EP3742070B1 - Zyklonwärmerückgewinnungseinheit und wärmepumpensystem mit dieser zyklonwärmerückgewinnungseinheit - Google Patents

Zyklonwärmerückgewinnungseinheit und wärmepumpensystem mit dieser zyklonwärmerückgewinnungseinheit Download PDF

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Publication number
EP3742070B1
EP3742070B1 EP19741070.7A EP19741070A EP3742070B1 EP 3742070 B1 EP3742070 B1 EP 3742070B1 EP 19741070 A EP19741070 A EP 19741070A EP 3742070 B1 EP3742070 B1 EP 3742070B1
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EP
European Patent Office
Prior art keywords
refrigerant
fluid
cyclone
cooled
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.)
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Application number
EP19741070.7A
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English (en)
French (fr)
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EP3742070A1 (de
EP3742070A4 (de
Inventor
Hiroshi Yamaguchi
Haruhiko Yamasaki
Petter Neksaa
Kazuhiro Hattori
Takeshi Kamimura
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Mayekawa Manufacturing Co
Doshisha Co Ltd
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Mayekawa Manufacturing Co
Doshisha Co Ltd
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Publication of EP3742070A1 publication Critical patent/EP3742070A1/de
Publication of EP3742070A4 publication Critical patent/EP3742070A4/de
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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
    • F25D3/00—Devices using other cold materials; Devices using cold-storage bodies
    • F25D3/12—Devices using other cold materials; Devices using cold-storage bodies using solidified gases, e.g. carbon-dioxide snow
    • 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
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B9/02—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect
    • F25B9/04—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect using vortex effect
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • 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
    • F25D3/00—Devices using other cold materials; Devices using cold-storage bodies
    • F25D3/10—Devices using other cold materials; Devices using cold-storage bodies using liquefied gases, e.g. liquid air

Definitions

  • the present invention relates to a cyclone heat recovery unit and a cascade heat pump system provided with a cyclone refrigeration device or cyclone heat recovery unit.
  • This kind of refrigeration device comprises, for example, a compressor compressing CO 2 to saturation pressure or supercritical pressure at room temperature level, a condenser cooling and condensing the high pressure gas-phase CO 2 from the compressor, a CO 2 expansion device decompressing the condensed CO 2 to a pressure and temperature level below the triple point of CO 2 so as to transfer the condensed CO 2 into solid-gas two-phase CO 2 which is mixture of solid-phase CO 2 (dry ice) and gas-phase CO 2 (carbon dioxide gas), and a CO 2 sublimation means supplying heat due to sublimation of the solid-gas two-phase CO 2 to fluid to be cooled discharged from a cooling load and supplying the sublimated gas phase CO 2 to the compressor (see, for example, Patent Document 1).
  • the CO 2 sublimation means is a direct contact CO 2 sublimation device (see, Fig. 1 of Patent Document 1) or an indirect contact CO 2 sublimation device (see, Fig. 2 of Patent Document 1).
  • the solid-gas two-phase CO 2 is ejected into the brine stored in a reservoir, and the solid-gas two-phase CO 2 is sublimated by heat of the brine, and the brine is cooled by this sublimation, and the cooled brine exchanges heat with the fluid to be cooled which is discharged from the cooling load.
  • the fluid to be cooled which is discharged from the cooling load flows into many cooling tubes arranged in parallel while the solid-gas two-phase CO 2 supplied from the CO 2 expansion device flows into a CO 2 passage provided between the cooling tubes, so that the solid-gas two-phase CO 2 is sublimated by heat of the fluid to be cooled in the cooling tubes and the fluid to be cooled is cooled to very low temperature by this sublimation.
  • this refrigeration device uses the latent heat of the solid-phase CO 2 in the solid-gas two-phase state, but this refrigeration device has a drawback that the cooling capacity thereof is inferior to the case where the heat of sublimation of only the solid-phase CO 2 is used.
  • Patent Document 1 JP 2004-308972 A .
  • US 4224801A1 (Tyree, JR. ), which describes a refrigeration apparatus and method of refrigerating material using stored cryogenic refrigeration
  • EP 2656741 A2 (Messer ), which describes an apparatus and method for cooling products.
  • an object of the present invention to provide refrigeration device that has a high cooling capacity and can be smoothly and continuously operated.
  • the present invention provides a cyclone heat recovery unit according to claim 1, comprising a cyclone refrigeration device comprising: a cylindrical portion vertically extending and closed at a top end thereof; an exhaust pipe whose radius is smaller than the radius of the cylindrical portion connected coaxially to the top end of the cylindrical portion in fluid connection with an interior space of the cylindrical portion and extended upward from the top end of the cylindrical portion; a cooling portion connected to a bottom end of the cylindrical portion and provided with a cavity which communicates with the interior space of the cylindrical portion, the cylindrical portion having a refrigerant inlet at an upper portion of a side wall thereof; a refrigerant inflow pipe connected to the refrigerant inlet at one end thereof and receiving a supply of liquid-phase refrigerant compressed under high pressure at the other end thereof; and a first decompression unit provided in the refrigerant inflow pipe, wherein the liquid-phase refrigerant supplied to the refrigerant inflow pipe is decompressed to form solid-gas two-phase refrig
  • the first heat exchanger consists of a container made of heat conductor, the container having a fluid outlet and a fluid inlet and filled with the fluid to be cooled, wherein the circulation pipeline for fluid to be cooled consists of a discharge line for fluid to be cooled connected to the fluid outlet of the container at one end thereof and projecting from the container to the outside of the cooling portion, and a supply line for fluid to be cooled connected to the fluid inlet of the container at one end thereof and projecting from the container to the outside of the cooling portion, wherein the other end of the discharge line for fluid to be cooled and the other end of the supply line for fluid to be cooled are connected to each other through the cooling load, and the pump is provided in the discharge line for fluid to be cooled or the supply line for fluid to be cooled.
  • the cyclone refrigeration device further comprises a vortex flow control body arranged across the interior space of the cylindrical portion and the cavity of the cooling portion, the vortex flow control body having a columnar bottom portion, a frustoconical middle portion connecting to a top surface of the bottom portion and tapering upward from the bottom portion, and a columnar top portion connecting to a top surface of the middle portion and extending upward from the middle portion, wherein the vortex flow control body is provided with an axial through hole with circular cross section therein, the second vortex flow flowing into the through hole, the through hole spreading out toward the top surface of the vortex flow control body after tapering upward from the bottom surface of the vortex flow control body, wherein the vortex flow control body is supported coaxially to the cylindrical portion by the cooling portion and/or the cylindrical portion in a manner such that the bottom portion is located within the cavity and the middle portion across the cavity and the interior space and a certain space is formed under the bottom surface of the vortex control body.
  • the interior space of the cylindrical portion is tapered downward.
  • the refrigerant is carbon dioxide or water or ammonia.
  • the present invention further provides a cascade heat pump system comprising a low-temperature side cycle and a high-temperature side cycle, wherein the low-temperature side cycle consists of the above cyclone heat recovery unit, and the second heat exchanger of the cyclone heat recovery unit forms a low-temperature side heat exchanger of a cascade heat exchanger.
  • the high-temperature side cycle includes a high-temperature side heat exchanger pairing with the second heat exchanger of the cyclone heat recovery unit to form the cascade heat exchanger; a high-temperature side refrigerant circulation pipe extending between an exit and an entrance of the high-temperature side heat exchanger; a second compressor provided downstream of the high-temperature side heat exchanger in the high-temperature side refrigerant circulation pipe; third and fourth condensers provided in series downstream of the second compressor in the high-temperature side refrigerant circulation pipe; and a third decompression unit provided downstream of the third and fourth condensers in the high-temperature side refrigerant circulation pipe.
  • the liquid-phase refrigerant condensed under high pressure is decompressed into the solid-gas two-phase refrigerant, and the solid-gas two-phase refrigerant flows downward into the interior space of the cylindrical portion while forming the first vortex flow and separating into the solid-phase refrigerant and the gas-phase refrigerant.
  • the solid-phase refrigerant deposits in the cavity of the cooling portion on the one hand and the gas-phase refrigerant forms a second vortex flow rising from the bottom of the cavity through the inside space of the first vortex flow to flow out through the exhaust pipe on the other hand.
  • the solid-phase refrigerant is prevented from adhering to and depositing in a refrigerant flow passage to block the refrigerant flow passage during operation of the refrigeration device.
  • a flow passage for the fluid to be cooled is separated from the solid-phase refrigerant by circulating the fluid to be cooled in the circulation pipeline for fluid to be cooled and exchanging heat between the fluid to be cooled and the solid-phase refrigerant deposited in the cavity, and accordingly, the solid-phase refrigerant is prevented from adhering to and depositing in a flow passage for the fluid to be cooled to block the flow passage for the fluid to be cooled during operation of the refrigeration device.
  • the cooling capacity of the refrigeration device is greatly improved, compared with the conventional refrigeration device using the latent heat of the solid-phase refrigerant in the solid-gas two-phase state.
  • Fig. 1 is a front view schematically illustrating a configuration of a cyclone refrigeration device according to an embodiment of the present invention.
  • the cyclone refrigeration device of the cyclone heat recovery unit of the present invention comprises a cylindrical portion 1 extending vertically, an inner flange 2 provided at a top opening 1a of the cylindrical portion 1, an exhaust pipe 3 whose outer diameter corresponds to an opening diameter of the inner flange connected to the inner flange 2 at one end thereof in a manner such that the exhaust pipe protrudes upward from and coaxially with the top opening 1a of the cylindrical portion 1.
  • a structure of connecting the cylindrical portion 1 and the exhaust pipe 3 is not limited to this embodiment, and the connection may have any structure as long as the cylindrical portion vertically extends and is closed at a top end thereof and the exhaust pipe whose radius is smaller than the radius of the cylindrical portion is connected coaxially to the top end of the cylindrical portion and extended upward from the top end of the cylindrical portion.
  • an interior space 1b of the cylindrical portion 1 is tapered downward (the interior space 1b is formed so that inner diameter thereof gradually decreases downward), the inner diameter of the interior space 1b may be constant.
  • a cooling portion 4 is connected to a bottom end of the cylindrical portion 1 and provided with a cavity 4a which communicates with the interior space 1b of the cylindrical portion 1.
  • the cylindrical portion 1 has a refrigerant inlet 1c at an upper portion of a side wall thereof.
  • the refrigerant inlet 1c preferably extends tangentially to a cross section of the cylindrical portion 1.
  • a refrigerant inflow pipe 5 is connected to the refrigerant inlet 1c of the cylindrical portion 1 at one end 5a thereof.
  • the refrigerant inflow pipe 5 receives supply of liquid-phase refrigerant condensed under high pressure at the other end 5b thereof.
  • An expansion valve (decompression unit) 6 is provided in the refrigerant inflow pipe 5.
  • a tank G as a supply source of liquid-phase refrigerant is connected to the other end 5b of the refrigerant inflow pipe 5.
  • liquid-phase refrigerant supplied to the refrigerant inflow pipe 5 is decompressed to form solid-gas two-phase refrigerant by the expansion valve 6, and the solid-gas two-phase refrigerant flows into the interior space 1b of the cylindrical portion 1 through the refrigerant inlet 1c and flows downward along an inner wall surface of the interior space 1b to form a first vortex flow.
  • the pressure outside the first vortex flow is greater than the pressure inside the first vortex flow, and this pressure difference between the outside and inside of the first vortex flow decreases from top to the bottom of the interior space 1b.
  • the first vortex flow extends from the refrigerant inlet 1c of the cylindrical portion 1 to the cavity 4a of the cooling portion 4 and is maintained as it is.
  • the solid-gas two-phase refrigerant is separated from a solid-phase refrigerant S and a gas-phase refrigerant by the formation of the first vortex flow, and the solid-phase refrigerant S is deposited in the cavity 4a.
  • the gas-phase refrigerant reaches the bottom of the cavity 4a, where the pressure difference between the outside and the inside of the first vortex flow is small so that the gas-phase refrigerant forms a second vortex flow rising through an inside space of the first vortex flow descending into the interior space 1b and flows out through the exhaust pipe 3.
  • the refrigerant used in the present invention can be maintained at pressure and temperature levels below the triple point thereof inside the refrigeration device.
  • a refrigerant satisfying this condition for example, carbon dioxide (CO 2 ), water, ammonia and so on can be listed.
  • the refrigeration device of the cyclone heat recovery unit of the present invention also comprises a circulation pipeline for fluid to be cooled 7 extending through the cavity 4a of the cooling portion 4. Both ends of the circulation pipeline for fluid to be cooled 7 are connected to each other outside the cooling portion 4, and the fluid to be cooled from a cooling load 9 flows in the circulation pipeline for fluid to be cooled 7.
  • a heat exchanger 8 is provided in a portion of the circulation pipeline for fluid to be cooled 7 which is located within the cavity 4. The heat exchanger 8 performs heat exchange between the solid-phase refrigerant deposited in the cavity 4a and the fluid to be cooled.
  • the heat exchanger 8 consists of a container made of heat conductor, the container having a fluid outlet 8a and a fluid inlet 8b and filled with the fluid to be cooled.
  • the container (heat exchanger) 8 is preferably made of a metal such as aluminum that has high thermal conductivity and is not easily affected by corrosion by the fluid to be cooled.
  • the circulation pipeline for fluid to be cooled 7 consists of a discharge line for fluid to be cooled 7a connected to the fluid outlet 8a of the container (heat exchanger) 8 at one end thereof and projecting from the container 8 to the outside of the cooling portion 4 through the cavity 4a, and a supply line for fluid to be cooled 7b connected to the fluid inlet 8b of the container 8 at one end thereof and projecting from the container 8 to the outside of the cooling portion 4 through the cavity 4a.
  • the other end of the discharge line for fluid to be cooled 7a and the other end of the supply line for fluid to be cooled 7b are connected to each other through the cooling load 9.
  • a pump 10 is provided in the discharge line for fluid to be cooled 7a or the supply line for fluid to be cooled 7b.
  • the fluid to be cooled is circulated by the pump 10 in the order of the container (heat exchanger) 8 -> the discharge line for fluid to be cooled 7a -> the cooling load 9 -> the supply line for fluid to be cooled 7b -> the container (heat exchanger) 8.
  • liquid-phase refrigerant condensed under high pressure is decompressed to form solid-gas two-phase refrigerant, and the solid-gas two-phase refrigerant flows downward into the interior space 1a of the cylindrical portion 1 while forming the first vortex flow and separating into the solid-phase refrigerant S and the gas-phase refrigerant.
  • the solid-phase refrigerant S deposits in the cavity 4a of the cooling portion 4 on the one hand and the gas-phase refrigerant forms a second vortex flow rising from the bottom of the cavity 4a through the inside space of the first vortex flow to flow out through the exhaust pipe 3 on the other hand.
  • the solid-phase refrigerant S deposited in the cavity 4a is sublimated by the heat of the fluid to be cooled which is filled in the container (heat exchanger) 8, and the sublimation heat is supplied to the fluid to be cooled so that the cooled fluid to be cooled is supplied to the cooling load 9 through the discharge line for fluid to be cooled 7a.
  • the descending vortex flow (first vortex flow) of the solid-gas two-phase refrigerant is generated in the interior space 1b of the cylindrical portion 1 so that the solid-gas two-phase refrigerant is separated into the solid-phase refrigerant S and the gas-phase refrigerant. Then the solid-phase refrigerant S deposits in the cavity 4a of the cooling portion 4, while the gas-phase refrigerant flows upward through the inside space of the descending vortex flow (first vortex flow) to flow out through the exhaust pipe 3. Thereby the solid-phase refrigerant S is prevented from adhering to and depositing in a refrigerant flow passage to block the refrigerant flow passage during operation of the refrigeration device.
  • a flow passage for the fluid to be cooled is separated from the solid-phase refrigerant S by circulating the fluid to be cooled in the circulation pipeline for fluid to be cooled 7 and exchanging heat between the fluid to be cooled and the solid-phase refrigerant S deposited in the cavity 4a, and accordingly, the solid-phase refrigerant S is prevented from adhering to and depositing in a flow passage for the fluid to be cooled to block the flow passage for the fluid to be cooled during operation of the refrigeration device.
  • the cooling capacity of the refrigeration device is greatly improved, compared with the conventional refrigeration device using the latent heat of the solid-phase refrigerant in the solid-gas two-phase state.
  • Fig. 2 is a view similar to Fig. 1 schematically illustrating a configuration of a cyclone refrigeration device of the cyclone heat recovery unit according to another embodiment of the present invention.
  • Fig. 2 differs from the embodiment of Fig. 1 only in that a structure for controlling the vortex flows is provided over the interior space 1b of the cylindrical portion 1 and the cavity 4a of the cooling portion 4. Therefore, in Fig. 2 , the same structural elements as those shown in Fig. 1 are designated by the same reference numerals and the detailed description of them will be omitted in the following.
  • a vortex control body 11 is arranged across the interior space 1b of the cylindrical portion 1 and the cavity 4b of the cooling portion 4 and extends vertically.
  • the vortex flow control body 11 has a columnar bottom portion 11a, a frustoconical middle portion 11b connecting to a top surface of the bottom portion 11a and tapering upward from the bottom portion 11a, and a columnar top portion 11c connecting to a top surface of the middle portion 11b and extending upward from the middle portion 11b.
  • the vortex flow control body 11 is provided with an axial through hole 12 with circular cross section therein, and the second vortex flow flows into the through hole 12.
  • the through hole 12 tapers upward from a bottom surface 11e of the vortex flow control body 11 and then spreads out toward a top surface 11d of the vortex flow control body 11.
  • the through hole 12 functions as a diffuser.
  • the vortex flow control body 11 is supported coaxially to the cylindrical portion 1 by the cooling portion 4 and/or the cylindrical portion 1 through an appropriate support member (not shown) in a manner such that the bottom portion 11a is located within the cavity 4a and the middle portion 11b across the cavity 4a and the cylindrical portion 1 and a certain space is formed under the bottom surface 11e of the vortex control body 11.
  • the first vortex flow of the solid-gas two-phase refrigerant descending outside of the vortex control body 11 while the second vortex flow of the gas-phase refrigerant separated from the solid-gas two-phase refrigerant passes upward through the through hole 12 of the vortex flow control body 11 and pressurized by the diffuser function of the through hole during passage of the through hole.
  • the vortex flow control body 11 facilitates inward movement of the gas-phase refrigerant in the first vortex flow at the bottom of the interior space 1b and the cavity 4a and makes the second vortex flow of the gas-phase refrigerant more stable and stronger.
  • Fig. 3 is a view schematically illustrating a configuration of a heat pump system, not falling within the scope of the claims, into which the cyclone refrigeration device of Fig. 1 as an evaporator is incorporated.
  • the same structural elements as those shown in Fig. 1 are designated by the same reference numerals and the detailed description of them will be omitted in the following.
  • the heat pump system 16 comprises the cyclone refrigeration device shown in Fig. 1 , and a refrigerant circulation pipe 15 connecting an exit of the exhaust pipe 3 of the cyclone refrigeration device and the other end 5b of refrigerant inflow pipe 5.
  • the heat pump system 16 further comprises a compressor 13 provided in the refrigerant circulation pipe 15 to compress the gas-phase refrigerant exhausted from the exhaust pipe 3 of the cyclone refrigeration device, and a condenser 14 arranged downstream of the compressor 13 in the refrigerant circulation pipe 15 to condense the gas-phase refrigerant compressed by the compressor 13 into the liquid-phase refrigerant.
  • Fig. 4 is a Mollier diagram of the heat pump system 16 when CO 2 is used as a refrigerant.
  • a gas-phase CO 2 taken into the compressor 13 through the refrigerant circulation pipe 15 is compressed by the compressor 13 (D -> A in Fig. 4 ) to form high-pressure gas-phase CO 2 , and the high-pressure gas-phase CO 2 is supplied to the condenser 14 through the refrigerant circulation pipe 15.
  • the gas-phase CO 2 is cooled under high pressure to form a liquid-phase CO 2 (A -> B in Fig. 4 ), and the high-pressure liquid-phase CO 2 is supplied to the expansion valve 6 through the refrigerant inflow pipe 5.
  • the high-pressure liquid-phase CO 2 is expanded and decompressed by the expansion valve 6 to form a solid-gas two-phase CO 2 (B -> C in Fig. 4 ), and the solid-gas two-phase CO 2 flows into the interior space 1b of the cylindrical portion 1 of the evaporator (cyclone refrigeration device) through the refrigerant inlet 1c of the evaporator (cyclone refrigeration device).
  • the solid-gas two-phase CO 2 forms the first vortex flow descending into the interior space 1b and separates into a solid-phase CO 2 and a gas-phase CO 2 (C -> E (corresponding to a separation process of the solid-phase CO 2 from the solid-gas two-phase CO 2 ) and C -> D (corresponding to a separation process of the gas-phase CO 2 from the solid-gas two-phase CO 2 ) in Fig. 4 ).
  • the solid-phase CO 2 deposits in the cavity 4a of the cooling portion 4 of the evaporator (cyclone refrigeration device) while the gas-phase CO 2 forms the second vortex flow rising through the inside space of the first vortex flow and is taken from the exhaust pipe 3 into the compressor 13 through the refrigerant circulation pipe 15.
  • the solid-phase CO 2 deposited in the cavity 4a of the evaporator (cyclone refrigeration device) is sublimated by the heat of the fluid to be cooled (E -> D in Fig. 4 ), and this sublimation heat is supplied to the fluid to be cooled.
  • Fig. 6 is a Mollier diagram of a case in which a well-known evaporator is provided instead of the cyclone refrigeration device of the cyclone heat recovery unit of the present invention and CO 2 as a refrigerant is used.
  • D -> A corresponds to a compression process in the compressor 13
  • a -> B corresponds to a condensation process in the condenser 14
  • B -> C corresponds to an expansion process in the expansion valve (decompression unit)
  • C -> D corresponds to an evaporation process in the evaporator.
  • Fig. 5 is a Mollier diagram of a variation of the heat pump system 16 of Fig. 3 in which the cyclone refrigeration device of Fig. 2 is provided instead of the cyclone refrigeration device of Fig. 1 .
  • D -> A corresponds to a compression process in the compressor 13
  • a -> B corresponds to a condensation process in the condenser 14
  • B -> C corresponds to an expansion process in the expansion valve (decompression unit) 6
  • C -> E corresponds to a separation process of the solid-phase refrigerant from the solid-gas two-phase refrigerant S in the evaporator (cyclone refrigeration device)
  • C -> D corresponds to a separation process of the gas-phase refrigerant from the solid-gas two-phase refrigerant in the evaporator (cyclone refrigeration device)
  • E -> D corresponds to an evaporation process of the solid-phase refrigerant S in the evaporator (cyclone refrigeration device).
  • one compressor is used alone in the compression process of CO 2 (D -> A) in the above embodiment, it is possible to provide a compressor composed of a low pressure compressor and a high pressure compressor which are connected in series, and an inter cooler arranged between the low pressure and high pressure compressors so as to compress CO 2 in two stages.
  • a gas-phase CO 2 can be easily compressed to saturation or supercritical pressure.
  • the cooling capacity of the condenser improves so that the high-pressure gas-phase CO 2 can be cooled to lower temperature in one stage.
  • Fig. 7 is a view schematically illustrating a configuration of a cyclone heat recovery unit provided with the cyclone refrigeration device shown in Fig. 1 .
  • a cyclone heat recovery unit 17 of the present invention comprises the cyclone refrigeration device shown in Fig. 1 , and a refrigerant circulation pipe 18 connecting an exit of the exhaust pipe 3 of the cyclone refrigeration device and the other end 5b of refrigerant inflow pipe 5.
  • a compressor 19 is provided in the refrigerant circulation pipe 18 so as to compress a gas-phase refrigerant exhausted from the exhaust pipe 3 of the cyclone refrigeration device, and first and second condensers 20, 21 are provided in series downstream of the compressor 19 in the refrigerant circulation pipe 18 so as to condense the gas-phase refrigerant compressed by the compressor 18 into a liquid-phase refrigerant.
  • a heat exchanger 22 is provided downstream of the first and second condensers 20, 21 in the refrigerant circulation pipe 18.
  • a bypass line 23 is provided in the refrigerant circulation pipe 18 so as to connect a downstream side of the heat exchanger 22 and an upstream side of the compressor 18.
  • An expansion valve (decompression unit) 24 is provided in the bypass line 23 and an evaporator 25 is provided downstream of the expansion valve 24 in the bypass line 23.
  • a first flow controller 27 is provided downstream of the connection point 26 with an upstream end of the bypass line 23 in the refrigerant circulation pipe 18, and a second flow controller 28 is provided upstream of the expansion valve 24 in the bypass line 23.
  • a third flow controller 30a is provided upstream of the connection point 29 with a downstream end of the bypass line 23 in the refrigerant circulation pipe 18, and a fourth flow controller 30b is provided downstream of the evaporator 25 in the bypass line 23.
  • the third and fourth flow controllers 30a, 30b are primarily intended for pressure control.
  • the cyclone refrigeration device when CO 2 is used as a refrigerant, the cyclone refrigeration device operates under the pressure condition below the triple point at which CO2 enters a solid-gas two-phase state while the evaporator 25 operates under the pressure condition above the triple point at which CO 2 enters a gas-liquid two-phase state and therefore, the third and fourth flow controllers 30a, 30b operate in such a way that the above pressure conditions are satisfied.
  • the fluid to be cooled which exchanges heat with the solid-phase refrigerant S in the heat exchanger 8 of the cyclone refrigeration device is preferably low-temperature refrigerant (carbon dioxide, ethanol and helium and so on).
  • a lower temperature cold source can be obtained by using the low temperature refrigerant as fluid to be cooled.
  • the refrigerant circulation pipe 18 it is possible to divide some of the liquid-phase refrigerant flowing through the refrigerant circulation pipe 18 into the bypass line 23 so as to operate the cyclone refrigeration device and the evaporator 25 at the same time, or it is possible to stop the supply of the liquid-phase refrigerant to the bypass line 23 so as to operate only the cyclone refrigeration device, or it is possible to stop the supply of the liquid-phase refrigerant to the cyclone refrigeration device so as to operate only the evaporator 25.
  • Fig. 8 is a view schematically illustrating a configuration of a cascade heat pump system into which the cyclone heat recovery unit shown in Fig. 7 is incorporated as a low-temperature side cycle.
  • Fig. 8 the same structural elements as those shown in Fig. 7 are designated by the same reference numerals and the detailed description of them will be omitted in the following.
  • a cascade heat pump system 31 comprises a low-temperature side cycle 32 and a high-temperature side cycle 33, and the low-temperature side cycle consists of the cyclone heat recovery unit 17 shown in Fig. 7 .
  • the heat exchanger 22 of the cyclone heat recovery unit 17 forms a low-temperature side heat exchanger 35 of a cascade heat exchanger 34 of the cascade heat pump system 31.
  • the high-temperature side cycle 33 includes a high-temperature side heat exchanger 36 pairing with the low-temperature side heat exchanger 35 to form the cascade heat exchanger 34, a high-temperature side refrigerant circulation pipe 37 extending between an exit 36a and an entrance 36b of the high-temperature side heat exchanger 36, a compressor 38 provided downstream of the high-temperature side heat exchanger 36 in the high-temperature side refrigerant circulation pipe 37, third and fourth condensers 39, 40 provided in series downstream of the compressor 38 in the high-temperature side refrigerant circulation pipe 37, and an expansion valve (decompression unit) 41 provided downstream of the third and fourth condensers 39, 40 in the high-temperature side refrigerant circulation pipe 37.
  • a compressor 38 provided downstream of the high-temperature side heat exchanger 36 in the high-temperature side refrigerant circulation pipe 37
  • third and fourth condensers 39, 40 provided in series downstream of the compressor 38 in the high-temperature side refrigerant circulation pipe 37

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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)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Cyclones (AREA)

Claims (7)

  1. Zyklon-Wärmerückgewinnungseinheit (17), umfassend:
    eine Zyklon-Kühlvorrichtung, die Zyklon-Kühlvorrichtung umfassend
    einen zylindrischen Abschnitt (1), der sich vertikal erstreckt und an einem oberen Ende davon geschlossen ist,
    ein Ableitungsrohr (3), dessen Radius kleiner ist als der Radius des zylindrischen Abschnitts (1), das koaxial mit dem oberen Ende des zylindrischen Abschnitts (1) in Fluidverbindung mit einem Innenraum (1b) des zylindrischen Abschnitts (1) ist und sich von dem oberen Ende des zylindrischen Abschnitts (1) nach oben erstreckt,
    einen Abkühlabschnitt (4), der mit einem unteren Ende des zylindrischen Abschnitts (1) verbunden und mit einem Hohlraum (4a) bereitgestellt ist, der mit dem Innenraum (1b) des zylindrischen Abschnitts (1) in Verbindung ist,
    wobei der zylindrische Abschnitt (1) einen Kältemitteleinlass (1c) an einem oberen Abschnitt einer Seitenwand davon aufweist;
    ein Kältemittelzuflussrohr (5), das an einem Ende (5a) davon mit dem Kältemitteleinlass (1c) verbunden ist und an dem anderen Ende davon eine Zufuhr von Flüssigphasenkältemittel aufnimmt, das unter hohem Druck verdichtet wird, und
    eine erste Dekompressionseinheit (6), die mit dem Kältemittelzuflussrohr (5) bereitgestellt ist,
    wobei das dem Kältemittelzuflussrohr (5) zugeführte Flüssigphasenkältemittel durch die erste Dekompressionseinheit (6) dekomprimiert wird, um ein Festgas-Zweiphasenkältemittel zu bilden, und das Festgas-Zweiphasenkältemittel in den Innenraum (1b) des zylindrischen Abschnitts (1) nach unten strömt, wobei es eine erste Wirbelströmung bildet und sich in Festphasenkältemittel und Gasphasenkältemittel trennt, und das Festphasenkältemittel (S) sich einerseits in dem Hohlraum (4a) absetzt und das Gasphasenkältemittel andererseits eine zweite Wirbelströmung bildet, die von dem Boden des Hohlraums (4a) durch einen Innenraum der ersten Wirbelströmung aufsteigt, um aus dem Ableitungsrohr (3) zu strömen, wobei die Zyklon-Kühlvorrichtung ferner Folgendes umfasst
    eine Zirkulationsleitung (7) für abzukühlendes Fluid, die sich durch den Hohlraum (4a) des Abkühlabschnitts (4) erstreckt, wobei beide Enden der Zirkulationsleitung (7) außerhalb des Abkühlabschnitts (4) miteinander verbunden sind, wobei das abzukühlende Fluid von einer Abkühllast (9) in der Zirkulationsleitung (7) strömt,
    einen ersten Wärmetauscher (8), der in einem Abschnitt der Zirkulationsleitung (7) für abzukühlendes Fluid bereitgestellt ist, die sich innerhalb des Hohlraums (4a) befindet, und
    eine Pumpe (10), die in der Zirkulationsleitung (7) für abzukühlendes Fluid außerhalb des Abkühlabschnitts (4) bereitgestellt ist;
    ein Kältemittelzirkulationsrohr (18), das einen Ausgang des Ableitungsrohrs (3) der Zyklon-Kühlvorrichtung mit dem anderen Ende (5b) des Kältemittelzuflussrohrs (5) verbindet;
    einen ersten Verdichter (19), der in dem Kältemittelzirkulationsrohr (18) bereitgestellt ist, um das Gasphasenkältemittel zu verdichten, das aus dem Ableitungsrohr (3) der Zyklon-Kühlvorrichtung austritt;
    einen ersten und einen zweiten Kondensator (20, 21), die stromabwärts von dem ersten Verdichter (19) in dem Kältemittelzirkulationsrohr (18) in Reihe bereitgestellt sind, um das durch den ersten Verdichter (19) verdichtete Gasphasenkältemittel in das Flüssigphasenkältemittel zu kondensieren;
    einen zweiten Wärmetauscher (22), der stromabwärts von dem ersten und zweiten Kondensator (20, 21) in der Kältemittelzirkulationsrohr (18) bereitgestellt ist;
    eine Bypassleitung (23), die eine stromabwärtige Seite des zweiten Wärmetauschers (22) und eine stromaufwärtige Seite des ersten Verdichters (19) in dem Kältemittelzirkulationsrohr (18) verbindet;
    eine zweite Dekompressionseinheit (24), die in der Bypassleitung (23) bereitgestellt ist;
    einen Verdampfer (25), der stromabwärts von der zweiten Dekompressionseinheit (24) in der Bypassleitung (23) bereitgestellt ist;
    einen ersten Durchflussregler (27), der stromabwärts von der Verbindungsstelle (26) mit einem stromaufwärtigen Ende der Bypassleitung (23) in der Kältemittelzirkulationsrohr (18) bereitgestellt ist;
    einen zweiten Durchflussregler (28), der stromaufwärts von der zweiten Dekompressionseinheit (24) in der Bypassleitung (23) bereitgestellt ist;
    einen dritten Durchflussregler (30a), der stromaufwärts von dem Verbindungspunkt (29) mit einem stromabwärtigen Ende der Bypassleitung (23) in der Kältemittelzirkulationsrohr (18) bereitgestellt ist; und
    einen vierten Durchflussregler (30b), der stromabwärts von dem Verdampfer (25) in der Bypassleitung (23) bereitgestellt ist.
  2. Zyklon-Wärmerückgewinnungseinheit (17) nach Anspruch 1, wobei der erste Wärmetauscher (8) aus einem Behälter besteht, der aus Wärmeleiter gefertigt ist, wobei der Behälter (8) einen Fluidauslass (8a) und einen Fluideinlass (8b) aufweist und mit dem abzukühlenden Fluid gefüllt ist, wobei die Zirkulationsleitung (7) für abzukühlendes Fluid aus Folgendem besteht
    einer Ausgabelinie (7a) für abzukühlendes Fluid, die mit dem Fluidauslass (8a) des Behälters (8) an einem Ende davon verbunden ist und aus dem Behälter (8) zu der Außenseite des Abkühlabschnitts (4) hervorsteht, und
    eine Zufuhrlinie (7b) für abzukühlendes Fluid, die mit dem Fluideinlass (8b) des Behälters (8) an einem Ende davon verbunden ist und aus dem Behälter (8) zu der Außenseite des Abkühlabschnitts (4) hervorsteht,
    wobei das andere Ende der Ausgabelinie (7a) für abzukühlendes Fluid und das andere Ende der Zufuhrlinie (7b) für abzukühlendes Fluid durch die Abkühllast (9) miteinander verbunden sind, und die Pumpe (10) in der Ausgabelinie (7a) für abzukühlendes Fluid oder der Zufuhrlinie (7b) für abzukühlendes Fluid bereitgestellt ist.
  3. Zyklon-Wärmerückgewinnungseinheit (17) nach Anspruch 1, wobei die Zyklon-Kühlvorrichtung ferner Folgendes umfasst
    einen Wirbelströmungs-Regelkörper (11), der über dem Innenraum (1b) des zylindrischen Abschnitts (1) und dem Hohlraum (4a) des Abkühlabschnitts (4) angeordnet ist und sich vertikal erstreckt, wobei der Wirbelströmungs-Regelkörper (11) einen säulenförmigen Bodenabschnitt (11a) aufweist,
    einen kegelstumpfförmigen mittleren Abschnitt (11b), der mit einer oberen Fläche des Bodenabschnitts (11a) verbunden ist und sich von dem Bodenabschnitt (11a) nach oben verjüngt, und
    einen säulenförmigen oberen Abschnitt (11c), der mit einer oberen Fläche des mittleren Abschnitts (11b) verbunden ist und sich von dem mittleren Abschnitt (11b) nach oben erstreckt,
    wobei der Wirbelströmungs-Regelkörper (11) mit einem axialen Durchgangsloch (12) mit kreisförmigem Querschnitt darin bereitgestellt ist, wobei die zweite Wirbelströmung in das Durchgangsloch (12) strömt, wobei sich das Durchgangsloch zu der oberen Fläche (11d) des Wirbelströmungs-Regelkörpers (11) ausbreitet, nachdem es sich von der unteren Fläche (11e) des Wirbelströmungs-Regelkörpers (11) nach oben verjüngt, wobei der Wirbelströmungs-Regelkörper (11) koaxial zu dem zylindrischen Abschnitt (1) durch den Abkühlabschnitt (4) und/oder den zylindrischen Abschnitt (1) auf eine solche Weise gestützt wird, dass der Bodenabschnitt (11a) sich innerhalb des Hohlraums (4a) befindet und sich der mittlere Abschnitt (11b) über dem Hohlraum (4a) und dem Innenraum (1b) befindet und ein gewisser Raum unter der unteren Fläche (11e) des Wirbelströmungs-Regelkörpers (11) gebildet ist.
  4. Zyklon-Wärmerückgewinnungseinheit (17) nach Anspruch 1, wobei der Innenraum (1b) des zylindrischen Abschnitts (1) nach unten verjüngt ist.
  5. Zyklon-Wärmerückgewinnungseinheit (17) nach Anspruch 1, wobei das Kältemittel Kohlendioxid oder Wasser oder Ammoniak ist.
  6. Kaskaden-Wärmepumpensystem (31), umfassend eine niedertemperaturseitigen Kreislauf (32) und einem hochtemperaturseitigen Kreislauf (33),
    wobei der niedertemperaturseitige Kreislauf (32) aus der Zyklon-Wärmerückgewinnungseinheit (17) nach einem der Ansprüche 1 bis 5 besteht, und der zweite Wärmetauscher (22) der Zyklon-Wärmerückgewinnungseinheit (17) einen niedertemperaturseitigen Wärmetauscher (35) eines Kaskadenwärmetauschers (34) bildet.
  7. Kaskaden-Wärmepumpensystem (31) nach Anspruch 6, wobei der hochtemperaturseitige Kreislauf (33) Folgendes beinhaltet
    einen hochtemperaturseitigen Wärmetauscher (36), der mit dem zweiten Wärmetauscher (22) der Zyklon-Wärmerückgewinnungseinheit (17) gekoppelt ist, um den Kaskadenwärmetauscher (34) zu bilden;
    ein hochtemperaturseitiges Kältemittelzirkulationsrohr (37), die sich zwischen einem Ausgang (36a) und einem Eingang (36b) des hochtemperaturseitigen Wärmetauschers (36) erstreckt; einen zweiten Verdichter (38), der stromabwärts von dem hochtemperaturseitigen Wärmetauscher (36) in dem hochtemperaturseitigen Kältemittelzirkulationsrohr (37) bereitgestellt ist;
    einen dritten und einen vierten Kondensator (39, 40), die stromabwärts von dem zweiten Verdichter (38) in dem hochtemperaturseitigen Kältemittelzirkulationsrohr (37) in Reihe bereitgestellt sind; und
    eine dritte Dekompressionseinheit (41), die stromabwärts von dem dritten und dem vierten Kondensator (39, 40) in dem hochtemperaturseitigen Kältemittelzirkulationsrohr (37) bereitgestellt ist.
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PCT/JP2019/001499 WO2019142919A1 (ja) 2018-01-19 2019-01-18 サイクロン式冷凍装置、サイクロン式冷熱回収ユニット、および該サイクロン式冷凍装置または該サイクロン式冷熱回収ユニットを備えたヒートポンプシステム

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US2043190A (en) * 1931-09-10 1936-06-02 Mccabe Maier Corp Refrigerating apparatus and method
FR2253193A1 (en) * 1973-12-03 1975-06-27 Air Liquide Refrigeration of prods partic food prods - using carbon dioxide snow
US4224801A (en) * 1978-11-13 1980-09-30 Lewis Tyree Jr Stored cryogenic refrigeration
JPH1130599A (ja) * 1997-07-09 1999-02-02 Toyo Eng Works Ltd ドライアイスの蓄熱を利用する二元冷却設備の蓄熱量 計測方法及び同二元冷却設備
JP2004308972A (ja) * 2003-04-03 2004-11-04 Mayekawa Mfg Co Ltd Ｃｏ２冷凍機
DE102012008592A1 (de) * 2012-04-27 2013-10-31 Messer France S.A.S Verfahren und Vorrichtung zum Kühlen von Produkten

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