WO2007132805A1 - Système de réfrigération - Google Patents

Système de réfrigération Download PDF

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Publication number
WO2007132805A1
WO2007132805A1 PCT/JP2007/059847 JP2007059847W WO2007132805A1 WO 2007132805 A1 WO2007132805 A1 WO 2007132805A1 JP 2007059847 W JP2007059847 W JP 2007059847W WO 2007132805 A1 WO2007132805 A1 WO 2007132805A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
compressor
temperature side
refrigerant circuit
evaporator
Prior art date
Application number
PCT/JP2007/059847
Other languages
English (en)
Japanese (ja)
Inventor
Katsuji Takasugi
Original Assignee
Sanyo Electric Co., Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanyo Electric Co., Ltd. filed Critical Sanyo Electric Co., Ltd.
Priority to US12/300,706 priority Critical patent/US20100147017A1/en
Priority to EP07743282A priority patent/EP2019271A4/fr
Priority to KR1020087027849A priority patent/KR101364317B1/ko
Priority to CN2007800174016A priority patent/CN101443602B/zh
Publication of WO2007132805A1 publication Critical patent/WO2007132805A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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 so-called dual refrigeration system refrigeration apparatus in which two independent refrigerant circuits are configured and a heat exchanger is configured by an evaporator of a high temperature side refrigerant circuit and a condenser of a low temperature side refrigerant circuit. It is related.
  • FIG. 7 shows a refrigerant circuit diagram of the refrigeration apparatus 135 using the binary refrigeration apparatus.
  • the refrigerant circuit 100 includes a high temperature side refrigeration cycle 101 and a low temperature side refrigeration cycle 102.
  • the discharge side piping 103D of the compressor 103 constituting the high temperature side refrigeration cycle 101 is connected to the auxiliary condenser 105, and the auxiliary condenser 105 is connected to the frame pipe 104 (see the frame pipe 27 of the present application for the frame pipe). After that, it is connected to the condenser 107 via the oil cooler 106 of the compressor 103.
  • the condenser 107 is cooled by a condenser fan 116.
  • the outlet-side refrigerant pipe of the condenser 107 is connected to an evaporator 110 as an evaporator portion constituting the evaporator via a dryer 108 and a decompressor 109 in order.
  • An accumulator 111 is connected to the outlet-side refrigerant pipe of the evaporator 110, and the refrigerant pipe exiting the accumulator 111 is connected to the suction-side pipe 103 S of the compressor 103.
  • an oil separator 114 is connected to the discharge side pipe 113D of the compressor 113 constituting the low temperature side refrigeration cycle 102, and the refrigerant pipe connected to the outlet side of the oil separator 114 is It is connected to a condensing pipe 115 as a high temperature side pipe inserted into the evaporator 110.
  • the condensing pipe 115 constitutes a cascade heat exchanger 130 together with the evaporator 110.
  • the discharge pipe connected to the outlet side of the condensing pipe 115 is connected to the first gas-liquid separator 116 via the dryer 131, and the gas phase separated by the gas-liquid separator 116 is connected.
  • the refrigerant passes through the first intermediate heat exchanger 117 via the gas-phase piping, and the second gas-liquid separator 11 Flows into 8.
  • the liquid-phase refrigerant separated by the gas-liquid separator 116 flows into the first intermediate heat exchanger 117 through the dryer 119 and the decompressor 120 via the liquid-phase piping, and evaporates the gas-phase refrigerant. It is cooling.
  • the liquid-phase refrigerant separated by the second gas-liquid separator 118 passes through the dryer 121 through the liquid-phase piping and then flows into the second intermediate heat exchanger 123 via the decompressor 122.
  • the gas-phase refrigerant separated by the second gas-liquid separator 1 18 passes through the second intermediate heat exchanger 123 through the gas-phase piping and passes through the third intermediate heat exchanger 124. Further, it flows into the decompressor 126 through the dryer 125.
  • the decompressor 126 is connected to an evaporator pipe 127 as an evaporator disposed on the inner wall on the storage chamber side of the heat insulating box 132 of the refrigeration apparatus, and the evaporator pipe 127 is further connected to the third intermediate heat exchange. Connected to vessel 124.
  • the third intermediate heat exchanger 124 is connected to the second and first intermediate heat exchangers one after another, and is then connected to the suction-side piping 113S of the compressor 113.
  • An expansion tank 128 that stores refrigerant when the compressor 113 is stopped is connected to the suction side pipe 113S via a decompressor 129.
  • Patent Document 1 Japanese Patent No. 3208151
  • the refrigeration apparatus of the present invention includes a high-temperature side refrigerant circuit and a low-temperature side refrigerant circuit that constitute an independent refrigerant closed circuit that condenses and evaporates the refrigerant discharged from the compressor and exhibits a cooling action.
  • the low-temperature side refrigerant circuit has a compressor, a condenser, an evaporator, a plurality of intermediate heat exchangers connected in series so that a return refrigerant from the evaporator flows, and a plurality of decompression devices, Plural types of non-azeotropic refrigerant mixture are enclosed, and the condensed refrigerant in the refrigerant that has passed through the condenser is joined to the intermediate heat exchanger via the decompression device, and the uncondensed refrigerant in the refrigerant is removed by the intermediate heat exchanger.
  • the refrigerant having a lower boiling point is condensed sequentially, and the refrigerant having the lowest boiling point flows into the evaporator through the decompression device in the final stage, and the evaporator of the high-temperature side refrigerant circuit and the low-temperature side refrigerant circuit are condensed.
  • An ultra-low temperature is obtained by an evaporator, and is provided on the discharge side of the compressor in the low-temperature side refrigerant circuit, with an oil separator for separating the oil in the non-azeotropic refrigerant mixture and returning it to the compressor.
  • a heat radiator is interposed between the oil separator and the compressor.
  • the refrigeration apparatus according to the invention of claim 2 is the refrigerant according to the above invention, wherein the non-azeotropic refrigerant mixture has good compatibility with oil and has a high boiling point as compared with at least other refrigerants. Is included.
  • the present invention is provided with a high-temperature side refrigerant circuit and a low-temperature side refrigerant circuit that constitute an independent refrigerant closed circuit that exhibits a cooling action by condensing and evaporating the refrigerant discharged from the compressor,
  • the low-temperature side refrigerant circuit has a compressor, a condenser, an evaporator, a plurality of intermediate heat exchangers connected in series so that the return refrigerant from the evaporator flows, and a plurality of decompression devices.
  • the condensed refrigerant in the refrigerant that has passed through the condenser is joined to the intermediate heat exchanger via the pressure reducing device, and the intermediate heat exchanger cools the uncondensed refrigerant in the refrigerant.
  • the refrigerant having a lower boiling point is condensed sequentially, and the refrigerant having the lowest boiling point is introduced into the evaporator through the decompressor of the final stage, and the evaporator of the high-temperature side refrigerant circuit is lowered.
  • a refrigeration system that forms a cascade heat exchanger with the condenser of the warm side refrigerant circuit and obtains ultra-low temperature with the evaporator of the cold side refrigerant circuit, it is provided on the discharge side of the compressor of the cold side refrigerant circuit and is non-azeotropic
  • An oil separator for separating the oil in the mixed refrigerant and returning it to the compressor is provided, and a radiator is interposed between the oil separator and the compressor so that each refrigerant in the low-temperature side refrigerant circuit is Using the difference in evaporation temperature, the refrigerant that is still in the gas phase can be condensed one after another using multiple heat exchangers, and an ultra-low temperature of 150 ° C can be achieved in the final stage evaporator.
  • the radiator can be used as a cascade heat exchanger of the low-temperature side refrigerant circuit. It becomes possible to reduce the temperature of the refrigerant entering. As a result, it is possible to reduce the load on the compressors of both refrigerant circuits and to improve the operation efficiency.
  • the non-azeotropic refrigerant mixture has at least good compatibility with oil and has a high boiling point as compared with other refrigerants.
  • the oil carrier refrigerant mixed with the non-azeotropic refrigerant mixture is liquefied by the radiator and returned to the oil separator power compressor together with the oil. Will flow to the circuit after the cascade heat exchanger, and ultra-low temperature can be obtained more efficiently.
  • 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 perspective view of a storage chamber 4 of the refrigeration apparatus 1.
  • FIG. 5 shows a perspective view of the refrigeration apparatus 1 with the top panel 5 opened.
  • the refrigeration apparatus 1 of the present embodiment is suitable for ultra-low temperature storage of, for example, a living tissue or specimen that is stored at a low temperature for a long period of time, and includes a heat insulating box 2 that opens to the upper surface, and a side of the heat insulating box 2 And the machine room 3 in which the compressor 10 and the like are installed.
  • the heat insulating box 2 is composed of a steel plate outer box 6 having an open upper surface, a metal inner box 7 such as aluminum having good thermal conductivity, and a gap between the upper ends of both boxes 6, 7.
  • the inside of the inner box 7 is a shellfish storage room 4 whose upper surface is open.
  • a heat insulating box that partitions the storage chamber 4 from the outside air. 2 is required to have a greater heat insulation capacity than the low temperature where the internal temperature is set to around 0 ° C. For this reason, in order to ensure the heat insulation capacity only by the heat insulating material 9 made of polyurethane resin as described above, it must be formed extremely thick, and with the limited main body dimensions, the storage capacity in the storage chamber 4 is reduced. There are problems that cannot be secured sufficiently.
  • the heat insulating box 2 in the present embodiment is made of glass wool on each inner wall surface of the side wall 6C located on the opposite side to the side on which the front wall 6A, the rear wall 6B and the machine room 3 of the outer box 6 are provided.
  • the vacuum heat insulation panel 12 is arranged and temporarily fixed with double-sided adhesive tape, and then the heat insulation material 9 is filled between these boxes 6 and 7 by an in-situ foaming method.
  • the vacuum heat insulation panel 12 stores glass wool having heat insulation in a container made of a multilayer film made of aluminum, synthetic resin or the like that does not have air permeability. After that, the air in the container is discharged by a predetermined evacuation means, and the opening of the container is joined by thermal welding. For this reason, the vacuum heat insulation panel 12 can obtain the same heat insulation effect while reducing the thickness of the heat insulating material 9 as compared with the conventional heat insulation performance.
  • an evaporator (evaporation pipe) 62 constituting a refrigerant circuit of a cooling device R, which will be described in detail later, is attached to the peripheral surface of the inner box 7 on the heat insulating material 9 side in a heat exchange manner.
  • the upper surface of the breaker 8 of the heat insulating box 2 configured as described above is formed in a step shape as shown in FIG. 2 and FIG. 4, and a heat insulating door is provided there through a packing (not shown). 13 is provided at one end, and in this embodiment, is pivotally provided by pivot members 14 and 14 around the rear end. Further, the upper opening of the storage chamber 4 is provided with an inner lid 15 made of a heat insulating material so as to be freely opened and closed. In addition, on the lower surface of the heat insulating door 13, there is a pressing portion configured to protrude downward.
  • the pressing portion of the heat insulating door 13 presses the inner lid 15, thereby closing the upper surface opening of the storage chamber 4 so that it can be opened and closed.
  • a handle portion 16 is provided at the other end of the heat insulating door 13, that is, the front end in the present embodiment, and the heat insulating door 13 is opened and closed by operating the handle portion 16.
  • the machine room 3 is provided by a side panel 3B that constitutes a side surface opposite to the front panel 3A, a rear panel (not shown) and the side on which the heat insulating box 2 is provided. It is The machine room 3 in this embodiment is provided with a partition plate 17 that divides the interior vertically. Below the partition plate 17, the compressors 10, 20 and the like constituting the cooling device R as described above are accommodated and installed. The front panel 3A and the side panel 3B located below the partition plate 17 are provided with ventilation holes. A slit 3C is formed.
  • an upper machine chamber 18 having an upper surface opened is provided above the partition plate 17, an upper machine chamber 18 having an upper surface opened is provided.
  • a top panel 5 is provided at the top opening of the upper machine room 18 so as to be pivotable around the rear end in this embodiment, so that the upper machine room 18 can be opened and closed. Obstructed.
  • the panel provided in front of the upper machine chamber 18 is an operation panel 21 for operating the refrigeration apparatus 1.
  • a measurement hole 19 is formed on a side surface of the upper machine room 18 on the heat insulating box 2 side.
  • the measurement hole 19 penetrates the outer box 6, the heat insulating material 9 and the inner box 7 constituting the heat insulating box 2 so as to communicate with the storage chamber 4 formed in the heat insulating box 2 provided adjacently. Formed.
  • the measurement hole 19 can insert a temperature sensor into the storage chamber 4 from the outside, and the wiring drawn out from the temperature sensor is connected to the external recording apparatus main body through the measurement hole 19. Then, the measurement hole 19 is closed by a plug 19A made of a special material that can be deformed in a sponge-like manner and has a heat insulating property. When the temperature sensor is not attached, the measurement hole 19 is thermally blocked by the stopper 19A.
  • the measurement hole 19 in the present embodiment is formed on the side surface of the heat insulating box 2 on the machine room 18 side, and thus the refrigeration apparatus 1 is provided. Even when it is installed adjacent to a wall or other equipment in an installation environment such as a laboratory, it is not necessary to have a special interval for using the measurement hole 19. As a result, the area required for installing the refrigeration apparatus 1 can be reduced, which is suitable for layout in a laboratory or the like.
  • the measurement hole 19 is formed in the wall surface of the heat insulation box 2 on the side adjacent to the machine room 3, the measurement hole 19 is configured to face the side other than the machine room 3 adjacent to the outside, that is, the outside. It is possible to dispose the vacuum insulation panel 12 as described above on the front and rear walls and side surfaces of the heat insulation box 2 without affecting the position where the measurement hole 19 is formed. As a result, the amount of cold heat leakage in the storage chamber 4 can be reduced, and wasteful use of cooling energy can be suppressed.
  • the measurement hole 19 in the present embodiment can be concealed by the top panel 5 that can open and close the upper surface opening of the upper machine room 18, the measurement hole 19 is not exposed to the appearance. It is possible to improve the appearance. Also, by opening the top panel 5, it becomes possible to easily operate the measurement hole 19, and workability can be improved. Further, by removing the partition plate 17, it becomes easy to operate the devices constituting the other cooling devices R installed below the partition plate 17, and it becomes possible to improve the maintenance work.
  • the top panel 5 can be used as a work side stand by closing the inside of the machine room 18 except when the measurement hole 19 is operated. Thus, it is suitable for the delivery work of articles such as samples into the storage chamber 4.
  • the measurement hole 19 is concealed by the top panel 5 that closes the upper surface opening of the upper machine chamber 18, but the measurement hole 19 is not limited to this. A cover member for concealing the measurement hole 19 may be provided in the vicinity.
  • the refrigerant circuit of the refrigeration apparatus 1 in this embodiment includes 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 as independent multi-stage multi-stage refrigerant circuits. It is composed of a two-stage and two-stage refrigerant circuit.
  • the compressor 10 constituting the high temperature side refrigerant circuit 25 is an electric compressor using a one-phase or three-phase AC power supply, and the discharge side pipe 10D of the compressor 10 is connected to the auxiliary condenser 26. .
  • the auxiliary condenser 26 is connected to a refrigerant pipe 27 (hereinafter referred to as a frame pipe) disposed on the back side of the opening edge in order to heat the opening edge of the storage chamber 4 and prevent dew condensation.
  • the frame pipe 27 is connected to the condenser 28 after being connected to the oil cooler 29 of the compressor 10.
  • the refrigerant pipe exiting the condenser 28 is connected to the oil cooler 30 of the compressor 20 constituting the low-temperature side refrigerant circuit 38, and then connected to the condenser 31.
  • the refrigerant pipe exiting the condenser 31 Are connected to an evaporator 34 as an evaporator portion constituting the evaporator through a dryer 32 and a cavity tube 33 as a decompression device in order.
  • An accumulator 35 serving as a refrigerant reservoir is connected to the outlet-side refrigerant pipe of the evaporator 34, and the refrigerant pipe exiting the accumulator 35 is connected to the suction-side pipe 10 S of the compressor 10.
  • the auxiliary condenser 26 and the condensers 28 and 31 in this embodiment are configured as an integral condenser and are cooled by the condenser blower 36.
  • the high temperature side refrigerant circuit 25 is filled with a refrigerant composed of R407D and n-pentane as a non-azeotropic refrigerant having different boiling points.
  • R407D includes R32 (difluoromethane: CH F), R125 (pentafluoroethane: CHF CF), and R134a (l, 1, 1, 2-tetrafluoroethane: C
  • the high-temperature gaseous refrigerant discharged from the compressor 10 is supplied from the auxiliary condenser 26, the frame pipe 27, the oil cooler 29, the condenser 28, and the low-temperature side refrigerant circuit 38 in the compressor 20 oil cooler 30. Then, after being condensed in the condenser 31 and converted into the heat radiation liquid, the moisture contained in the dryer 32 is removed, decompressed by the capillary tube 33, and successively flows into the evaporator 34 to enter the refrigerants R32, R1 25 and R134a. Evaporates, absorbs the heat of vaporization from the surroundings, cools the evaporator 34, and returns to the compressor 10 through the accumulator 35 as a refrigerant liquid reservoir.
  • the capacity of the compressor 10 is 1.5 HP, for example, and the final temperature reached by the evaporator 34 during operation is _27 ° C to _35 ° C.
  • the boiling point of n-pentane in the refrigerant is + 36.1 ° C, so it does not evaporate in the evaporator 34 and remains in a liquid state.
  • the function of returning the mixed oil that could not be absorbed by the lubricating oil of the compressor 10 and the dryer 32 to the compressor 10 while being dissolved therein and the evaporation of the liquid refrigerant in the compressor 10 The function of reducing the temperature of the compressor 10 is achieved.
  • the compressor 20 is an electric compressor that uses a one-phase or three-phase AC power supply like the compressor 10, and the discharge-side piping 20D of the compressor 20 includes
  • the oil separator 40 is connected through a radiator 39 composed of a wire capacitor.
  • the oil separator 40 is connected to an oil return pipe 41 that returns to the compressor 20.
  • the 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, together with the evaporator 34, constitutes a cascade heat exchanger 43.
  • the discharge pipe connected to the outlet side of the condensing pipe 42 is connected to the first gas-liquid separator 46 via the dryer 44.
  • the gas-phase refrigerant separated by the gas-liquid separator 46 passes through the first intermediate heat exchanger 48 via the gas-phase pipe 47 and flows into the second gas-liquid separator 49.
  • the liquid-phase refrigerant separated by the first gas-liquid separator 46 flows into the first intermediate heat exchanger 48 via the liquid-phase pipe 50, the dryer 51, and the capillary tube 52 as a decompression device. .
  • the liquid-phase refrigerant separated by the second gas-liquid separator 49 passes through the dryer 54 through the liquid-phase piping 53 and then through the capillary tube 55 serving as a decompression device, to the second intermediate heat exchanger 56. Flows into.
  • the gas-phase refrigerant separated by the second gas-liquid separator 54 passes through the second intermediate heat exchanger 56 via the gas-phase pipe 57, and the third and fourth intermediate heat exchangers 58,
  • the liquid is cooled and liquefied while passing through 59, and is passed through a dryer 68 through a pipe 68 as a decompression device. It flows into the rally tube 61.
  • the capillary tube 61 is connected to an evaporation pipe 62 as an evaporator, and the evaporation pipe 62 is further connected to a fourth intermediate heat exchanger 59 via a return pipe 69.
  • the fourth intermediate heat exchanger 59 is connected to the third, second, and first intermediate heat exchangers 58, 56, and 48 one after another, and is then connected to the suction side pipe 20S of the compressor 20. .
  • an expansion tank 65 for storing refrigerant when the compressor 20 is stopped is connected to the suction side pipe 20S via a capillary tube 66 as a decompression device.
  • the expansion tube 65 is connected to the capillary tube 66.
  • a check valve 67 with the direction as the forward direction is connected in parallel.
  • the low temperature side refrigerant circuit 38 includes R245fa, R600, R404A, R508, R14, R50, and R740 as seven kinds of mixed refrigerants having different boiling points ⁇ azeotropic? Kenggoi refrigerant S is sealed.
  • R245fa is 1,1,1,1,3,3-pentafluoropropane (CF CH CHF), R
  • R 600 is butane (CH 2 CH 2 CH 2).
  • the boiling point of R245fa is + 15.3.
  • the boiling point of C and R600 is -0.5 ° C. Therefore, by mixing these at a predetermined ratio, it can be used as an alternative to R21, which has a boiling point of + 8.9 ° C, which has been used in the past.
  • R600 is a flammable substance, it is made non-flammable by mixing it with non-flammable R245fa at a predetermined ratio, in this example R245fa / R600: 70/30. Shall be enclosed in In this example, R245fa is 70% by weight with respect to the total weight of R245fa and R600, and if it is more than that, it will be nonflammable. .
  • R404A is composed of R125 (pentafluoroethane: CHF CF), R143a (l, 1, 1, 1-trifluoroethane: CH CF), and R134a (l, 1, 1, 1, 2-tetrafluoroethane). : CH FCF), and the composition is 44% by weight of R125 force, 52% by weight of R143a, and 4% by weight of R134a.
  • the boiling point of the mixed refrigerant is -46.48 ° C. Therefore, it can be used as an alternative to R22, which has a boiling point of 140.8 ° C.
  • R508 is R23 (trifluoromethane: CHF) and R116 (hexafluoroethane: CF C)
  • composition is 39% by weight for R23 and 61% by weight for 116.
  • the boiling point of the mixed refrigerant is -88.64 ° C.
  • R14 is tetrafluoromethane (carbon tetrafluoride: CF), and R50 is methane (CH ), R740 is argon (Ar). Their boiling points are: R14 force S—127. 9 ° C, R50 force S—1 61.5. C, R740 force S—185.86. C.
  • R50 has a danger of explosion when combined with oxygen, but mixing with R14 eliminates the danger of explosion. Therefore, even if a mixed refrigerant leakage accident occurs, no explosion will occur.
  • R245fa and R600 and R14 and R50 are mixed in advance to make incombustible state, then mixed refrigerant of R245fa and R600, R404A, R508A, The mixed refrigerant of R14 and R50 and R740 are mixed in advance and sealed in the refrigerant circuit.
  • each refrigerant for example, R245fa and mixed refrigerant force 3 weight 0/0 of R600, R404A force S28 weight 0/0, R508A force 29.2 wt 0/0, R14 and R50 refrigerant mixture of 26.4 wt %, R740 force S5. 1% by weight.
  • n- ⁇ ntan in the range of 0.5-2% by weight with respect to the total weight of the non-azeotropic refrigerant
  • R404A 4% by weight of n- ⁇ ntan (in the range of 0.5-2% by weight with respect to the total weight of the non-azeotropic refrigerant)
  • the mixed refrigerant that has passed through the radiator 39 flows into the oil separator 40, and most of the lubricating oil of the compressor 20 mixed with the refrigerant and a part of the refrigerant condensed and liquefied by the radiator 39. (n—pentane, part of R600) is returned to the compressor 20 through the oil return pipe 41.
  • the low-boiling point refrigerant having higher purity flows through the refrigerant circuit 38 downstream from the cascade heat exchanger 43, and it is possible to efficiently obtain an ultra-low temperature.
  • even the compressors 10 and 20 having the same capacity can cool the interior of the storage chamber 4 to be cooled to a predetermined ultra-low temperature, and the overall size of the refrigeration apparatus 1 is increased. It is possible to increase the storage capacity without doing so.
  • the temperature of the refrigerant entering the cascade heat exchanger 43 can be lowered. It becomes ability. Specifically, conventionally, the temperature of the refrigerant flowing into the cascade heat exchanger 43 In the present embodiment, the temperature of about + 65 ° C can be lowered to about + 45 ° C.
  • the other mixed refrigerants themselves are cooled by the cascade heat exchanger 43 from the evaporator 34 to about _40 ° C to -30 ° C, and some refrigerants with high boiling points in the mixed refrigerants (R245fa, R600, R404A , Part of R508).
  • the mixed refrigerant that has exited the condensation pipe 42 of the cascade heat exchanger 43 flows into the first gas-liquid separator 46 through the dryer 44.
  • R14, R50, and R740 in the mixed refrigerant are still not condensed because they have very low boiling points, and only some of R245fa, R600, R404A, and R508 are condensed and liquefied.
  • R14, R50 and R740 are separated into gas phase self-tube 47, and R245fa, R600, R404A and R508A are separated into liquid phase pipe 50.
  • the refrigerant mixture flowing into the gas-phase pipe 47 is condensed by exchanging heat with the first intermediate heat exchanger 48, 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, and the liquid refrigerant flowing into the liquid-phase pipe 50 is depressurized by the capillary tube 52 through the dryer 51.
  • a part of the uncondensed R14, R50, R740, and R508 is cooled.
  • the intermediate temperature of heat exchanger 48 is about -60 ° C.
  • R508 in the mixed refrigerant that has passed through the gas-phase pipe 47 is completely condensed and liquefied, and is divided into the second gas-liquid separator 49.
  • R14, R50, and R740 are still in a gas state because of their lower boiling points.
  • the second intermediate heat exchanger 56 the R508 separated by the second gas-liquid separator 49 is dehydrated by the dryer 54 and decompressed by the capillary tube 55, and then the second intermediate heat exchanger 56 R14, R50, and R740 in the gas-phase piping 57 are cooled together with the low-temperature refrigerant that flows into the intermediate heat exchanger 56 and returns from the evaporation pipe 62.
  • the evaporation temperature is the highest, and R14 is condensed. Let this As a result, the intermediate temperature of the second intermediate heat exchanger 56 is about -90 ° C.
  • the gas-phase pipe 57 passing through the second intermediate heat exchanger 56 passes through the fourth intermediate heat exchanger 59 via the third intermediate heat exchanger 58.
  • the refrigerant immediately after leaving the evaporator 62 is returned to the fourth intermediate heat exchanger 59.
  • the intermediate temperature of the fourth intermediate heat exchanger 59 is about ⁇ 130 ° C. A fairly low temperature is reached.
  • the intermediate heat exchangers 48, 56, 58, 59 condense the refrigerant still in a gas phase state one after another, In the final stage of the evaporation pipe 42, an ultra-low temperature of 150 ° C or less can be achieved. Therefore, the evaporation pipe 62 is configured to be heat-exchanged along the heat insulating material 9 side of the inner box 6 so that the inside temperature of the storage room 4 of the refrigeration apparatus 1 is 152 ° C. or lower. It can be realized.
  • the refrigerant that has left the evaporating pipe 62 passes to 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 one after another.
  • the refrigerant flows in, merges with the refrigerant evaporated in each heat exchanger, and returns to the compressor 20 from the suction pipe 20S.
  • the compressor 20 constituting the low-temperature side refrigerant circuit 38 as described above is subjected to ON-OFF control by a control device (not shown) based on the internal temperature in the storage chamber 4.
  • a control device not shown
  • the mixed refrigerant in the low temperature side refrigerant circuit 38 is Recovered in expansion tank 65 via check valve 67 with expansion tank 65 in the forward direction
  • the refrigerant circuit 3 8 can be connected via the check valve 67 very quickly. This refrigerant can be recovered in the expansion tank 65.
  • the pressure in the refrigerant circuit 38 can be quickly balanced, and the compressor 20 can be restarted.
  • the compressor 20 can be restarted smoothly without applying a load to the compressor 20. This significantly improves the operating efficiency of the compressor 20 by significantly reducing the time required for the refrigerant circuit 38 to reach the equilibrium pressure at the time of starting the compressor, for example, shortening the time required for the pruning down operation. It is possible to improve convenience.
  • the refrigerant circuit constituting the refrigeration apparatus 1 condenses the refrigerant discharged from the compressor 10 or 20, respectively, and then evaporates to constitute an independent refrigerant closed circuit that exhibits a cooling action.
  • the low-temperature side refrigerant circuit 38 is configured so that the compressor 20, the condensing pipe 42, the evaporation pipe 62, and the return refrigerant from the evaporation pipe 62 circulate.
  • a plurality of, in particular, four intermediate heat exchangers 48, 56, 58, 59 connected in series, and a plurality of, eg white birch, have three capillary tubes 42, 55, 61
  • a plurality of types of non-azeotropic refrigerant mixtures are enclosed, and condensed refrigerant in the refrigerant that has passed through the condensation pipe 42 is joined to each intermediate heat exchanger via each capillary tube, and the intermediate heat exchanger uses the intermediate heat exchanger.
  • the refrigerant with a lower boiling point is condensed sequentially.
  • the lowest boiling point refrigerant flows into the evaporation pipe 62 through the last stage capillary tube 61, and cascade heat exchange is performed between the evaporator 34 of the high temperature side refrigerant circuit 25 and the condensing pipe 42 of the low temperature side refrigerant circuit 38. 43, and at the evaporation pipe 42 of the low-temperature side refrigerant circuit 38
  • the present invention is not limited to this, and may be a multi-element multi-stage refrigeration apparatus.
  • 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.
  • FIG. 3 is a plan view of the refrigeration apparatus of FIG.
  • FIG. 4 is a side view of the refrigeration apparatus shown in FIG.
  • FIG. 5 is a perspective view of the refrigeration apparatus with the top panel opened.
  • FIG. 6 is a refrigerant circuit diagram of the refrigeration apparatus of FIG.
  • 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)

Abstract

L'invention concerne un système de réfrigération dans lequel la charge appliquée sur un compresseur peut être réduite, et l'efficacité de fonctionnement accrue. Dans un système de réfrigération multiétage appelé binaire (1) dans lequel un échangeur de chaleur en cascade (43) est constitué d'un évaporateur (34) de circuit de fluide frigorigène latéral haute température (25) et d'un conduit de condensation (42) de circuit de fluide frigorigène latéral basse température (38), et une température cryogénique est atteinte grâce à un conduit d'évaporation (62) du circuit de fluide frigorigène latéral basse température (38), un séparateur d'huile (43) destiné à séparer l'huile du fluide frigorigène mélangé non azéotropique et à renvoyer cette huile au compresseur (20) est situé du côté de distribution du compresseur (20) du circuit de fluide frigorigène latéral basse température (38), et un radiateur (39) est intercalé entre le séparateur d'huile (43) et le compresseur (20).
PCT/JP2007/059847 2006-05-15 2007-05-14 Système de réfrigération WO2007132805A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US12/300,706 US20100147017A1 (en) 2006-05-15 2007-05-14 Refrigeration apparatus
EP07743282A EP2019271A4 (fr) 2006-05-15 2007-05-14 Système de réfrigération
KR1020087027849A KR101364317B1 (ko) 2006-05-15 2007-05-14 냉동 장치
CN2007800174016A CN101443602B (zh) 2006-05-15 2007-05-14 冷冻装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006-135300 2006-05-15
JP2006135300A JP2007303794A (ja) 2006-05-15 2006-05-15 冷凍装置

Publications (1)

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WO2007132805A1 true WO2007132805A1 (fr) 2007-11-22

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US (1) US20100147017A1 (fr)
EP (1) EP2019271A4 (fr)
JP (1) JP2007303794A (fr)
KR (1) KR101364317B1 (fr)
CN (1) CN101443602B (fr)
WO (1) WO2007132805A1 (fr)

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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 (fr) * 2010-11-15 2017-04-19 Mitsubishi Electric Corporation Congélateur
JP6431986B2 (ja) * 2015-08-26 2018-11-28 Ｐｈｃホールディングス株式会社 超低温フリーザ
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
JP6994419B2 (ja) * 2018-03-29 2022-01-14 東京エレクトロン株式会社 冷却システム
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
GB202100707D0 (en) * 2021-01-19 2021-03-03 Stratox Ltd Apparatus and method for cryo-preservation during transport and storage of items and/or substances

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KR101364317B1 (ko) 2014-02-18
CN101443602B (zh) 2012-08-22
KR20090014274A (ko) 2009-02-09
JP2007303794A (ja) 2007-11-22
US20100147017A1 (en) 2010-06-17
CN101443602A (zh) 2009-05-27
EP2019271A4 (fr) 2012-09-12
EP2019271A1 (fr) 2009-01-28

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