposed suction tank 105 is formed in a cylindrical shape extending in the vertical direction, and a gas atmosphere such as nitrogen is stored on the upper end side of the succession tank 105.
  • the Suction tank 105 The heat medium B is stored on the lower end side of the central force.
  • the position of the liquid level of the heat medium B in the succession tank 105 is uniquely set by the filling amount of the heat medium B filled in the tertiary refrigerant circulation circuit 101.
  • a pipe 104 is connected between the suction tank 105 and the heat exchanger 103.
  • the opening 104a on the side of the suction tank 105 of the pipe 104 is disposed on the upper end side of the suction tank 105, and is exposed to the nitrogen gas atmosphere filled in the suction tank 105.
  • the heat exchange 103 includes a pipe 103a through which the heat medium B flows and a casing 103b that is formed so as to cover the pipe 103a and through which the heat medium A flows.
  • the heat medium A is heated in the evaporator 112 and a part thereof is evaporated.
  • the gaseous heat medium A heated to a high temperature passes through the conduit 124A and enters the heat exchanger 103.
  • the heat medium A is cooled by exchanging heat with the heat medium B flowing in the pipe 103a.
  • the heat medium A liquefied by this heat exchange flows through the pipe 124C and returns to the evaporator 112.
  • the gaseous heat medium A after the heat exchange flows through the pipe 124B, enters the condenser 123, and is cooled.
  • heat exchanger 103 Since heat exchanger 103 is arranged upstream of condenser 123 in the flow direction of heat medium A, heat medium B can be heated by heat medium A in a high temperature state. The heat exchange efficiency can be improved.
  • the heat medium A condenses in the condenser 123, the internal pressure in the condenser 123 tends to be lower than the internal pressure in the heat exchanger 103. For this reason, the heat medium A in the heat exchanger 10 3 is easily pulled toward the condenser 123, and the heat medium A circulates well in the secondary refrigerant circulation circuit 102. Then, the heat medium A cooled and liquefied in the condenser 123 passes through the pipe 125 and is supplied into the evaporator 112.
  • Heat medium B is heated by heat exchange with heat medium A in heat exchanger 103. Then, it circulates through the pipe 104 and enters the suction tank 105. Then, the gas contained in the heat medium B is separated in the suction tank 105.
  • the opening 104a of the pipe 104 is exposed in the gas atmosphere, the external pressure is not applied near the opening 104a. For this reason, the bubbles that have been displaced to the vicinity of the opening 104 a are discharged well into the succession tank 105. Thereby, bubbles and the like in the tertiary refrigerant circulation circuit 101 are separated in the suction tank 105.
  • the heat medium B flows toward the piezoelectric pump 108 through the pipe 107 connected to the lower end side of the suction tank 105.
  • the heat medium B is pressurized by the piezoelectric pump 108 and is discharged toward the dew condensation prevention pipe 110 and the drain water heating unit 111.
  • the heat medium B By causing the heat medium B to circulate in the dew condensation prevention pipe 110, the door packing contact portion and its vicinity in the freezing room and the refrigeration room are heated and the occurrence of dew is suppressed. Further, when the heat medium B flows through the drain water heating unit 111, the drain water is heated and evaporated. The heat medium B that has passed through the dew prevention pipe 110 and the drain water heating unit 111 is then supplied into the heat exchanger 103 and heated again.
  • FIG. 11 is a plan view showing another example of heat exchange ⁇ 103.
  • the heat exchange ⁇ 103 shown in FIG. 11 includes main pipes 134 and 135 arranged opposite to each other, a plurality of sub pipes 136 connecting the main pipes 134 and 135, and an inner pipe 132. Yes.
  • the inner pipe 132 is bent in a meandering manner so as to pass through each sub pipe 136.
  • the heat medium A heated in the evaporator 112 shown in FIG. 10 is supplied from the main pipe line 134 into the heat exchanger 103. Then, the heat medium A flows through the sub pipe 136 and flows from the main pipe 135 toward the condenser 123 shown in FIG.
  • the heat exchanger 103 since the heat exchanger 103 includes a plurality of sub-pipes 136 through which the heat medium A flows, a large distribution area of the heat medium A is secured. For this reason, the flow resistance of the heat medium A is reduced, and the heat medium A circulates in the heat exchanger 103 well.
  • the inner pipe 132 through which the heat medium B flows is arranged so as to pass through each sub-pipe 136.
  • the heat exchange between the heat medium A and the heat medium B is performed on the surface of the inner pipe 132 in the sub pipe 136, while the inner pipe 132 is disposed in the sub pipe 136, so that heat exchange is performed. Area to do Widely secured and heat exchange efficiency can be improved. Furthermore, since the heat medium A is distributed well, the heat exchange efficiency between the heat medium A and the heat medium B can be further improved.
  • FIG. 12 is a plan view showing still another example of the heat exchange ⁇ 103.
  • the heat exchange ⁇ 103 is composed of main pipes 134 and 135 arranged opposite to each other, a plurality of sub pipes 136 arranged between the main pipes 134 and 135, and a meander arranged on the surface of the sub pipe 136.
  • the meandering pipe 137 extends in a direction intersecting the sub-pipe 136 and is folded back on the sub-pipe 136 so as to have a meandering shape. For this reason, the contact area between the meandering pipe 137 and the auxiliary pipe 136 is secured widely.
  • the heat medium A also enters the heat exchanger 103 and the heat medium B circulates in the meandering pipe 137.
  • heat exchange between the heat medium A and the heat medium B is performed at the contact surface between the meandering pipe 137 and the sub pipe 136. Since such a heat exchanger 103 is formed by arranging the meandering pipe 137 on the surface of the sub pipe 136, it can be easily manufactured. Furthermore, by adjusting the shape of the meandering pipe 137 such as the number of bends, the contact area between the sub pipe 136 and the meandering pipe 137 can be adjusted, and the heat exchange efficiency between heat medium A and heat medium B is easy Can be adjusted.
  • heat exchange 103 and condenser 123 are sequentially arranged in the flow direction of heat medium A as shown in FIG. A circulation can be secured. Accordingly, the heat radiating portion 13a of the Stirling refrigerator 13 shown in FIG. 1 can be cooled well.
  • the heat exchange efficiency between the heat medium A and the heat medium B can be improved in the heat exchanger 103.
  • the heat exchange efficiency between the heat medium A and the heat medium B can be improved, the occurrence of dew generation can be suppressed well, and the drain water can be vaporized well.
  • the bubbles in the tertiary refrigerant circulation circuit 101 can be well separated in the suction tank 105.
  • Heat medium B can be circulated well.
  • the present invention is suitable for a Stirling refrigerator.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Removal Of Water From Condensation And Defrosting (AREA)

Abstract

Chambre de refroidissement de Sterling (100) ayant une machine de réfrigération de Sterling (13) avec une section d'émission thermique (13a) et une section d'absorption thermique (13b), une chambre de refroidissement refroidie par une chaleur froide de la section d'absorption thermique (13b), un circuit secondaire de circulation de réfrigérant destiné à refroidir la section d'émission thermique (13a), et un circuit tertiaire de circulation de réfrigérant destiné à échanger de la chaleur avec le circuit secondaire de circulation de réfrigérant.
PCT/JP2006/311478 2005-06-23 2006-06-08 Chambre de refroidissement de sterling Ceased WO2006137269A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/916,837 US20100018224A1 (en) 2005-06-23 2006-06-08 Stirling cooler

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-183808 2005-06-23
JP2005183808A JP4001607B2 (ja) 2005-01-04 2005-06-23 スターリング冷却庫

Publications (1)

Publication Number Publication Date
WO2006137269A1 true WO2006137269A1 (fr) 2006-12-28

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PCT/JP2006/311478 Ceased WO2006137269A1 (fr) 2005-06-23 2006-06-08 Chambre de refroidissement de sterling

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US (1) US20100018224A1 (fr)
CN (1) CN100549560C (fr)
WO (1) WO2006137269A1 (fr)

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EP2283289A2 (fr) * 2008-05-23 2011-02-16 Aktiebolaget Electrolux Dispositif réfrigérant
JP6326708B2 (ja) * 2015-05-14 2018-05-23 Ｐｈｃホールディングス株式会社 冷凍装置
US10260819B2 (en) * 2016-07-26 2019-04-16 Tokitae Llc Thermosiphons for use with temperature-regulated storage devices
CN106500386B (zh) * 2016-12-28 2022-12-30 宁波华斯特林电机制造有限公司 基于斯特林电机的冷却装置
CN106762207B (zh) * 2016-12-28 2019-01-01 宁波华斯特林电机制造有限公司 一种带除霜单元的斯特林电机
CN106762212B (zh) * 2017-01-03 2019-02-26 宁波华斯特林电机制造有限公司 一种斯特林电机及除霜单元
WO2019231017A1 (fr) * 2018-05-31 2019-12-05 삼성전자주식회사 Dispositif de distribution d'eau en circulation et système de distribution d'eau en circulation doté dudit dispositif
CN113237246B (zh) * 2021-04-15 2022-01-14 成都仙德科技有限公司 一种斯特林制冷制热一体机
CN115727562B (zh) * 2022-11-28 2025-09-12 中车长春轨道客车股份有限公司 一种制冷系统

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JP2003279219A (ja) * 2002-03-20 2003-10-02 Mitsubishi Electric Corp 冷凍冷蔵庫
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JPH10148411A (ja) * 1996-11-15 1998-06-02 Sanyo Electric Co Ltd スターリング冷凍装置
JP3746496B2 (ja) * 2003-06-23 2006-02-15 シャープ株式会社 冷蔵庫
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JP2001033140A (ja) * 1999-07-22 2001-02-09 Sharp Corp スターリング冷蔵庫
JP2003050073A (ja) * 2001-08-03 2003-02-21 Sharp Corp スターリング冷凍システム及びスターリング冷蔵庫
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JP2004020056A (ja) * 2002-06-17 2004-01-22 Sharp Corp 冷却庫

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US20100018224A1 (en) 2010-01-28
CN101208566A (zh) 2008-06-25

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