WO2021246137A1 - 二元冷凍装置 - Google Patents

二元冷凍装置 Download PDF

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Publication number
WO2021246137A1
WO2021246137A1 PCT/JP2021/018389 JP2021018389W WO2021246137A1 WO 2021246137 A1 WO2021246137 A1 WO 2021246137A1 JP 2021018389 W JP2021018389 W JP 2021018389W WO 2021246137 A1 WO2021246137 A1 WO 2021246137A1
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WO
WIPO (PCT)
Prior art keywords
temperature side
heat exchanger
low temperature
tube
low
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/JP2021/018389
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
峻 豊岡
稔 須藤
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.)
PHC Holdings Corp
Original Assignee
PHC Holdings 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
Application filed by PHC Holdings Corp filed Critical PHC Holdings Corp
Priority to EP21816648.6A priority Critical patent/EP4137754B1/en
Priority to CN202180038693.1A priority patent/CN115667816A/zh
Priority to JP2022528511A priority patent/JP7393543B2/ja
Publication of WO2021246137A1 publication Critical patent/WO2021246137A1/ja
Priority to US18/072,247 priority patent/US12326285B2/en
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
    • 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
    • F25B39/00—Evaporators; Condensers
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0037—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Definitions

  • This disclosure relates to a dual refrigeration system.
  • Patent Document 1 discloses a dual refrigeration circuit including a cascade capacitor in which a high temperature side refrigerant flowing through a high temperature side refrigeration circuit and a low temperature side refrigerant flowing through a low temperature side refrigeration circuit exchange heat.
  • the cascade capacitor of Patent Document 1 is a plate heat exchanger.
  • the present disclosure is to solve the above-mentioned conventional problems, and an object of the present disclosure is to provide a dual refrigeration circuit capable of improving the efficiency of heat exchange in a plate heat exchanger.
  • the dual refrigerating apparatus in the present disclosure is formed in a tubular shape having a wavy cross-sectional shape cut by a plane orthogonal to the axis, and the low temperature side flowing out of the low temperature side compressor.
  • It includes a low-temperature side refrigeration circuit having a double-tube heat exchanger with an inflowing outer tube, and a high-temperature side refrigeration circuit in which a high-temperature side refrigerant that exchanges heat with a low-temperature side refrigerant via a plate heat exchanger circulates. ..
  • the efficiency of heat exchange in the plate heat exchanger can be improved.
  • FIG. 7 It is a schematic diagram of the dual refrigerating apparatus in the 1st Embodiment of this disclosure. It is a perspective view of the plate type heat exchanger shown in FIG. It is a figure which shows the structure of the heat exchange unit in 1st Embodiment. It is a figure which shows the arrangement of the equipment which comprises the heat exchange unit shown in FIG. It is a schematic diagram of the freezer in which the dual refrigerating apparatus shown in FIG. 1 is used. It is a partially enlarged sectional view of the rear side wall of the box body shown in FIG. It is a schematic diagram of the dual refrigerating apparatus in the 2nd Embodiment of this disclosure. It is sectional drawing of the double tube type heat exchanger shown in FIG. 7.
  • FIG. It is a perspective view which shows the outline of the multi-leaf tube shown in FIG. It is a figure which shows the structure of the heat exchange unit in 2nd Embodiment. It is a figure which shows the arrangement of the apparatus which constitutes the heat exchange unit of the dual refrigerating apparatus in one modification of 1st Embodiment of this disclosure. It is a schematic diagram of the dual refrigerating apparatus in another modification of 1st Embodiment of this disclosure. It is a figure which shows the structure of the heat exchange unit in the dual refrigerating apparatus shown in FIG. It is a perspective view which shows the outline of the multi-leaf tube of the double tube type heat exchanger in the modification of the 2nd Embodiment of this disclosure.
  • the dual refrigerating apparatus 1 is provided in, for example, a freezer 2 (FIG. 5) such as an ultra-low temperature freezer in which the internal temperature of the storage is ⁇ 80 ° C. or lower.
  • a freezer 2 such as an ultra-low temperature freezer in which the internal temperature of the storage is ⁇ 80 ° C. or lower.
  • the dual refrigeration apparatus 1 includes a high temperature side refrigeration circuit 10 and a low temperature side refrigeration circuit 20.
  • the high temperature side refrigeration circuit 10 includes a high temperature side compressor 11, a high temperature side condenser 12, a high temperature side dryer 13, a high temperature side decompressor 14, a high temperature side evaporator 15, a liquid receiver 16 and a high temperature side heat exchanger 17. ing.
  • the high temperature side heat exchanger 17 is composed of a double tube.
  • the inner tube of the high temperature side heat exchanger 17 is the high temperature side decompressor 14.
  • the high temperature side evaporator 15 constitutes a plate type heat exchanger 30, which will be described later.
  • the liquid receiver 16 is formed in a cylindrical shape.
  • Each of the above-mentioned devices is connected by the high temperature side pipe 18 so that the high temperature side refrigerant discharged from the high temperature side compressor 11 returns to the high temperature side compressor 11 again.
  • the high temperature side pipe 18 is an example of “piping”.
  • the high temperature side refrigerant circulates in the direction of the arrow shown in FIG. Specifically, the high-temperature side refrigerants are the high-temperature side compressor 11, the high-temperature side condenser 12, the high-temperature side dryer 13, the high-temperature side decompressor 14, the high-temperature side evaporator 15, the liquid receiver 16 and the high-temperature side heat exchanger. It flows through the outer pipe 17a of 17 in this order and returns to the high temperature side compressor 11.
  • the low temperature side refrigeration circuit 20 includes a low temperature side compressor 21, a spiral heat exchanger 22, a low temperature side condenser 23, a low temperature side dryer 24, a low temperature side decompressor 25, a low temperature side evaporator 26, and a low temperature side heat exchanger 27. It is equipped with.
  • the low temperature side dryer 24 is an example of a “dryer”.
  • the low temperature side dryer 24 is formed in a cylindrical shape.
  • the spiral heat exchanger 22 includes a main body tube 22a and a spiral tube 22b.
  • the main body tube 22a is formed in a cylindrical shape through which the low temperature side refrigerant flows.
  • the main body tube 22a is arranged so that the direction of the axis of the main body tube 22a is along the vertical direction.
  • the spiral tube 22b is spirally wound around the main body tube 22a so that the low temperature side refrigerant flows from the upper side to the lower side of the main body tube 22a.
  • the spiral tube 22b has a rectangular cross section.
  • the low temperature side heat exchanger 27 is composed of a double tube.
  • the inner tube of the low temperature side heat exchanger 27 is the low temperature side decompressor 25.
  • the low temperature side condenser 23 constitutes a plate type heat exchanger 30, which will be described later.
  • Each of the above-mentioned devices is connected by a low temperature side pipe 28 so that the low temperature side refrigerant discharged from the low temperature side compressor 21 returns to the low temperature side compressor 21 again.
  • the low temperature side pipe 28 is an example of “pipe”.
  • the low temperature side refrigerant circulates in the direction of the arrow shown in FIG. Specifically, the low temperature side refrigerant is the low temperature side compressor 21, the spiral tube 22b, the low temperature side condenser 23, the low temperature side dryer 24, the low temperature side decompressor 25, the low temperature side evaporator 26, and the low temperature side heat exchanger 27. It flows through the outer tube 27a and the main body tube 22a in this order, and returns to the low temperature side compressor 21.
  • an ultra-low temperature of ⁇ 80 ° C. or lower can be obtained in the low temperature side evaporator 26.
  • the plate heat exchanger 30 In the plate heat exchanger 30, the high temperature side refrigerant flowing through the high temperature side evaporator 15 and the low temperature side refrigerant flowing through the low temperature side condenser 23 exchange heat. As shown in FIG. 2, the plate heat exchanger 30 is formed in a rectangular parallelepiped shape.
  • the plate heat exchanger 30 includes a plurality of heat transfer plates 31 and a cover plate 32.
  • the heat transfer plate 31 and the cover plate 32 are plate members having a rectangular shape when viewed from the front.
  • the heat transfer plate 31 is formed in a wavy cross section.
  • the plurality of heat transfer plates 31 are laminated at a predetermined distance so that a flow path through which one of the high temperature side refrigerant and the low temperature side refrigerant flows is formed between the heat transfer plates 31 adjacent to each other.
  • the high temperature side flow path (not shown) through which the high temperature side refrigerant flows and the low temperature side flow path (not shown) of the low temperature side refrigerant are formed so as to be adjacent to each other with one heat transfer plate 31 interposed therebetween. That is, the high temperature side flow path and the low temperature side flow path are alternately arranged in the stacking direction of the plurality of heat transfer plates 31.
  • cover plates 32 are arranged at both ends of the stack of the plurality of heat transfer plates 31.
  • the high temperature side inflow section 33 into which the high temperature side refrigerant flows in On the plate surface of one of the cover plates 32, the high temperature side inflow section 33 into which the high temperature side refrigerant flows in, the high temperature side outflow section 34 in which the high temperature side refrigerant flows out, the low temperature side inflow section 35 in which the low temperature side refrigerant flows in, and the low temperature side outflow section.
  • the unit 36 is arranged.
  • the plate surface of the cover plate 32 on which the high temperature side inflow portion 33 and the like are arranged is referred to as the first surface 30a of the plate heat exchanger 30.
  • the high temperature side refrigerant flowing in from the high temperature side inflow section 33 flows through the high temperature side flow path and flows out from the high temperature side outflow section 34.
  • the low temperature side refrigerant flowing in from the low temperature side inflow section 35 flows through the low temperature side flow path and flows out from the low temperature side outflow section 36.
  • the high temperature side refrigerant and the low temperature side refrigerant exchange heat via the heat transfer plate 31. Further, since the heat transfer plate 31 is formed in a wavy cross section, the flow of the high temperature side refrigerant and the flow of the low temperature side refrigerant become turbulent, so that the heat exchange between the high temperature side refrigerant and the low temperature side refrigerant is relatively small. It is done efficiently.
  • FIGS. 3 and 4 a part of the equipment constituting the dual refrigerating apparatus 1 constitutes the heat exchange unit 40 shown in FIGS. 3 and 4.
  • the upper side and the lower side in FIG. 3 are the upper side and the lower side of the heat exchange unit 40, respectively, and the left side and the right side are the left side and the right side of the heat exchange unit 40, respectively.
  • the sides will be described as front and rear of the heat exchange unit 40, respectively.
  • the heat exchange unit 40 includes a plate heat exchanger 30, a high temperature side heat exchanger 17, a liquid receiver 16, a spiral heat exchanger 22, a low temperature side dryer 24, and a low temperature side heat exchanger 27. ..
  • the plate heat exchanger 30 is arranged so that the longitudinal direction is along the vertical direction and the first surface 30a faces forward.
  • the high temperature side heat exchanger 17 is arranged on the right side of the plate heat exchanger 30.
  • the liquid receiver 16 is arranged between the plate heat exchanger 30 and the high temperature side heat exchanger 17 so that the longitudinal direction is along the vertical direction.
  • the spiral heat exchanger 22 is arranged between the liquid receiver 16 and the high temperature side heat exchanger 17 so that the axis of the main body tube 22a is along the vertical direction.
  • the low temperature side dryer 24 is arranged on the left side of the plate heat exchanger 30 so that the longitudinal direction is along the vertical direction.
  • the low temperature side heat exchanger 27 is arranged on the left side of the low temperature side dryer 24.
  • the heat exchange unit 40 includes a part of the high temperature side pipe 18 and a part of the low temperature side pipe 28 connected to the above-mentioned components, respectively.
  • the high temperature side pipe 18 is the first to fifth high temperature side pipes 18a to 18e.
  • the first high temperature side pipe 18a is a pipe connecting the high temperature side inflow portion 33 of the plate type heat exchanger 30 and the inner pipe (high temperature side decompressor 14) of the high temperature side heat exchanger 17.
  • the second high temperature side pipe 18b is a portion of the pipe connecting the inner pipe of the high temperature side heat exchanger 17 and the high temperature side condenser 12 on the high temperature side heat exchanger 17 side.
  • the third and fourth high temperature side pipes 18c and 18d are pipes connected to the liquid receiver 16.
  • the fifth high temperature side pipe 18e is a portion of the pipe connecting the outer pipe 17a of the high temperature side heat exchanger 17 and the high temperature side compressor 11 on the outer pipe 17a side of the high temperature side heat exchanger 17.
  • a part of the low temperature side pipe 28 is the first to eighth low temperature side pipes 28a to 28h.
  • the first low temperature side pipe 28a is a pipe connecting the low temperature side inflow portion 35 of the plate heat exchanger 30 and the spiral pipe 22b.
  • the second low temperature side pipe 28b is a portion of the pipe connecting the spiral pipe 22b and the low temperature side compressor 21 on the spiral pipe 22b side.
  • the third and fourth low temperature side pipes 28c and 28d are pipes connected to the low temperature side dryer 24.
  • the fifth and sixth low temperature side pipes 28e and 28f are portions on the low temperature side heat exchanger 27 side of the pipe connecting the low temperature side heat exchanger 27 and the low temperature side evaporator 26.
  • the seventh low temperature side pipe 28g is a pipe connecting the outer pipe 27a of the low temperature side heat exchanger 27 and the main body pipe 22a.
  • the eighth low temperature side pipe 28h is a portion of the pipe connecting the main body pipe 22a and the low temperature side compressor 21 on the main body pipe 22a side.
  • the heat exchange unit 40 is formed so that the length A in a predetermined direction is suppressed.
  • the predetermined direction is a direction perpendicular to the vertical direction.
  • the predetermined direction is a direction orthogonal to the first surface 30a, that is, a front-rear direction.
  • the length A in the predetermined direction is, for example, a pipe connected from the second surface 30b opposite to the first surface 30a of the plate heat exchanger 30 to the high temperature side inflow portion 33 arranged on the first surface 30a. Is the length to the front end in.
  • the pipe connected to the plate heat exchanger 30 is bent so that the length A in a predetermined direction is suppressed.
  • the above-mentioned spiral heat exchanger 22 and the like are arranged, and a part of the high temperature side pipe 18 and a part of the low temperature side pipe 28 are routed.
  • the heat exchange unit 40 further includes a heat insulating member 40a that covers each component.
  • the heat insulating member 40a is formed of, for example, urethane foam.
  • the outer shape of the heat insulating member 40a is formed in a rectangular parallelepiped shape. A part of the high temperature side pipe 18 and the low temperature side pipe 28 are taken out from the lower side surface and the left side surface of the heat insulating member 40a.
  • the upper side and the lower side in FIG. 5 are the upper side and the lower side of the freezer 2, respectively, the upper left side and the lower right side are the front side and the rear side of the freezer 2, respectively, and the lower left side and the upper right side are the freezer 2 respectively. It will be described as the left side and the right side of.
  • the freezer 2 includes a box body 3 having an opening (not shown) formed on the front side, a door 4 that can open and close the opening of the box body 3, a lid member 5, and a machine room 6.
  • the box body 3 has a rear side wall 3a.
  • the rear side wall 3a is an example of a “side wall”.
  • the box body 3 has an inner box 3b made of an iron plate, an outer box 3c made of an iron plate arranged at intervals on the outside of the inner box 3b, and urethane foam, for example, between the inner box 3b and the outer box 3c. It has a heat insulating layer 3d formed by foam filling.
  • a storage portion 3d1 for accommodating the heat exchange unit 40 is formed on the rear side wall 3a. The storage portion 3d1 is formed so that the outer box 3c is opened and the heat insulating layer 3d is recessed.
  • the lid member 5 covers the storage portion 3d1.
  • the lid member 5 is detachably attached to the back surface of the box body 3.
  • the lid member 5 includes a cover panel 5a, a first sheet 5b, a heat insulating panel 5c, and a second sheet 5d.
  • the cover panel 5a is made of an iron plate having a rectangular shape when viewed from the front.
  • the cover panel 5a is formed with recesses 5a1 that are recessed from the front to the rear so that the first sheet 5b, the heat insulating panel 5c, and the second sheet 5d can be arranged inside.
  • a flange portion 5a2 is formed on the peripheral edge portion of the cover panel 5a so that the lid member 5 can be attached to the rear side wall 3a by, for example, a screw.
  • the first sheet 5b, the heat insulating panel 5c and the second sheet 5d are arranged in the recess 5a1 in this order.
  • the first sheet 5b is a flexible sheet made of, for example, polyethylene, and is adhered to the bottom surface of the recess 5a1.
  • the heat insulating panel 5c is, for example, a plate-shaped vacuum heat insulating material whose outer surface is sealed with a resin film, a metal film, or the like, and is adhered to the first sheet 5b.
  • the second sheet 5d is a flexible sheet made of, for example, polyethylene, and is adhered to the heat insulating panel 5c.
  • the heat exchange unit 40 is housed in the storage unit 3d1 so that the vertical direction of the heat exchange unit 40 faces the vertical direction of the freezer 2 and the front or rear of the heat exchange unit 40 faces the front of the freezer 2. ..
  • the machine room 6 is arranged so as to support the box body 3.
  • compressors 11 and 21, which form a part of the high temperature side refrigeration circuit 10 and the low temperature side refrigeration circuit 20 of the dual refrigeration apparatus 1, and condensers 12, 23 and the like are arranged.
  • the flow of the low-temperature side refrigerant in the spiral tube 22b of the spiral heat exchanger 22 will be described. As described above, the low temperature side refrigerant flowing out of the low temperature side compressor 21 flows into the spiral tube 22b.
  • the spiral tube 22b is wound from the upper side to the lower side of the main body tube 22a as described above (FIG. 3). Therefore, the low-temperature side refrigerant that has flowed into the spiral tube 22b flows downward in a spiral direction along the vertical direction. Due to the flow of the low temperature side refrigerant in this way, the flow of the low temperature side refrigerant becomes turbulent. Further, the length of the spiral tube 22b, the curvature of the spiral of the spiral tube 22b, and the number of turns of the spiral tube 22b are set so that turbulence is likely to occur. Further, the cross-sectional shape of the spiral tube 22b is formed in a rectangular shape in which turbulent flow is likely to occur. The low temperature side refrigerant whose flow has become turbulent flows into the plate heat exchanger 30.
  • the low temperature side refrigerant whose flow has become turbulent due to flowing through the spiral tube 22b flows into the plate heat exchanger 30.
  • the efficiency of heat exchange is improved as compared with the case of laminar flow. Therefore, the efficiency of heat exchange in the plate heat exchanger 30 is improved.
  • main body tube 22a is arranged so that the direction of the axis of the main body tube 22a is along the vertical direction. Further, the spiral tube 22b is wound so that the low temperature side refrigerant flows from the upper side to the lower side of the main body tube 22a.
  • the flow of the low temperature side refrigerant tends to be turbulent. Therefore, the efficiency of heat exchange in the plate heat exchanger 30 is further improved.
  • the portion of the spiral tube 22b through which the low-temperature side refrigerant flows is formed in a rectangular cross section.
  • the flow of the low temperature side refrigerant tends to be turbulent. Therefore, the efficiency of heat exchange in the plate heat exchanger 30 is further improved.
  • the heat exchange unit 40 is formed so that the length A in a predetermined direction is suppressed.
  • the plate heat exchanger 30 and the spiral heat exchanger 22 can be unitized so as to shorten the length A in the predetermined direction. Therefore, the degree of freedom in the layout of the heat exchange unit 40 can be improved.
  • the plate heat exchanger 30 is formed in a rectangular parallelepiped shape, and the high temperature side pipe 18 and the low temperature side pipe 28 are connected to the first surface 30a.
  • the predetermined direction is a direction orthogonal to the first surface 30a.
  • the length of the heat exchange unit 40 can be suppressed in the direction orthogonal to the first surface 30a.
  • the dual refrigerating apparatus 1 includes a liquid receiver 16 into which the high-temperature side refrigerant flowing out of the plate heat exchanger 30 flows in, and a low-temperature side dryer 24 in which the low-temperature side refrigerant flowing out of the plate heat exchanger 30 flows in. And, further equipped.
  • the heat exchange unit 40 further includes a liquid receiver 16 and a low temperature side dryer 24.
  • the heat exchange unit 40 includes the liquid receiver 16 and the low temperature side dryer 24, the length A in the predetermined direction can be suppressed.
  • the heat exchange unit 40 is covered with the heat insulating member 40a and is housed in the rear side wall 3a of the box body 3 in the freezer 2 in which the dual refrigerating device 1 is used.
  • the thermal effect on the heat exchange unit 40 by the components of the dual refrigerating device 1 housed in the machine room 6 is obtained. Can be suppressed.
  • the double tube heat exchanger 122 includes a multi-leaf tube 122a and an outer tube 122b.
  • the multi-leaf tube 122a is formed in a tubular shape having a wavy cross-sectional shape cut by a plane orthogonal to the axis line 122a1 (FIGS. 8 and 9).
  • the side wall of the multi-leaf tube 122a is formed so that the wave shape in which the mountain portion 122a2 and the valley portion 122a3 repeat in the circumferential direction extends straight along the direction of the axis 122a1 (FIGS. 8 and 9).
  • the first end of the multi-leaf pipe 122a is connected to the low temperature side compressor 21 via the second low temperature side pipe 28b (FIG. 10). Further, the second end of the multi-leaf pipe 122a is connected to the low temperature side inflow portion 35 of the plate heat exchanger 30 via the first low temperature side pipe 28a. That is, the low temperature side refrigerant flowing out of the low temperature side compressor 21 flows into the multi-leaf tube 122a. The low temperature side refrigerant flowing out of the multi-leaf pipe 122a flows into the low temperature side inflow portion 35 of the plate heat exchanger 30.
  • the outer tube 122b is formed in a tubular shape that accommodates the multi-leaf tube 122a inside (FIG. 8).
  • the first end of the outer pipe 122b is connected to the outer pipe 27a of the low temperature side heat exchanger 27 via the seventh low temperature side pipe 28g (FIG. 10). Further, the second end portion of the outer pipe 122b is connected to the low temperature side compressor 21 via the eighth low temperature side pipe 28h.
  • the low temperature side refrigerant flowing out from the outer pipe 27a of the low temperature side heat exchanger 27 flows into the outer pipe 122b.
  • the low temperature side refrigerant flowing into the outer pipe 122b flows between the inner peripheral surface of the outer pipe 122b and the outer peripheral surface of the multi-leaf pipe 122a.
  • the low temperature side refrigerant flowing out from the outer pipe 122b flows into the low temperature side compressor 21.
  • the double tube heat exchanger 122 In the double tube heat exchanger 122, the low temperature side refrigerant flowing through the multi-leaf tube 122a and the low temperature side refrigerant flowing through the outer tube 122b exchange heat. Since the multi-leaf tube 122a has a wavy cross-sectional shape as described above, the area of the outer surface of the multi-leaf tube 122a is larger than that of the case where the cross-sectional shape is circular. Therefore, the heat exchange in the double tube heat exchanger 122 is performed relatively efficiently. Further, in the heat exchange unit, the double tube heat exchanger 122 is arranged so that the axis line 122a1 of the multi-leaf tube 122a is along the vertical direction.
  • the dual refrigerating apparatus 1 is formed in a tubular shape having a wavy cross-sectional shape cut by a plane orthogonal to the axis line 122a1, and the low-temperature side refrigerant flowing out from the low-temperature side compressor 21.
  • the high temperature side refrigerating circuit 20 including the double tube type heat exchanger 122 having the outer tube 122b into which the side refrigerant flows, and the high temperature side refrigerant that exchanges heat with the low temperature side refrigerant via the plate type heat exchanger 30 circulate.
  • a side refrigeration circuit 10 is provided.
  • the inner pipe of the double-tube heat exchanger 122 is a multi-leaf pipe 122a
  • the flow of the low-temperature side refrigerant tends to be turbulent as compared with the case where the inner pipe is a cylindrical pipe. Therefore, the efficiency of heat exchange in the plate heat exchanger 30 is improved.
  • the inner tube of the double tube heat exchanger 122 is the multi-leaf tube 122a, heat exchange can be performed relatively efficiently. Therefore, the length of the multi-leaf tube 122a along the axis line 122a1 can be shortened to make the double-tube heat exchanger 122 compact.
  • the cross-sectional shape of the spiral tube 22b is rectangular, but instead of this, it may be circular.
  • the predetermined direction is the direction orthogonal to the first surface 30a, but instead of this, the width direction of the first surface 30a may be used.
  • the width direction of the first surface 30a is the front-rear direction when the first surface 30a of the plate heat exchanger 30 faces to the left.
  • the low temperature side dryer 24 is arranged on the left side of the plate heat exchanger 30.
  • the spiral heat exchanger 22 and the liquid receiver 16 are arranged on the right side of the plate heat exchanger 30.
  • the length of the low temperature side dryer 24, the spiral heat exchanger 22 and the liquid receiver 16 in the front-rear direction, and the routing of the low temperature side pipes 18 and 28 are within the width direction of the first surface 30a.
  • the length A in the predetermined direction corresponds to the length in the width direction of the first surface 30a.
  • the predetermined direction of the second embodiment may be the width direction of the first surface 30a instead of the direction orthogonal to the first surface 30a.
  • the heat exchange unit 40 includes a plate heat exchanger 30, a high temperature side heat exchanger 17, a liquid receiver 16, a spiral heat exchanger 22, a low temperature side dryer 24, and the like.
  • a low temperature side heat exchanger 27 is provided.
  • the heat exchange unit 40 may include at least a plate heat exchanger 30 and a spiral heat exchanger 22.
  • the heat exchange unit 40 does not have to include at least one of the high temperature side heat exchanger 17, the liquid receiver 16, the low temperature side dryer 24, and the low temperature side heat exchanger 27.
  • the heat exchange unit 40 of the second embodiment may be provided with at least a plate heat exchanger 30 and a double tube heat exchanger 122.
  • the heat insulating member 40a of the heat exchange unit 40 includes a plate heat exchanger 30, a high temperature side heat exchanger 17, a liquid receiver 16, a spiral heat exchanger 22, and a low temperature side dryer. It is formed so as to cover 24 and the low temperature side heat exchanger 27.
  • the heat insulating member 40a may not cover at least one of the high temperature side heat exchanger 17, the liquid receiver 16, the low temperature side dryer 24, and the low temperature side heat exchanger 27.
  • at least one of the high temperature side heat exchanger 17, the liquid receiver 16, the low temperature side dryer 24, and the low temperature side heat exchanger 27 You may not cover it.
  • the heat exchange unit 40 is housed in the rear side wall 3a of the box body 3, but instead, the heat exchange unit may be housed in another side wall of the box body 3.
  • the 40 is housed in, for example, the right side wall or the left side wall of the box body 3.
  • the heat exchange unit 40 is arranged so that the vertical direction of the heat exchange unit 40 is along the vertical direction of the freezer 2 and the front or rear of the heat exchange unit 40 faces the right or left of the freezer 2. It is stored in the right side wall and the left wall.
  • the low temperature side refrigeration circuit 20 includes the low temperature side heat exchanger 27, but instead of this, the low temperature side heat exchanger 27 may not be provided.
  • the low temperature side compressor is the low temperature side compressor 21, the spiral tube 22b, the low temperature side condenser 23, the low temperature side dryer 24, and the low temperature side. It flows through the side decompressor 25, the low temperature side evaporator 26, and the main body tube 22a in this order, and returns to the low temperature side compressor 21.
  • the low temperature side evaporator 26 and the main body pipe 22a are connected by the ninth low temperature side pipe 128i.
  • the low temperature side decompressor 25 is arranged on the left side of the plate type heat exchanger 30 and the low temperature side dryer 24, and the heat insulating member 40a is provided. It may not be covered with.
  • the ninth low temperature side pipe 128i connects the low temperature side evaporator 26 and the outer pipe 122b.
  • the high temperature side refrigeration circuit 10 includes the high temperature side heat exchanger 17 (FIG. 1), but instead of this, the high temperature side heat exchanger 17 does not have to be provided.
  • the high temperature side refrigerant is the high temperature side compressor 11, the high temperature side condenser 12, the high temperature side dryer 13, the high temperature side decompressor 14, the high temperature side evaporator 15, and the receiver.
  • the liquid vessel 16 flows in this order and returns to the high temperature side compressor 11.
  • the side wall of the multi-leaf tube 122a is formed so that the wave shape in which the mountain portion 122a2 and the valley portion 122a3 repeat in the circumferential direction extends straight along the axis line 122a1.
  • the side wall of the multi-leaf tube 222a may be formed in a spiral shape in which the wave shape swirls around the axis 222a1. As a result, the flow of the low-temperature side refrigerant in the multi-leaf pipe 222a is more likely to become turbulent.
  • the dual freezer of the present disclosure can be widely used in ultra-low temperature freezer and freezer.
  • Dual refrigeration system Freezer 3 Box body 3a Rear side wall (side wall) 3d1 Storage part 5 Cover member 5a Cover panel 5b 1st sheet 5c Insulation panel 5d 2nd sheet 10 High temperature side refrigeration circuit 16 Liquid receiver 18 High temperature side piping (piping) 20 Low temperature side refrigeration circuit 21 Low temperature side compressor 22 Spiral heat exchanger 22a Main body tube 22b Spiral tube 24 Low temperature side dryer (dryer) 28 Low temperature side piping (piping) 30 Plate heat exchanger 30a First surface 40 Heat exchange unit 40a Insulation member 122 Double tube heat exchanger 122a, 222a Multi-leaf tube 122a 1,222a1 Axis line 122b Outer tube

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2021/018389 2020-04-06 2021-05-14 二元冷凍装置 Ceased WO2021246137A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP21816648.6A EP4137754B1 (en) 2020-06-04 2021-05-14 Binary refrigeration device
CN202180038693.1A CN115667816A (zh) 2020-06-04 2021-05-14 二元冷冻装置
JP2022528511A JP7393543B2 (ja) 2020-06-04 2021-05-14 二元冷凍装置
US18/072,247 US12326285B2 (en) 2020-04-06 2022-11-30 Binary refrigeration apparatus

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JP2020097933 2020-06-04
JP2020-097933 2020-06-04

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CN117366894A (zh) * 2022-06-30 2024-01-09 青岛海尔特种电冰柜有限公司 复叠式压缩制冷系统、制冷装置及其控制方法
CN117366896A (zh) * 2022-06-30 2024-01-09 青岛海尔特种电冰柜有限公司 制冷系统、制冷装置及其控制方法

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CN117366896A (zh) * 2022-06-30 2024-01-09 青岛海尔特种电冰柜有限公司 制冷系统、制冷装置及其控制方法

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US12326285B2 (en) 2025-06-10
CN115667816A (zh) 2023-01-31
JPWO2021246137A1 (https=) 2021-12-09
EP4137754A4 (en) 2023-10-11
EP4137754A1 (en) 2023-02-22
JP7393543B2 (ja) 2023-12-06
EP4137754B1 (en) 2025-09-10

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