US20100147017A1 - Refrigeration apparatus - Google Patents

Refrigeration apparatus Download PDF

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Publication number
US20100147017A1
US20100147017A1 US12/300,706 US30070607A US2010147017A1 US 20100147017 A1 US20100147017 A1 US 20100147017A1 US 30070607 A US30070607 A US 30070607A US 2010147017 A1 US2010147017 A1 US 2010147017A1
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Prior art keywords
refrigerant
temperature
compressor
low
refrigerant circuit
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US12/300,706
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English (en)
Inventor
Katsuji Takasugi
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PHC Holdings Corp
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Sanyo Electric Co Ltd
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Assigned to SANYO ELECTRIC CO., LTD. reassignment SANYO ELECTRIC CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TAKASUGI, KATSUJI
Publication of US20100147017A1 publication Critical patent/US20100147017A1/en
Assigned to PANASONIC HEALTHCARE CO., LTD. reassignment PANASONIC HEALTHCARE CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SANYO ELECTRIC CO., LTD.
Assigned to PANASONIC HEALTHCARE HOLDINGS CO., LTD. reassignment PANASONIC HEALTHCARE HOLDINGS CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: PANASONIC HEALTHCARE CO., LTD.
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • 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
    • F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
    • F25D2400/10—Refrigerator top-coolers

Definitions

  • the present invention relates to a refrigeration apparatus of a so-called two-dimensional refrigeration system in which independent two-system refrigerant circuits are constituted and in which an evaporator of a high-temperature-side refrigerant circuit and a condenser of a low-temperature-side refrigerant circuit constitute a heat exchanger.
  • FIG. 7 shows a refrigerant circuit diagram of a refrigeration apparatus 135 using the two-dimensional refrigeration apparatus.
  • a refrigerant circuit 100 is constituted of a high-temperature-side refrigerant cycle 101 and a low-temperature-side refrigerant cycle 102 .
  • a discharge-side pipe 103 D of a compressor 103 constituting the high-temperature side-refrigerant cycle 101 is connected to an auxiliary condenser 105 , and the auxiliary condenser 105 is connected to a frame pipe 104 (for the frame pipe, refer to a frame pipe 27 of the present application), and then connected to a condenser 107 via an oil cooler 106 of the compressor 103 .
  • the condenser 107 is cooled by a blower 116 for the condenser.
  • an outlet-side refrigerant pipe of the condenser 107 is connected to an evaporator 110 as an evaporator portion constituting the evaporator successively through a drier 108 and a pressure reducing unit 109 .
  • An outlet-side refrigerant pipe of the evaporator 110 is connected to an accumulator 111 , and a refrigerant pipe exiting from the accumulator 111 is connected to a suction-side pipe 103 S of the compressor 103 .
  • a discharge-side pipe 113 D of a compressor 113 constituting the low-temperature-side refrigerant cycle 102 is connected to an oil separator 114 , and a refrigerant pipe connected to the outlet side of this oil separator 114 is connected to a condensing pipe 115 as a high-temperature-side pipe inserted into the evaporator 110 .
  • This condensing pipe 115 constitutes a cascade heat exchanger 130 together with the evaporator 110 .
  • a discharge pipe connected to the outlet side of the condensing pipe 115 is connected to a first gas-liquid separator 116 through a drier 131 , and the gas-phase refrigerant separated by the gas-liquid separator 116 passes through a first intermediate heat exchanger 117 via a gas-phase pipe to flow into a second gas-liquid separator 118 .
  • a liquid-phase refrigerant separated by the gas-liquid separator 116 passes through a drier 119 and a pressure reducing unit 120 via a liquid-phase pipe, flows into the first intermediate heat exchanger 117 , and evaporates the gas-phase refrigerant to cool.
  • the liquid-phase refrigerant separated by the second gas-liquid separator 118 passes through a drier 121 and a pressure reducing unit 122 via the liquid-phase pipe to flow into a second intermediate heat exchanger 123 .
  • the gas-phase refrigerant separated by the second gas-liquid separator 118 passes through the second intermediate heat exchanger 123 via the liquid-phase pipe, and passes through a third intermediate heat exchanger 124 and a drier 125 to flow into a pressure reducing unit 126 .
  • the pressure reducing unit 126 is connected to an evaporation pipe 127 as an evaporator arranged in a heat exchanging manner in an inner wall of an insulating box body 132 of the refrigeration apparatus on a storage chamber side, and the evaporation pipe 127 is further connected to the third intermediate heat exchanger 124 .
  • the third intermediate heat exchanger 124 is successively connected to the second and first intermediate heat exchangers, and then connected to a suction-side pipe 113 S of the compressor 113 .
  • This suction-side pipe 113 S is connected to an expansion tank 128 for receiving the refrigerant during the stop of the compressor 113 through a pressure reducing unit 129 .
  • the evaporation pipe 127 of the low-temperature-side refrigerant cycle 102 can obtain an extremely low temperature of ⁇ 150° C. or less.
  • Patent Document 1 Japanese Patent No. 3208151
  • the present invention has been developed to solve the conventional technical problem, and an object thereof is to provide a refrigeration apparatus capable of decreasing a load on a compressor and improving an operation efficiency.
  • a refrigeration apparatus of the present invention is characterized by comprising: a high-temperature side refrigerant circuit and a low temperature-side refrigerant circuit each constituting an independent refrigerant closed circuit in which a refrigerant discharged from a compressor is condensed and then evaporated to exert a cooling function, the low-temperature-side refrigerant circuit having the compressor, a condenser, an evaporator, and a plurality of intermediate heat exchangers and a plurality of pressure reducing units connected in series so that the refrigerant fed back from the evaporator circulates, wherein a plurality of types of non-azeotropic mixed refrigerants are introduced, a condensed refrigerant in the refrigerants passed through the condenser is allowed to join the intermediate heat exchanger through the pressure reducing unit, a non-condensed refrigerant in the refrigerants is cooled by the intermediate heat exchanger to successively condense the refrigerant having a lower boiling point,
  • a refrigeration apparatus of the invention of a second aspect is characterized in that in the above invention, the non-azeotropic mixed refrigerants include a refrigerant having a satisfactory solubility in the oil and a high boiling point as compared with at least another refrigerant.
  • the refrigeration apparatus comprises the high-temperature-side refrigerant circuit and the low-temperature-side refrigerant circuit each constituting the independent refrigerant closed circuit in which the refrigerant discharged from the compressor is condensed and then evaporated to exert the cooling function.
  • the low temperature-side refrigerant circuit has the compressor, the condenser, the evaporator, and the plurality of intermediate heat exchangers and the plurality of pressure reducing units connected in series so that the refrigerant fed back from the evaporator circulates.
  • the plurality of types of non-azeotropic mixed refrigerants are introduced, the condensed refrigerant in the refrigerants passed through the condenser is allowed to join the intermediate heat exchanger through the pressure reducing unit, the non-condensed refrigerant in the refrigerants is cooled by the intermediate heat exchanger to successively condense the refrigerant having the lower boiling point, the refrigerant having the lowest boiling point is allowed to flow into the evaporator through the final stage of the pressure reducing unit, the evaporator of the high-temperature-side refrigerant circuit and the condenser of the low-temperature-aide refrigerant circuit constitute the cascade heat exchanger, and the evaporator of the low-temperature side refrigerant circuit is configured to obtain the extremely low temperature.
  • the refrigeration apparatus further comprises the oil separator provided on the discharge side of the compressor of the low-temperature-side refrigerant circuit so that the oil is separated from the non-azeotropic mixed refrigerants to return the oil to the compressor, and the radiator interposed between the oil separator and the compressor.
  • the refrigerants still having a gas-phase state are successively condensed using an evaporation temperature difference between the refrigerants in the low-temperature-side refrigerant circuit by a plurality of heat exchangers, and an extremely low temperature of ⁇ 150° C. can be achieved in the evaporator of the final stage.
  • the radiator is interposed between the discharge side of the compressor of the low-temperature-side refrigerant circuit and the oil separator, the temperature of the refrigerant entering the cascade heat exchanger of the low-temperature side refrigerant circuit can be lowered by the radiator. In consequence the loads on the compressors of both the refrigerant circuits can be decreased, and the operation efficiency can be improved.
  • the non-azeotropic mixed refrigerants include the refrigerant having the satisfactory solubility in the oil and the high boiling point as compared with at least the other refrigerant.
  • the refrigerant is fed from the oil separator back to the compressor together with the oil. Therefore, a more highly pure refrigerant having a low boiling point flows through the circuit in the stage subsequent to the cascade heat exchanger, and the extremely low temperature can more efficiently be obtained.
  • the inside of the storage chamber as a cooling target having a larger volume can be cooled to a predetermined extremely low temperature even by the compressor having the same capability, and a storage capacity can be increased without enlarging the whole apparatus.
  • FIG. 1 is a perspective view of a refrigeration apparatus 1 to which the present invention is applied
  • FIG. 2 is a front view of the refrigeration apparatus 1
  • FIG. 3 is a plan view of the refrigeration apparatus 1
  • FIG. 4 is a side view-in a state in which a storage chamber 4 is seen through the refrigeration apparatus 1
  • FIG. 5 is a perspective view of the refrigeration apparatus 1 in a state in which a top panel 5 is opened.
  • the refrigeration apparatus 1 of the present embodiment is suitable for storing, at an extremely low temperature, for example; a living tissue, a specimen or the like to be stored at a low temperature for a long time, and a main body of the apparatus is constituted of an insulating box body 2 which opens in an upper surface, and a mechanical chamber 3 which is positioned by the side of the insulating box body 2 and in which a compressor 10 and the like are installed.
  • This insulating box body 2 is constituted of an outer box 6 made of a steel plate and an inner box 7 made of a satisfactorily thermally conductive metal such as aluminum, the boxes having opened upper surfaces.
  • the insulating box body is also constituted of a breaker 8 connecting the upper ends of both the boxes 6 , 7 to each other, and an insulating material 9 with which a space surrounded by the outer box 6 , the inner box 7 and the breaker 8 is filled by an on-site foam system and which is made of a polyurethane resin.
  • the inside of the inner box 7 is the storage chamber 4 having an open upper surface.
  • a targeted temperature (hereinafter referred to as the in-chamber temperature) in the storage chamber 4 is set to, for example, ⁇ 150° C. or less. Therefore, the insulating box body 2 which separates the inside of the storage chamber 4 and outside air needs to have large insulating capability against a set low in-chamber temperature around 0° C. Therefore, to secure the insulating capability only by the insulating material 9 made of the polyurethane resin, the material has to be formed to be remarkably thick. There is also a problem that a sufficient storage amount in the storage chamber 4 cannot be secured with a limited main body dimension.
  • vacuum insulating panels 12 made of glass wool are arranged in the inner wall surfaces of a front wall 6 A of the outer box 6 , a rear wall 6 B and a side wall 6 C positioned on a side opposite to aside provided with the mechanical chamber 3 .
  • the panels are tentatively fixed with an adhesive double coated tape, and then a space between both the boxes 6 and 7 is filled with the insulating material 9 by the on-site foam system.
  • this vacuum insulating panel 12 glass wool having insulating properties is received in a container constituted of a multilayered film made of aluminum, a synthetic resin or the like which does not have any gas permeability. Afterward, air is discharged from the container by predetermined vacuum exhaust means, and an opening of the container is thermally sealed and joined. In consequence, since the vacuum insulating panel 12 has the insulating performance, the thickness dimension of the insulating material 9 is decreased as compared with a conventional example, but the same insulating effect can be obtained.
  • an evaporator (an evaporation pipe) 62 constituting a refrigerant circuit of a cooling apparatus R described later in detail is attached to the peripheral surface of the inner box 7 on the insulating material 9 side in a heat exchange manner.
  • the upper surface of the breaker 8 of the insulating box body 2 having the above constitution is formed in a staircase-like shape, and an insulating door 13 is provided on the surface via a packing (not shown) so that the insulating door is rotatable around one end, that is, the rear end of the door in the present embodiment by pivotable members 14 , 14 .
  • the upper-surface opening of the storage chamber 4 is provided with an openable/closable inner lid 15 constituted of an insulating material.
  • the lower surface of the insulating door 13 is provided with a pressing portion configured to protrude downwards.
  • the pressing portion of the insulating door 13 presses the inner lid 15 to openably close the upper surface opening of the storage chamber 4 .
  • the other end, that is, the front end of the insulating door 13 in the present embodiment is provided with a handle portion 16 , and the handle portion 16 is operated to open or close the insulating door 13 .
  • a front panel 3 A, a rear panel (not shown) and a side panel 3 B constituting a side surface on a side opposite to a side provided with the insulating box body 2 form the mechanical chamber 3 .
  • the mechanical chamber 3 of the present embodiment is provided with a partition plate 17 which divides the inside of the chamber into upper and lower chambers.
  • the compressor 10 , a compressor 20 and the like constituting the cooling apparatus R as described above are received and installed under the partition plate 17 , and the front panel 3 A and the side panel 3 B positioned under the partition plate 17 are provided with slits 3 C for ventilation.
  • An upper mechanical chamber 18 having an opened upper surface is constituted above the partition plate 17 .
  • the upper-surface opening of the upper mechanical chamber 18 is provided with the top panel 5 so that the panel is rotatable around one end, that is, the rear end of the panel in the present embodiment, whereby the upper mechanical chamber 18 is openably closed.
  • a panel positioned on the front surface of the upper mechanical chamber 18 is an operation panel 21 for operating the refrigeration apparatus 1 .
  • a side surface constituting this upper mechanical chamber 18 on the insulating box body 2 side is provided with a measurement hole 19 .
  • This measurement hole 19 is extended through the outer box 6 , the insulating material 9 and the inner box 7 constituting the insulating box body 2 so as to communicate with the storage chamber 4 formed the insulating box body 2 provided adjacent to the measurement hole.
  • temperature sensor can be inserted into the storage chamber 4 from the outside, and a wiring line drawn from the temperature sensor is connected to an external recording apparatus main body through the measurement hole 19 .
  • a gap between this measurement hole 19 and the wiring line is closed by a plug 19 A constituted of a sponge-like deformable special material having insulating properties. It is to be noted that the measurement hole 19 is closed by the plug 19 A in an insulating manner in a state in which the temperature sensor is not attached to the hole.
  • the top panel 5 provided in the mechanical chamber 3 is opened, and the measuring instrument can be inserted into the storage chamber 4 through the measurement hole 19 formed in the side surface of the insulating box body 2 positioned in the upper mechanical chamber 18 .
  • This can facilitate an operation of installing the measuring instrument in the storage chamber 4 cooled to a predetermined extremely low temperature.
  • the measurement hole 19 of the present embodiment is formed in the side surface of the insulating box body 2 on the mechanical chamber 18 side. Therefore, even when the refrigeration apparatus 1 is installed adjacent to the wall of an installation environment such as the laboratory, or another device, a space necessary for using the measurement hole 19 does not especially have to be disposed. In consequence, an area required for installing the refrigeration apparatus 1 can be decreased, which is suitable for determining the layout of the laboratory or the like.
  • the vacuum insulating panels 12 can be provided in the side surface other than the side surface adjacent to the mechanical chamber 3 , that is, the front and rear walls and the side surface of the insulating box body 2 constituted so as to face the outside without influencing the forming position of the measurement hole 19 .
  • the leakage of cold from the storage chamber 4 can be decreased, and the wasting of useless cooling energy can be suppressed.
  • the insulating performance of the insulating box body 2 itself can be improved, and the dimension of an insulating wall can be decreased.
  • a storage volume in the storage chamber 4 can be increased.
  • the outer dimension can be decreased. Even in this case, the area required for installing the refrigeration apparatus 1 can be decreased.
  • the measurement hole 19 of the present embodiment can be covered with the top panel 5 which can openably close the upper-surface opening of the upper mechanical chamber 18 , whereby the appearance of the apparatus has a constitution in which the measurement hole 19 is not exposed, and the appearance can, be improved. Moreover, when the top panel 5 is opened, an operation can easily be performed with respect to the measurement hole 19 , and operability can be improved. When the partition plate 17 is removed, another device constituting the cooling apparatus R installed under the partition plate 17 can easily be operated, and the efficiency of a maintenance operation can be improved.
  • the mechanical chamber 18 is closed with the top panel 5 in a case other than the case where the operation is performed with respect to the measurement hole 19 , so that the top panel 5 can be used as a side table for an operation, and the panel is convenient for an operation of storing articles such as samples in the storage chamber 4 or taking the articles from the chamber.
  • the measurement hole 19 is covered with the top panel 5 which closes the upper-surface opening of the upper mechanical chamber 18 , but this is not restrictive, and a lid member for covering the measurement hole 19 or the like may be provided in the vicinity of the measurement hole 19 .
  • the refrigerant circuit of the refrigeration apparatus 1 in the present embodiment is constituted of a two-dimensional two-stage refrigerant circuit, as a multi-dimensional multistage refrigerant circuit, including independent refrigerant circuits of a high-temperature-side refrigerant circuit 25 as a first refrigerant circuit and a low-temperature-side refrigerant circuit 38 as a second refrigerant circuit.
  • the compressor 10 constituting the high-temperature-side refrigerant circuit 25 is an electromotive compressor using a one-phase or three-phase alternating-current power source, and a discharge side pipe 10 D of the compressor 10 is connected to an auxiliary condenser 26 .
  • this auxiliary condenser 26 is connected to a refrigerant pipe 27 (hereinafter referred to as a frame pipe) arranged on the back side of this opening edge.
  • this frame pipe 27 is connected to an oil cooler. 29 of the compressor 10 , and then connected to a condenser 28 .
  • the refrigerant pipe exiting from the condenser 28 is connected to an oil cooler 30 of the compressor 20 constituting the low-temperature-side refrigerant circuit 38 , and is then connected to a condenser 31 .
  • the refrigerant pipe exiting from the condenser 31 is connected to an evaporator 34 as an evaporator portion constituting the evaporator successively via a drier 32 and a capillary tube 33 as a pressure reducing unit.
  • An outlet side refrigerant pipe of the evaporator 34 is connected to an accumulator 35 as a refrigerant liquid reservoir, and the refrigerant pipe exiting from the accumulator 35 is connected to a suction side pipe 10 S of the compressor 10 .
  • the auxiliary condenser 26 and the condensers 28 and 31 in the present embodiment are constituted as an integral condenser, and are cooled by a blower 36 for the condenser.
  • the high-temperature-side refrigerant circuit 25 is filled with a refrigerant constituted of R407D and n-pentane as non-azeotropic refrigerants having different boiling points.
  • R407D is constituted of R32 (difluoromethane: CH 2 F 2 ), R125 (pentafluoroethane: CHF 2 CF 3 ), and R134a (1,1,1,2-tetrafluoroethane: CH 2 FCF 3 ), and a composition includes 15 wt % of R32, 15 wt % of R125 and 70 wt % of R134a.
  • R32 has ⁇ 51.8° C.
  • R125 has ⁇ 48.57° C.
  • R134a has ⁇ 26.16° C.
  • the boiling point of n-pentane is +36.1° C.
  • the high-temperature gas refrigerant discharged from the compressor 10 is condensed, releases heat and is liquefied by the auxiliary condenser 26 , the frame pipe 27 , the oil-cooler 29 , the condenser 28 , the oil cooler 30 of the compressor 20 of the low-temperature-side refrigerant circuit 38 and the condenser 31 .
  • a water content contained in the refrigerant is removed by the drier 32 , and the pressure of the refrigerant is reduced by the capillary tube 33 .
  • the refrigerants successively flow into the evaporator 34 to evaporate the refrigerants R32, R125 and R134a. Then, vaporization heat is absorbed from a surrounding area to cool the evaporator 34 , and the refrigerant returns to the compressor 10 through the accumulator 35 as the refrigerant liquid reservoir.
  • the compressor 10 has a capability of, for example, 1.5 HP, and the final reaching temperature of the evaporator 34 which is being operated is in a range of ⁇ 27° C. to ⁇ 35° C.
  • the refrigerant does not evaporate in the evaporator 34 and still has a liquid state. Therefore, the refrigerant hardly contributes to cooling, but the refrigerant has a function of feeding the lubricant of the compressor 10 and a mixed water content which cannot completely be absorbed by the drier 32 back to the compressor 10 in a state in which the same is dissolved in the refrigerant.
  • the refrigerant also has a function of lowering the temperature of the compressor 10 by the evaporation of the liquid refrigerant in the compressor 10 .
  • the compressor 20 of the low-temperature-side refrigerant circuit 38 is an electromotive compressor using a one-phase or three-phase alternating-current power source in the same manner as in the compressor and a discharge side pipe 20 D of the compressor 20 is connected to an oil separator 40 via a radiator 39 constituted of a wire condenser.
  • This Oil separator 40 is connected to an oil return tube 41 which returns to the compressor 20 .
  • a refrigerant pipe connected to the outlet side of the oil separator 40 is connected to a condensing pipe 42 as a high-pressure-side pipe inserted into the evaporator 34 .
  • This condensing pipe 42 constitutes a cascade heat exchanger 43 together with the evaporator 34 .
  • a discharge pipe connected to the outlet side of the condensing pipe 42 is connected to a first gas-liquid separator 46 via a drier 44 .
  • a gas-phase refrigerant separated by the gas-liquid separator 46 passes through the first intermediate heat exchanger 48 via a gas-phase pipe 47 to flow into a second gas-liquid separator 49 .
  • a liquid-phase refrigerant separated by the first gas-liquid separator 46 flows into the first intermediate heat exchanger 48 through a liquid-phase pipe 50 , a drier 51 and a capillary tube 52 as a pressure reducing unit.
  • the liquid-phase refrigerant separated by the second gas-liquid separator 49 flows into a second intermediate heat exchanger 56 through a liquid-phase pipe 53 , a drier 54 and a capillary tube 55 as a pressure reducing unit.
  • the gas-phase refrigerant separated by the second gas-liquid separator 54 is cooled and liquefied while passing through a gas-phase pipe 57 , the second intermediate heat exchanger 56 and third and fourth intermediate heat exchangers 58 , 59 , and the refrigerant flows into a capillary tube 61 as a pressure reducing unit through a pipe 68 and a drier 60 .
  • the capillary tube 61 is connected to an evaporation pipe 62 as an evaporator, and the evaporation pipe 62 is connected to the fourth intermediate heat exchanger 59 via a return pipe 69 .
  • the fourth intermediate heat exchanger 59 is successively connected to the third, second and first intermediate heat exchangers 58 , 56 and 48 , and then connected to a suction side pipe 20 S of the compressor 20 .
  • the suction side pipe 20 S is further connected to expansion tanks 65 which store the refrigerant during the stop of the compressor 20 via a capillary tube 66 as a pressure reducing unit.
  • the capillary tube 66 is connected in parallel with a check valve 67 in an expansion tank 65 direction as a forward direction.
  • a non-azeotropic mixed refrigerant including R245fa, R600, R404A, R508, R14, R50 and R740 is introduced as a mixed refrigerant of seven types of refrigerants having different boiling points.
  • R245fa is 1,1,1,3,3-pentafluoropropane (CF 3 CH 2 CHF 2 ), and R600 is butane (CH 3 CHCH 2 CH 3 ).
  • R245fa has a boiling point of +15.3° C.
  • R600 has a boiling point of ⁇ 0.5° C. Therefore, when these refrigerants are mixed at a predetermined ratio, the mixed refrigerant can be used as a substitute for heretofore used R21 having a boiling point of +8.9° C.
  • R600 is a combustible substance
  • the refrigerant is introduced as an incombustible refrigerant in the refrigerant circuit 38 .
  • R245fa is set to 70 wt % with respect to a total weight of R245fa and R600. Above this value, the refrigerant becomes incombustible. Therefore, the weight percentage may be set to this value or more.
  • R404A is constituted of R125 (pentafluoroethane: CHF 2 CF 3 ), R143a (1,1,1-trifluoroethane: CH 3 CF 3 ) and R134a (1,1,1,2-tetrafluoroethane: CH 2 FCF 3 ), and a composition includes 44 wt % of R125, 52 wt % of R143a and 4 wt % of R134a.
  • the mixed refrigerant has a boiling point of ⁇ 46.48° C. Therefore, the refrigerant can be used as a substitute for heretofore used R22 having a boiling point of ⁇ 40.8° C.
  • R508 is constituted of R23 (trifluoromethane: CHF 3 ) and R116 (hexafluoroethane: CF 3 CF 3 ), and a composition includes 39 wt % of R23 and 61 wt % of R 116 .
  • the mixed refrigerant has a boiling point of ⁇ 88.64° C.
  • R14 is tetrafluoromethane (carbon tetrafluoride: CF 4 ), R50 is methane (CH 4 ) and R740 is argon (Ar).
  • R14 has a boiling point of ⁇ 127.9° C.
  • R50 has ⁇ 161.5° C.
  • R740 has ⁇ 185.86° C.
  • R50 might cause explosion when coupled with oxygen, but when R50 is mixed with R14, the danger of the explosion is eliminated. Therefore, even if a mixed refrigerant leakage accident occurs, any explosion is not generated.
  • R245fa and R600, and R14 and R50 are beforehand mixed once in an incombustible state.
  • the mixed refrigerant of R245fa and R600, R404A, R508A, the mixed refrigerant of R14 and R50, and R740 are beforehand mixed, and introduced into the refrigerant circuit.
  • R245fa and R600, R404A, R5080A, R14 and R50, and R740 are introduced in this order from the refrigerant having the highest boiling point.
  • composition of the refrigerants includes, for example, 10.3 wt % of the mixed refrigerant of R245fa and R600, 28 wt % of R404A, 29.2 wt % of R508A, 26.4 wt % of the mixed refrigerant of R14 and R50 and 5.1 wt % of R740.
  • n-pentane in a range of 0.5 to 2 wt % with respect to the total weight of the non-azeotropic refrigerants may be added to R404A.
  • the high-temperature high-pressure gas mixed refrigerant discharged from the compressor 20 flows into the radiator 39 via the discharge side pipe 20 D, and radiates heat in the radiator: Then, a part of n-pentane or R600 as an oil carrier refrigerant having a high boiling point and a satisfactory oil solubility in the mixed refrigerant is condensed and liquefied.
  • the mixed refrigerant discharged from the radiator 39 flows into the oil separator 40 , and a large part of lubricating oil of the compressor 20 mixed with the refrigerant and a part (a part of n-pentane or R600) of the refrigerant condensed and liquefied in the radiator 39 are fed back to the compressor 20 via the oil return tube 41 .
  • the refrigerant having higher purity and lower boiling point flows into the refrigerant circuit 38 after the cascade heat exchanger 43 , and the extremely low temperature can efficiently be obtained. Therefore, even the compressors 10 and 20 having the same capability can cool the inside of the storage chamber 4 as a cooling target having a larger volume to a predetermined extremely low temperature, and the storage capacity can be increased without enlarging the whole refrigeration apparatus 1 .
  • the refrigerant fed into the oil separator 40 is once cooled in the radiator 39 , and hence the temperature of the refrigerant flowing into the cascade heat exchanger 43 can be lowered.
  • the temperature of the refrigerant fed into the cascade heat exchanger 43 has heretofore been about +65° C., but the temperature can be lowered to about +45° C. in the present embodiment.
  • load to be applied to the compressor of the high-temperature-side refrigerant circuit 25 for cooling the refrigerant in the low-temperature-side refrigerant circuit 35 can be decreased.
  • the load to be applied to the compressor 20 constituting the low-temperature-side refrigerant circuit 35 can be decreased. In consequence, the operation efficiency of the whole refrigeration apparatus 1 can be improved.
  • Another mixed refrigerant itself is cooled to about ⁇ 40° C. to ⁇ 30° C. by the evaporator 34 in the cascade heat exchanger 43 to condense and liquefy a part of the refrigerants (a part of R245fa, R600, R404A and R508) having the high boiling point in the mixed refrigerant.
  • the mixed refrigerant discharged from the condensing pipe 42 of the cascade heat exchanger 43 flows into the first gas-liquid separator 46 through the drier 44 .
  • the refrigerants are not condensed yet, and have a gas state, and an only part of R245fa, R600, R404A and R508 is condensed and liquefied. Therefore, R14, R50 and R740 are separated to the gas-phase pipe 47 , and R245fa, R600, R404A and R508 are separated to the liquid-phase pipe 50 .
  • the refrigerant mixture which has flowed into the gas-phase pipe 47 performs heat exchange between the mixture and the first intermediate heat exchanger 48 , is condensed, and then reaches the second gas-liquid separator 49 .
  • the low-temperature refrigerant returning from the evaporation pipe 62 flows into the first intermediate heat exchanger 48 .
  • the liquid refrigerant which has flowed into the liquid-phase pipe 50 flows through the drier 51 to reach the capillary tube 52 where the pressure of the refrigerant is reduced. Afterward, the refrigerant flows into the first intermediate heat exchanger 48 to evaporate in the exchanger, thereby contributing to the cooling.
  • the first intermediate heat exchanger 48 has an intermediate temperature of about ⁇ 60° C. Therefore, R508 in the mixed refrigerant which has passed through the gas-phase pipe 47 is completely condensed and liquefied, and branched to the second gas-liquid separator 49 .
  • R14, R50 and R740 have a lower boiling point, and hence still have a gas state.
  • the drier 54 removes the water content from R508 branched by the second gas-liquid separator 49 , and the pressure of the refrigerant is reduced by the capillary tube 55 .
  • the refrigerant flows into the second intermediate heat exchanger 56 , R14, R50 and R740 in the gas-phase pipe 57 are cooled together with the low-temperature refrigerant returning from the evaporation pipe 62 , and R14 having the highest evaporation temperature among these refrigerants is condensed.
  • the second intermediate heat exchanger 56 has an intermediate temperature of about ⁇ 90° C.
  • the gas-phase pipe 57 passing through this second intermediate heat exchanger 56 subsequently passes through the third intermediate heat exchanger 58 and the fourth intermediate heat exchanger 59 .
  • the refrigerant immediately discharged from the evaporation pipe 62 is fed back to the fourth intermediate heat exchanger 59 .
  • the fourth intermediate heat exchanger 59 reaches a considerably low intermediate temperature of about ⁇ 130° C.
  • the refrigerants still having a gas phase state are successively condensed in the intermediate heat exchangers 48 , 56 , 58 and 59 by use of an evaporation temperature difference between the refrigerants in the low-temperature-side refrigerant circuit 38 , and an extremely low temperature of ⁇ 150° C. or less can be achieved in the evaporation pipe 42 as a final stage. Therefore, the evaporation pipe 62 is wound along the insulating material 9 side of the inner box 6 in a heat exchange manner, so that an in-chamber temperature of ⁇ 152° C. or less can be realized in the storage chamber 4 of the refrigeration apparatus 1 .
  • the refrigerant discharged from the evaporation pipe 62 successively flows into the fourth intermediate heat exchanger 59 , the third intermediate heat exchanger 58 , the second intermediate heat exchanger 56 and the first intermediate heat exchanger 48 , and the refrigerant joins the refrigerants evaporated in the respective heat exchangers, and returns the compressor 20 via the suction side pipe 20 S.
  • a large part of the oil mixed with the refrigerant and discharged from the compressor 20 is separated by the oil separator 40 and returned, to the compressor 20 .
  • the mist-like oil discharged from the oil separator 40 together with the refrigerant is returned to the compressor 20 in a state in which the oil is dissolved in R600 having high oil solubility. In consequence, the lubricating defect of the compressor 20 , or locking can be prevented.
  • R600 returns the compressor 20 while maintaining the liquid state, and is evaporated in this compressor 20 , so that the discharge temperature of the compressor 20 can be lowered.
  • the compressor 20 constituting the low-temperature-side refrigerant circuit 38 having the above constitution is subjected to ON-OFF control by a controller (not shown) based on the in-chamber temperature of the storage chamber 4 .
  • a controller not shown
  • the mixed refrigerant in the low-temperature-side refrigerant circuit 38 is collected in the expansion tank 65 via the check valve 67 having the expansion tank 65 direction as the forward direction.
  • the refrigerant in the refrigerant circuit 38 can remarkably quickly be collected in the expansion tank 65 via the check valve 67 .
  • the rise of the pressure in the refrigerant circuit 38 can be prevented.
  • the compressor 20 is started by the controller, the refrigerant is gradually returned from the expansion tank 65 to the refrigerant circuit 38 via the capillary tube 66 , and the starting load of the compressor 20 can be decreased.
  • the refrigerant circuit constituting the refrigeration apparatus 1 is constituted of the high-temperature-side refrigerant circuit 25 and the low-temperature-side refrigerant circuit 38 constituting independent refrigerant closed circuits so that the refrigerant discharged from the compressor 10 or 20 is condensed and then evaporated to exert a cooling function.
  • the low-temperature-side refrigerant circuit 38 has the compressor 20 , the condensing pipe 42 , the evaporation pipe 62 , a plurality of, specifically four intermediate heat exchangers 48 , 56 , 58 and 59 connected in series so that the refrigerant fed back from the evaporation pipe 62 circulates, and a plurality of, specifically three capillary tubes 42 , 55 and 61 .
  • a plurality of types of non-azeotropic mixed refrigerants are introduced, and the condensed refrigerant in the refrigerants fed through the condensing pipe 42 joins each intermediate heat exchanger via each capillary tube.
  • the non-condensed refrigerant in the refrigerants is cooled by the intermediate heat exchanger to successively condense the refrigerant having a lower boiling point.
  • the refrigerant having the lowest boiling point is allowed to flow into the evaporation pipe 62 through the final-stage capillary tube 61 .
  • the evaporator 34 of the high-temperature-side refrigerant circuit 25 and the condensing pipe 42 of the low-temperature-side refrigerant circuit 38 constitute the cascade heat exchanger 43 , and the extremely low temperature is obtained in the evaporation pipe 42 of the low-temperature-side refrigerant circuit 38 .
  • the present invention is not limited to this apparatus, and may be a refrigeration apparatus of a multidimensional multistage system.
  • FIG. 1 is a perspective view of a refrigeration apparatus to which the present invention is applied;
  • FIG. 2 is a front view of the refrigeration apparatus of FIG. 1 ;
  • FIG. 3 is a plan view of the refrigeration apparatus of FIG. 1 ;
  • FIG. 4 is a side view in a state in which a storage chamber is seen through the refrigeration apparatus of FIG. 1 ;
  • FIG. 5 is a perspective view of the refrigeration apparatus in a state in which a top panel is opened;
  • FIG. 6 is a refrigerant circuit diagram of the refrigeration apparatus of FIG. 1 ;
  • FIG. 7 is a refrigerant circuit diagram of a conventional refrigeration apparatus.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Lubricants (AREA)
US12/300,706 2006-05-15 2007-05-14 Refrigeration apparatus Abandoned US20100147017A1 (en)

Applications Claiming Priority (3)

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JP2006-135300 2006-05-15
JP2006135300A JP2007303794A (ja) 2006-05-15 2006-05-15 冷凍装置
PCT/JP2007/059847 WO2007132805A1 (ja) 2006-05-15 2007-05-14 冷凍装置

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JP (1) JP2007303794A (ja)
KR (1) KR101364317B1 (ja)
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US20180163997A1 (en) * 2015-08-26 2018-06-14 Panasonic Healthcare Holdings Co., Ltd. Ultra-low temperature freezer
US10907864B2 (en) * 2018-03-29 2021-02-02 Tokyo Electron Limited Cooling system
WO2022157489A1 (en) * 2021-01-19 2022-07-28 Stenhouse James Thornton Apparatus and method for cryo-preservation during transport and storage of items and/or substances

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JP2011112351A (ja) * 2009-11-30 2011-06-09 Sanyo Electric Co Ltd 冷凍装置
KR101905161B1 (ko) * 2010-05-12 2018-10-08 브룩스 오토메이션, 인크. 극저온 냉각용 시스템 및 방법
EP2642220A4 (en) * 2010-11-15 2017-04-19 Mitsubishi Electric Corporation Freezer
CN106642780B (zh) * 2016-12-30 2019-09-27 中原工学院 一种冷藏与冷冻用同步双循环复合系统
CN110305631A (zh) * 2019-07-03 2019-10-08 上海沛芾航天科技发展有限公司 一种用于环境试验箱的混合工质制冷剂

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US20180163997A1 (en) * 2015-08-26 2018-06-14 Panasonic Healthcare Holdings Co., Ltd. Ultra-low temperature freezer
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US10907864B2 (en) * 2018-03-29 2021-02-02 Tokyo Electron Limited Cooling system
WO2022157489A1 (en) * 2021-01-19 2022-07-28 Stenhouse James Thornton Apparatus and method for cryo-preservation during transport and storage of items and/or substances
GB2618473A (en) * 2021-01-19 2023-11-08 Thornton Stenhouse James Apparatus and method for cryo-preservation during transport and storage of items and/or substances

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CN101443602B (zh) 2012-08-22
KR20090014274A (ko) 2009-02-09
JP2007303794A (ja) 2007-11-22
CN101443602A (zh) 2009-05-27
WO2007132805A1 (ja) 2007-11-22
EP2019271A4 (en) 2012-09-12
EP2019271A1 (en) 2009-01-28

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