EP2333459A2 - Appareil de réfrigération - Google Patents

Appareil de réfrigération Download PDF

Info

Publication number: EP2333459A2
Authority: EP; European Patent Office
Prior art keywords: refrigerant; evaporator; piping line; capillary tube; compressor
Prior art date: 2009-11-30
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 Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.): Withdrawn

Application number

EP10015097A

Other languages

German (de)

English (en)

Other versions

EP2333459A3 (fr

Inventor

Susumu Kobayashi

Fukuji Yoshida

Jiro Yuzawa

Hiroyuki Sato

Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

PHC Corp

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.)

2009-11-30

Filing date

2010-11-29

Publication date

2011-06-15

2010-11-29 Application filed by Sanyo Electric Co Ltd filed Critical Sanyo Electric Co Ltd

2011-06-15 Publication of EP2333459A2 publication Critical patent/EP2333459A2/fr

2011-09-21 Publication of EP2333459A3 publication Critical patent/EP2333459A3/fr

Status Withdrawn legal-status Critical Current

Images

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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/37—Capillary tubes
- 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
- F25B2400/05—Compression system with heat exchange between particular parts of the system
- F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—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
- F25B2400/05—Compression system with heat exchange between particular parts of the system
- F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle

Definitions

the present invention relates to a refrigerating apparatus which condenses a refrigerant discharged from a compressor and then evaporates the refrigerant by an evaporator to exert a cooling function.
a non-azeotropic mixed refrigerant including butane, ethylene and R14 (carbon tetrafluoride: CF 4 ) or a non-azeotropic mixed refrigerant including butane, ethane and R14 is introduced in a refrigerant circuit, to secure handleability of the refrigerant in the refrigerating apparatus owing to operability of butane having a high boiling point in such non-azeotropic mixed refrigerant gases, at ordinary temperature.
ethane or ethylene having a remarkably low boiling point is evaporated by the evaporator, thereby setting a temperature of the inside of a storage chamber to an ultralow temperature below -60°C.
the present invention has been developed to solve a conventional technical problem, and an object thereof is to provide a refrigerating apparatus which.can more efficiently cool the inside of a storage chamber to an ultralow temperature.
a refrigerating apparatus of the present invention of a first aspect condenses a refrigerant discharged from a compressor, reduces a pressure of the refrigerant by a capillary tube, and evaporates the refrigerant by an evaporator to exert a cooling function, characterized in that the capillary tube is passed through a suction piping line through which the refrigerant returning from the evaporator to the compressor flows, to constitute a double tube structure.
a refrigerating apparatus of the present invention of a second aspect comprises a high temperature side refrigerant circuit and a low temperature side refrigerant circuit to constitute independent closed refrigerant circuits, each of which condenses a refrigerant discharged from a compressor, reduces a pressure of the refrigerant by a capillary tube and evaporates the refrigerant by an evaporator to exert a cooling function, the evaporator of the high temperature side refrigerant circuit and a condenser of the low temperature side refrigerant circuit constituting a cascade heat exchanger, the evaporator of the low temperature side refrigerant circuit being configured to exert a final cooling function, characterized in that the capillary tube of the low temperature side refrigerant circuit is passed through a suction piping line through which the refrigerant returning from the evaporator to the compressor of the low temperature side refrigerant circuit flows, to constitute a double tube structure.
a refrigerating apparatus of the present invention of a third aspect is a refrigerating apparatus which comprises a compressor, a condenser, an evaporator, a single or a plurality of intermediate heat exchangers connected so that a refrigerant returning from the evaporator circulates therethrough and a plurality of capillary tubes and into which a plurality of types of non-azeotropic mixed refrigerants are introduced and which allows a condensed refrigerant of the refrigerants flowing through the condenser to join the refrigerants in the intermediate heat exchangers through the capillary tubes, cools a non-condensed refrigerant of the refrigerants in the intermediate heat exchangers to condense the refrigerant having a lower boiling point, and evaporates the refrigerant having the lowest boiling point by the evaporator through the capillary tube of the final stage to exert a cooling function, characterized in that the capillary tube of the final stage is passed through a suction
a refrigerating apparatus of the present invention of a fourth aspect comprises a high temperature side refrigerant circuit and a low temperature side refrigerant circuit to constitute independent closed refrigerant circuits, each of which condenses a refrigerant discharged from a compressor, reduces a pressure of the refrigerant by a capillary tube and evaporates the refrigerant by an evaporator to exert a cooling function, the low temperature side refrigerant circuit comprising the compressor, a condenser, the evaporator, a single or a plurality of intermediate heat exchangers connected so that the refrigerant returning from the evaporator circulates therethrough and a plurality of capillary tubes, a plurality of types of non-azeotropic mixed refrigerants being introduced, the refrigerating apparatus having a constitution which allows a condensed refrigerant of the refrigerant flowing through the evaporator to join the refrigerants in the intermediate heat exchangers through the capillary tubes, cool
a refrigerating apparatus of the present invention of a fifth aspect is characterized in that in the invention of the second or fourth aspect, the capillary tube of the high temperature side refrigerant circuit is passed through the suction piping line through which the refrigerant returning from the evaporator to the compressor of the high temperature side refrigerant circuit flows, to constitute the double tube structure.
a refrigerating apparatus of the present invention of a sixth aspect is characterized in that in the inventions of the above aspects, the suction piping line formed in the double tube structure by passing the capillary tube therethrough is surrounded with an insulating material.
a refrigerating apparatus of the present invention of a seventh aspect is characterized in that in the invention of the above aspects, a flow of the refrigerant through the capillary tube and a flow of the refrigerant through the suction piping line outside the capillary tube form a counter flow.
the capillary tube is passed through the suction piping line through which the refrigerant returning from the evaporator to the compressor flows, to constitute the double tube structure. Therefore, efficiency of the heat exchange between the refrigerant in the suction piping line and the refrigerant in the capillary tube can be enhanced to improve a performance of the refrigerating apparatus.
the capillary tube is passed through the suction piping line just exiting from the evaporator to constitute the double tube structure, thereby enabling the heat exchange by conduction of heat transmitted along the wall surface of the whole periphery of the capillary tube.
the refrigerant having the lowest boiling point is efficiently cooled by the refrigerant returning from the evaporator, whereby the performance can remarkably be improved.
the refrigerating apparatus comprises the high temperature side refrigerant circuit and the low temperature side refrigerant circuit to constitute the independent closed refrigerant circuits, each of which condenses the refrigerant discharged from the compressor, reduces the pressure of the refrigerant by the capillary tube and evaporates the refrigerant by the evaporator to exert the cooling function.
the evaporator of the high temperature side refrigerant circuit and the condenser of the low temperature side refrigerant circuit constitute the cascade heat exchanger.
the evaporator of the low temperature side refrigerant circuit exerts the final cooling function.
the capillary tube of the low temperature side refrigerant circuit is passed through the suction piping line through which the refrigerant returning from the evaporator to the compressor of the low temperature side refrigerant circuit flows, to constitute the double tube structure. Therefore, the efficiency of the heat exchange between the refrigerant in the suction piping line and the refrigerant in the capillary tube can be enhanced to improve the performance.
the capillary tube of the low temperature side refrigerant circuit is passed through the suction piping line just exiting from the evaporator to constitute the double tube structure, thereby enabling the heat exchange by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube.
the refrigerant having the lowest boiling point is efficiently cooled by the refrigerant returning from the evaporator of the low temperature side refrigerant circuit, whereby the performance can remarkably be improved.
the refrigerating apparatus comprises the compressor, the condenser, the evaporator, the single or the plurality of intermediate heat exchangers connected so that the refrigerant returning from this evaporator circulates therethrough, and the plurality of capillary tubes.
the plurality of types of non-azeotropic mixed refrigerants are introduced.
the refrigerating apparatus allows the condensed refrigerant of the refrigerants flowing through the condenser to join the refrigerants in the intermediate heat exchangers through the capillary tubes, cools the non-condensed refrigerant of the refrigerants in the intermediate heat exchangers to condense the refrigerant having the lower boiling point, and evaporates the refrigerant having the lowest boiling point by the evaporator through the capillary tube of the final stage to exert the cooling function.
the capillary tube of the final stage is passed through the suction piping line through which the refrigerant returning from the evaporator to the compressor flows, to constitute the double tube structure. Therefore, the efficiency of the heat exchange between the refrigerant in the suction piping line and the refrigerant in the capillary tube can be enhanced to improve the performance.
the capillary tube is passed through the suction piping line just exiting from the evaporator to constitute the double tube structure, thereby enabling the heat exchange by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube.
the refrigerant having the lowest boiling point is efficiently cooled by the refrigerant returning from the evaporator, whereby the performance can remarkably be improved.
the refrigerating apparatus comprises the high temperature side refrigerant circuit and the low temperature side refrigerant circuit to constitute the independent closed refrigerant circuits, each of which condenses the refrigerant discharged from the compressor, reduces the pressure of the refrigerant by the capillary tube and evaporates the refrigerant by the evaporator to exert the cooling function.
This low temperature side refrigerant circuit comprises the compressor, the condenser, the evaporator, the single or the plurality of intermediate heat exchangers connected so that the refrigerant returning from this evaporator circulates therethrough and the plurality of capillary tubes.
the plurality of types of non-azeotropic mixed refrigerants are introduced.
the refrigerating apparatus has the constitution which allows the condensed refrigerant of the refrigerants flowing through the evaporator to join the refrigerants in the intermediate heat exchangers through the capillary tubes, cools the non-condensed refrigerant of the refrigerants in the intermediate heat exchangers to condense the refrigerant having the lower boiling point, and evaporates the refrigerant having the lowest boiling point by the evaporator through the capillary tube of the final stage to exert the cooling function.
the evaporator of the high temperature side refrigerant circuit and the condenser of the low temperature side refrigerant circuit constitute the cascade heat exchanger, and the evaporator of the low temperature side refrigerant circuit is configured to exert the final cooling function.
the capillary tube of the final stage of the low temperature side refrigerant circuit is passed through the suction piping line through which the refrigerant returning from the evaporator to the compressor of the low temperature side refrigerant circuit flows, to constitute the double tube structure. Therefore, the efficiency of the heat exchange between the refrigerant in the suction piping line and the refrigerant in the capillary tube can be enhanced to improve the performance.
the capillary tube of the low temperature side refrigerant circuit is passed through the suction piping line just exiting from the evaporator to constitute the double tube structure, thereby enabling the heat exchange by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube.
the refrigerant having the lowest boiling point is efficiently cooled by the refrigerant returning from the evaporator of the low temperature side refrigerant circuit, whereby the performance can remarkably be improved.
the capillary tube of the high temperature side refrigerant circuit is passed through the suction piping line through which the refrigerant returning from the evaporator to the compressor of the high temperature side refrigerant circuit flows, to constitute the double tube structure. Therefore, also in the high temperature side refrigerant circuit, the efficiency of the heat exchange between the refrigerant in the suction piping line and the refrigerant in the capillary tube can further be enhanced to further improve the performance of the refrigerating apparatus.
the suction piping line formed in the double tube structure by passing the capillary tube therethrough is surrounded with the insulating material, which can further enhance the efficiency of the heat exchange.
the flow of the refrigerant through the capillary tube and the flow of the refrigerant through the suction piping line outside the capillary tube form the counter flow, which can further improve a heat exchange ability.
FIG. 1 is a side view of an ultralow temperature refrigerator 1 to which a refrigerating apparatus of the present invention is applied.
the ultralow temperature refrigerator 1 is used, for example, to store refrigerated food to be stored at a low temperature for a long period of time or to store an anatomy, a specimen or the like at an ultralow temperature.
a main body of the refrigerator is constituted of an insulating box member 2 having an open upper surface, and a mechanical chamber (not shown) which is positioned in the lower part of the insulating box member 2 and in which a compressor 14 and the like are installed to constitute a refrigerant circuit of a refrigerating apparatus R1 of the present embodiment therein.
the insulating box member 2 is constituted of an outer box 3 and an inner box 4 both made of steel plates and having open upper surfaces; a breaker 5 made of a synthetic resin and connecting the upper ends of both the boxes 3 and 4 to each other; and a polyurethane resin insulating material 7 charged in a space surrounded by the outer box 3, the inner box 4 and the breaker 5 by an in-situ foaming system.
the inside of the inner box 4 is a storage chamber 8 having an open upper surface.
the insulating box member 2 which insulates the inside of the storage chamber 8 from outside air, requires a larger insulating ability as compared with a low temperature refrigerator where the in-chamber temperature is set around 0°C. Therefore, when the insulating ability is acquired only by the polyurethane resin insulating material 7 described above, the material has to be formed with a considerable thickness, which causes a problem that the storage amount of the storage chamber 8 cannot sufficiently be acquired with a limited main body dimension.
a vacuum insulating material such as glass wool is disposed on the inner wall surface of the outer box 3, and the thickness of the polyurethane resin insulating material 7 is set to a small dimension in accordance with the insulating ability of the vacuum insulating material.
the upper surface of the breaker 5 is formed in a staircase pattern, and an insulating door 9 is provided rotatably around one end thereof, i.e., the rear end in the present embodiment via a packing 11.
the upper surface opening of the storage chamber 8 is openably closed with the insulating door 9.
the other end of the insulating door 9, i.e., the front end thereof in the present embodiment is provided with a grip portion 10, and the grip portion 10 is operated to open and close the insulating door 9.
an evaporator (a refrigerant piping line) 13 constituting the refrigerant circuit of the refrigerating apparatus R1 is attached to the peripheral surface of the inner box 4 on an insulating material 7 side so as to perform heat exchange (in the heat exchange manner).
the refrigerant circuit of the refrigerating apparatus R1 of the present embodiment has a constitution of a single unit/stage of a refrigerant circuit 12.
the compressor 14 constituting the refrigerant circuit 12 is an electromotive compressor using a single phase or three phase alternator.
the compressor 14 is connected to a disperse heater 20 in a constitution which once discharges a refrigerant compressed by the compressor 14 to the outside to radiate heat, returns the refrigerant into a shell of a sealed container and again discharges the refrigerant to a refrigerant discharge tube 31.
the refrigerant discharge tube 31 connected to the compressor 14 on a discharge side thereof is connected to a preliminary condenser 21.
the preliminary condenser 21 is connected to a frame pipe 22 for heating the opening edge of the storage chamber 8 to prevent dew condensation, and then connected to a condenser 15.
the refrigerant piping line exiting from the condenser 15 is connected to a dry core 17 and a condensing pipe 23.
the dry core 17 is water removal means for removing water from the refrigerant circuit 12.
the condensing pipe 23 constitutes a heat exchanger 16 together with a part of a suction piping line 32 exiting from the evaporator 13 and returning to the compressor 14.
the refrigerant piping line exiting from the condensing pipe 23 is connected to the evaporator 13 via a capillary tube 18 as a pressure reducing unit.
the capillary tube 18 is passed through a part (a piping line 32A) of the suction piping line 32 exiting from the evaporator 13 and returning to the compressor 14.
the capillary tube 18 is passed through the piping line 32A as a part of the suction piping line 32 positioned on a discharge side (the outlet side) of a header 26 provided on the discharge side of the evaporator 13 and on a suction side of the heat exchanger 16, to constitute a double tube structure as shown in FIG. 3 .
the linearly tubular capillary tube 18 is passed through the linearly tubular piping line 32A having a comparatively large diameter.
such a double tube is spirally wound as much as a plurality of stages.
the tube is wound so that the axial center of the piping line 32A coincides with the axial center of the capillary tube 18 as much as possible, to form the spiral double tube.
a gap is formed between the inner wall surface of the piping line 32A and the outer wall surface of the capillary tube 18 as consistently as possible.
the double tube is spirally wound as much as the plurality of stages to form the spiral double tube structure, thereby enabling miniaturization while sufficiently acquiring the length of the capillary tube 18 and sufficiently acquiring such a heat exchange portion of the double tube structure.
connection piping lines (not shown) having both end holes and side holes are attached to both ends of the piping line 32A, the ends of the capillary tube 18 are drawn from the side holes, respectively, and then the side holes are welded and sealed. Furthermore, one end of the connection piping line attached to the one end of the piping line 32A and a connecting portion of the piping line 32A are welded, the other end of the connection piping line is connected to the suction piping line 32 connected to the evaporator 13 on the discharge side thereof, and this connecting portion is welded.
connection piping line 32A attached to the other end of the piping line 32A and a connecting portion of the piping line 32A are welded, the other end of the connection piping line is connected to the suction piping line 32 leading to the heat exchanger 16, and this connecting portion is welded.
the piping line 32A formed in such a double tube structure is surrounded with an insulating material 35, whereby the double tube structure 25 of the present embodiment can be obtained.
the capillary tube has been disposed along the outer peripheral surface of the suction piping line so that the outer wall of the capillary tube can come in contact with the outer wall of the suction piping line in the heat exchange manner.
the suction piping line only linearly comes in contact with the capillary tube. Therefore, a heat exchange performance is so poor that the heat exchange cannot sufficiently be performed.
the capillary tube 18 is passed through the suction piping line 32 (the piping line 32A) to constitute the double tube structure as in the present invention, thereby performing the heat exchange between the refrigerant flowing through the capillary tube 18 and the refrigerant flowing through the suction piping line 32 by conduction of heat transmitted along the wall surface of the whole periphery of the capillary tube 18.
a heat exchange performance can remarkably be improved as compared with a conventional structure.
the whole outer periphery of the piping line 32A having the double tube structure is surrounded with the insulating material 35 as described above, whereby the structure is not easily influenced by the heat from the outside.
the refrigerant is allowed to flow through the capillary tube 18 inside the double tube structure and through the suction piping line 32 (the piping line 32A) outside the capillary tube 18 so as to form the counter flow of the refrigerant, whereby the heat exchange ability in the double tube structure 25 can further be improved.
the double tube structure 25 is disposed in the insulating material 7. Specifically, as shown in FIG. 1 , the double tube structure is removably received in the insulating material 7 under the heat exchanger 16 on the back surface side of the inner box 4.
the suction piping line 32 exiting from the double tube structure 25 is connected to the compressor 14 on the suction side thereof successively through the heat exchanger 16, a check valve 27 and an accumulator 28.
the preliminary condenser 21 and the condenser 15 have a constitution of an integral condenser, and are cooled by a condensing fan 29 as a blower for the condenser.
a mixed refrigerant of R245fa and R600 and a non-azeotropic mixed refrigerant of R23 and R14 are charged in the refrigerant circuit 12.
R245fa is 1,1,1,-3,3-pentafluoropropane (CF 3 CH 2 CHF 2 ) and has a boiling point of +15.3°C.
R600 is butane (C 4 H 10 ) and has a boiling point of -0.5°C.
R600 has a function of returning, to the compressor 14, a lubricant of the compressor 14 or mixed water which cannot be absorbed by the drier 17 in a state where the water is dissolved in R600.
R600 is a combustible substance.
R23 is trifluoromethane (CHF 3 ) and has a boiling point of -82.1°C.
R14 is tetrafluoromenthane (CF 4 ) and has a boiling point of -127.9°C.
composition of these mixed refrigerants in the present embodiment includes 64% by weight of the mixed refrigerant of R245fa and R600, 24% by weight of R23 and 12% by weight of R14 in total.
FIG. 2 arrows show the flow of the refrigerant circulating through the refrigerant circuit 12.
a high temperature gaseous refrigerant discharged from the compressor 14 is once discharged from the sealed container to the disperse heater 20 through a refrigerant discharge tube on a disperse heater 20 side, radiates heat and again returns into the shell of the sealed container.
the inside of the sealed container can be cooled by the refrigerant which has radiated the heat in the disperse heater 20 to lower the temperature thereof.
such a high temperature gaseous refrigerant is discharged from the sealed container through the refrigerant discharge tube 31, condensed by the preliminary condenser 21, the frame pipe 22 and the condenser 15 to radiate the heat, and is liquefied, followed by removing the water contained in the refrigerant by the dry core 17.
the refrigerant flows into the heat exchanger 16.
the heat exchanger 16 the heat exchange between the refrigerant from the condenser 15 and the low temperature refrigerant in the suction piping line 32 disposed in the heat exchange manner is performed, whereby the non-condensed refrigerant is cooled, condensed and liquefied.
the refrigerant flows into the capillary tube 18.
the heat exchange between the refrigerant in the capillary tube 18 and the refrigerant flowing through the suction piping line 32 disposed around the whole periphery of the capillary tube 18 is performed by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube 18.
the refrigerant having a pressure thereof reduced while lowering the temperature flows into the evaporator 13.
the refrigerants R14 and R23 take the heat from the ambient atmosphere to evaporate.
the refrigerants R14 and R23 evaporate in the evaporator 13 to exert a cooling function, thereby cooling the ambient atmosphere of the evaporator 13 to an ultralow temperature of -85°C.
the evaporator (the refrigerant piping line) 13 is wound along the inner box 4 on the insulating material 7 side in the heat exchange manner as described above, whereby the inside of the storage chamber 8 of the ultralow temperature refrigerator 1 can be set to an in-chamber temperature below -80°C by such cooling of the evaporator 13.
the refrigerant evaporated by the evaporator 13 exits from the evaporator 13 via the suction piping line 32 to return to the compressor 14 through the header 26, the double tube structure 25, the heat exchanger 16, the check valve 27 and the accumulator 28.
the finally reaching temperature of the evaporator 13 of the compressor 14 which is being operated is from -100°C to -60°C.
R245fa in the refrigerant has a boiling point of +15.3°C
R600 has a boiling point of -0.5°C. Therefore, the refrigerant does not evaporate but still has a liquid state in the evaporator 13, and hence the refrigerant hardly contributes to cooling.
R600 has a function of returning, to the compressor 14, the lubricant of the compressor 14 or the mixed water which cannot be absorbed by the dry core 17 in the state where the water is dissolved in R600, and the liquid refrigerant also has a function of evaporating in the compressor 14 to lower the temperature of the compressor 14.
the evaporation temperature in the evaporator 13 varies in accordance with the composition ratio of the non-azeotropic mixed refrigerant introduced in the refrigerant circuit 12.
the evaporator temperature, in-chamber temperature, high pressure side pressure and low pressure side pressure with respect to the composition ratio of each refrigerant will be described based on each experiment result in detail.
FIG. 4 is a graph showing the evaporator inlet temperature, the in-chamber temperature, the high pressure side pressure and the low pressure side pressure in a case where the weight of the mixed refrigerant of R245fa and R600 and the weight of R14 are set to be constant, while the weight of R23 is varied.
FIG. 4 is a graph showing the evaporator inlet temperature, the in-chamber temperature, the high pressure side pressure and the low pressure side pressure in a case where the weight of the mixed refrigerant of R245fa and R600 and the weight of R14 are set to be constant, while the weight of R23 is varied.
5 is a graph showing the evaporator inlet temperature, the in-chamber temperature, the high pressure side pressure and the low pressure side pressure in a case where the weight of the mixed refrigerant of R245fa and R600 and the weight of R23 are set to be constant, while the weight of R14 is varied.
the weight ratio of R23 with respect to the total weight of the introduced refrigerants is increased from 20.0% by weight to 42.0% by weight.
the inlet temperature of the evaporator 13 is -88.0°C
the in-chamber temperature is -71.0°C.
the weight ratio of R23 is 21.3% by weight
the inlet temperature of the evaporator 13 rapidly lowers to -95.9°C
the in-chamber temperature also lowers to -87.5°C.
the temperature only slightly rises, and in either case, the in-chamber temperature can be set below about -85°C.
the weight ratio of R14 with respect to the total weight of the introduced refrigerants is increased from 0.0% by weight to 14.1% by weight.
the inlet temperature of the evaporator 13 is -66.1°C
the in-chamber temperature is - 66.9°C.
the weight ratio of R14 is 1.8% by weight, the inlet temperature of the evaporator 13 rapidly lowers to -80.2°C, whereas the in-chamber temperature also lowers to -74.1°C.
the weight ratio of R14 is gradually increased, and in the present experiment, at 14.1% by weight, the inlet temperature of the evaporator 13 lowers to -98.9°C, whereas the in-chamber temperature lowers to -90.0°C.
R14 has a boiling point of -129.7°C. Therefore, it is then expected that when the weight ratio of R14 is increased, the temperature of the evaporator 13 and the in-chamber temperature further lower.
the high pressure side pressure rises, as the weight ratio of R14 increases. In consequence, there occurs a problem that when the weight ratio of R14 is increased to 20% by weight or more, the high pressure side pressure excessively increases to, for example, 3 MPa or more.
the rise of the high pressure side pressure causes a problem that an apparatus such as the compressor 14 is damaged or a problem that the start properties of the compressor 14 deteriorate. Therefore, when the in-chamber temperature is preferably set to a target temperature below -75°C, the weight ratio of the R14 is preferably set to a range of 3% by weight to 20% by weight of the total weight.
R23 has a boiling point of -82.1°C as described above. Therefore, only by R23, the temperature of the evaporator 13 cannot be set to a temperature which is not higher than the boiling point. However, as in the present invention, a predetermined amount, for example, about 5% or more by weight of R14 having a remarkably low boiling point is added, whereby the cooling function of R14 can constantly realize an ultralow temperature below -80°C as the evaporation temperature in the evaporator 13.
the total weight ratio of the mixed refrigerant of R245fa and R600 is from 40% by weight to 80% by weight with respect to the total weight, the weight ratio of R23 is from 15% by weight to 47% by weight, and the weight ratio of R14 is from 3% by weight to 20% by weight, whereby the incombustible non-azeotropic mixed refrigerant can realize the ultralow temperature so that the in-chamber temperature is below -70°C.
the total weight ratio of the mixed refrigerant of R245fa and R600 is from 49% by weight to 70% by weight with respect to the total weight
the weight ratio of R23 is from 21% by weight to 42% by weight
the weight ratio of R14 is from 9% by weight to 20% by weight
the storage of food, anatomy, specimen or the like for a long period of time can further be stabilized, and reliability can be improved.
the non-azeotropic mixed refrigerant is incombustible, the refrigerant can safely be used, handling properties are improved, and it is possible to avoid a disadvantage that when the mixed refrigerant leaks owing to the damage of the refrigerant piping line or the like, the refrigerant is combusted.
the ultralow temperature can be realized so that the in-chamber temperature is below -80°C.
the food, anatomy, specimen or the like can further stably be stored for a long period of time, and the reliability of the apparatus can be improved.
the refrigerant is not limited to R23.
R116 hexafluoroethane: CF 3 CF 3
the conventional refrigerant circuit hardly has to be changed in accordance with the change of the refrigerant composition, but the performance of the circuit can be maintained. Moreover, it is possible to cope with an environment problem such as depletion of ozone layer.
the capillary tube 18 is passed through the suction piping line 32 (the piping line 32A) through which the refrigerant returning from the evaporator 13 to the compressor 14 flows, constitute the double tube structure, whereby the efficiency of the heat exchange between the refrigerant in the piping line 32A and the refrigerant in the capillary tube 18 can be enhanced to improve the performance.
the capillary tube 18 is passed through the piping line 32A of the suction piping line 32 just exiting from the evaporator 13, to constitute the double tube structure which enables the heat exchange by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube 18. In consequence, the refrigerant returning from the evaporator 13 can efficiently cool the refrigerant having the lowest boiling point, and hence the performance can remarkably be improved.
the piping line 32A formed in the double tube structure by passing the capillary tube 18 therethrough is surrounded with the insulating material 35, whereby the heat exchange efficiency can further be enhanced.
the flow of the refrigerant through the capillary tube 18 and the flow of the refrigerant through the piping line 32A outside the capillary tube 18 form the counter flow, whereby the heat exchange ability can further be improved.
a so-called multistage refrigerating system is not used, but the ultralow temperature can be realized by a single stage refrigerating system as in the present embodiment, whereby the apparatus can be simplified and costs can be decreased.
the refrigerating apparatus of the present invention is not limited to the refrigerating apparatus R1 of the embodiment, and the present invention is effective as long as the refrigerant discharged from the compressor is condensed, has the pressure thereof reduced by the capillary tube, and is evaporated by the evaporator to exert the cooling function.
the temperature of the compressed gas may be lowered to the above temperature range by use of another known cooling means, to proceed with a targeted condensing process.
the present embodiment it has been described that there is introduced, in the refrigerant circuit 12, the non-azeotropic mixed refrigerant including R245fa, R600, R23 and R14, the non-azeotropic mixed refrigerant including R245fa, R600, R116 and R14, the non-azeotropic mixed refrigerant including R245fa, R600, R508A and R14 or the non-azeotropic mixed refrigerant including R245fa, R600, R508B and R14.
the present invention is not limited to this embodiment, and the present invention is also effective, when a single refrigerant is used.
FIG. 6 is a refrigerant circuit diagram of the embodiment having a constitution of the refrigerating apparatus for the ultralow temperature refrigerator 1 of FIG. 1 .
compressors 54 and 84 and the like constituting the refrigerant circuit of a refrigerating apparatus R2 are installed in a mechanical chamber (not shown) positioned in the lower part of an insulating box member 2 of the ultralow temperature refrigerator 1, and an evaporator (a refrigerant piping line) 83 is attached to the peripheral surface of an inner box 4 on an insulating material 7 side in a heat exchange manner, similarly to the evaporator 13 of Embodiment 1 described above.
the refrigerant circuit of the refrigerating apparatus R2 of the present embodiment is a multiunit (two units) single stage refrigerant circuit constituted of a high temperature side refrigerant circuit 52 and a low temperature side refrigerant circuit 82 constituting independent closed refrigerant circuits, respectively.
the compressor 54 constituting the high temperature side refrigerant circuit 52 is an electromotive compressor using a single phase or three phase alternator.
the compressor 54 is connected to a disperse heater 60, and has a constitution which once discharges a refrigerant compressed by the compressor 54 to the outside to radiate heat, returns the refrigerant into a shell of a sealed container and again discharges the refrigerant to a refrigerant discharge tube 71.
the refrigerant discharge tube 71 connected to the compressor 54 on a discharge side thereof is connected to a preliminary condenser 61.
the preliminary condenser 61 is connected to a frame pipe 62 for heating the opening edge of a storage chamber 8 to prevent dew condensation.
the refrigerant piping line exiting from the frame pipe 62 is connected to an oil cooler 84C of the compressor 84 constituting the low temperature side refrigerant circuit 82, and is then connected to a condenser 55.
the refrigerant piping line exiting from the condenser 55 is connected to a high temperature side dehydrator (a dry core) 57 and a capillary tube 58.
the dehydrator 57 is water removal means for removing water from the high temperature side refrigerant circuit 52.
the capillary tube 58 is passed through a part (72A) of a suction piping line 72 exiting from a high temperature side evaporator 59 of a cascade heat exchanger 56 and returning to the compressor 54.
the capillary tube 58 is passed through the piping line 72A as a part of the suction piping line 72 positioned on the discharge side of the evaporator 59 and on the suction side of an accumulator 68, to constitute a double tube structure as shown in FIG. 3 .
a double tube structure it is possible to perform heat exchange between the refrigerant flowing through the capillary tube 58 inside a double tube 67 (hereinafter referred to as the double tube structure) and the refrigerant flowing from the evaporator 83 through the piping line 72A outside the capillary tube.
the double tube structure 67 is manufactured by a method similar to that of the double tube structure 25 described above in Embodiment 1. That is, first, the linearly tubular capillary tube 58 is passed through the linearly tubular piping line 72A having a comparatively large diameter. Next, such a double tube is spirally wound as much as a plurality of stages. At this time, the tube is wound so that the axial center of the piping line 72A coincides with the axial center of the capillary tube 58 as much as possible, to form the spiral double tube. In consequence, a gap is formed between the inner wall surface of the piping line 72A and the outer wall surface of the capillary tube 58 as consistently as possible.
the double tube is spirally wound as much as the plurality of stages to form the spiral double tube structure, thereby enabling miniaturization while sufficiently acquiring the length of the capillary tube 58 and sufficiently acquiring such a heat exchange portion of the double tube structure.
connection piping lines (not shown) having both end holes and side holes are attached to both ends of the piping line 72A, the ends of the capillary tube 58 are drawn from the side holes, respectively, and then the side holes are welded and sealed. Furthermore, one end of the connection piping line attached to the one end of the piping line 72A and a connecting portion of the piping line 72A are welded, the other end of the connection piping line is connected to the suction piping line 72 connected to the evaporator 59 on the discharge side thereof, and this connecting portion is welded.
connection piping line 72A attached to the other end of the piping line 72A and a connecting portion of the piping line 72A are welded, the other end of the connection piping line is connected to the suction piping line 72 leading to the accumulator 68, and this connecting portion is welded.
the outer periphery of the piping line 72A formed in such a double tube structure is surrounded with an insulating material (not shown), whereby the double tube structure 67 of the present embodiment can be obtained.
the capillary tube 58 is passed through the suction piping line 72 (the piping line 72A) to constitute the double tube structure, thereby performing heat exchange between the refrigerant flowing through the capillary tube 58 and the refrigerant flowing through the suction piping line 72 (the piping line 72A) by conduction of heat transmitted along the wall surface of the whole periphery of the capillary tube 58.
a heat exchange performance can remarkably be improved as compared with a conventional structure in which a capillary tube is attached to the outer peripheral surface of a suction piping line.
the whole outer periphery of the piping line 72A having the double tube structure is surrounded with the insulating material as described above, whereby the structure is not easily influenced by the heat from the outside. Moreover, it is possible to further improve the ability of the heat exchange between the refrigerant in the piping line 72A and the refrigerant in the capillary tube 58. Furthermore, the refrigerant is allowed to flow through the capillary tube 58 inside the double tube structure and through the suction piping line 72 (the piping line 72A) outside the capillary tube 58 so as to form the counter flow of the refrigerant, whereby the heat exchange ability in the double tube structure 67 can further be improved.
the refrigerant piping line exiting from the capillary tube 58 is connected to the high temperature side evaporator 59 disposed in a heat exchange manner with respect to an evaporator 85 of the low temperature side refrigerant circuit 82.
the high temperature side evaporator 59 constitutes the cascade heat exchanger 56 together with the evaporator 85 of the low temperature side refrigerant circuit 82.
the suction piping line 72 exiting from the high temperature side evaporator 59 is connected to the compressor 54 on the suction side successively through a high temperature side header 66, the double tube structure 67, the accumulator 68 and a check valve 69.
R404A is introduced as the refrigerant.
R404A comprises 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 thereof includes 44% by weight of R125, 52% by weight of R143a and 4% by weight of R134a.
This mixed refrigerant has a boiling point of -46.5°C.
the refrigerant introduced in the high temperature side refrigerant circuit 52 is not limited to R404A described above.
R407C as a mixed refrigerant of three types R134a, R32 (difluoromethane: CH 2 F 2 ) and R125 is introduced as the refrigerant, the present invention is effective.
broken-line arrows show the flow of the refrigerant circulating through the high temperature side refrigerant circuit 52. That is, a high temperature gaseous refrigerant discharged from the compressor 54 is once discharged from the sealed container to the disperse heater 60 through a refrigerant discharge tube on a disperse heater 60 side, radiates heat and again returns into the shell of the sealed container. In consequence, the inside of the sealed container can be cooled by the refrigerant which has radiated the heat in the disperse heater 60 to lower the temperature thereof.
such a high temperature gaseous refrigerant is discharged from the sealed container through the refrigerant discharge tube 71, condensed by the preliminary condenser 61, the frame pipe 62, the oil cooler 84C of the compressor 84 of the low temperature side refrigerant circuit 82 and the condenser 55 to radiate the heat, and is liquefied, followed by removing the water contained in the refrigerant by the dehydrator 57. Afterward, the refrigerant flows into the capillary tube 58 of the double tube structure 67.
the heat exchange between the refrigerant in the capillary tube 58 and the refrigerant flowing through the suction piping line 72 (the piping line 72A) disposed along the whole periphery of the capillary tube 58 is performed by conduction of heat transmitted along the wall surface of the whole periphery of the capillary tube 58.
the refrigerant has a pressure thereof reduced while lowering the temperature, and flows into the evaporator 59.
the refrigerant R404A absorbs the heat from the refrigerant flowing through the evaporator 85 of the cascade heat exchanger 56 to evaporate. At this time, the refrigerant R404A evaporates to cool the refrigerant flowing through the evaporator 85.
the refrigerant which has evaporated in the evaporator 59 exits from the high temperature side evaporator 59 through the suction piping line 72, flows into the double tube structure 67 through the high temperature side header 66, and performs heat exchange between the refrigerant and the refrigerant flowing through the capillary tube 58. Then, the refrigerant returns to the compressor 54 through the accumulator 68 and the check valve 69.
the compressor 84 constituting the low temperature side refrigerant circuit 82 is an electromotive compressor using a single phase or three phase alternator in the same manner as in the compressor 54 of the high temperature side refrigerant circuit 52.
the compressor 84 is connected to a disperse heater 90, and has a constitution which once discharges the refrigerant compressed by the compressor 84 to the outside to radiate the heat, then returns the refrigerant into the shell of the sealed container and again discharges the refrigerant to a refrigerant discharge tube 101.
the refrigerant discharge tube 101 connected to the compressor 84 on the discharge side is connected to a preliminary condenser 91.
the refrigerant piping line exiting from the preliminary condenser 91 is connected to an oil separator 92.
the oil separator 92 is connected to an oil return tube 103 returning to the compressor 84.
the refrigerant piping line exiting from the oil separator 92 leads to an inner heat exchanger 93.
the inner heat exchanger 93 is a heat exchanger for performing heat exchange between the high pressure side refrigerant compressed by the compressor 84 and flowing toward a capillary tube 88 and the low pressure side refrigerant evaporated in the evaporator 83 and returning to the compressor 84.
the high pressure side refrigerant piping line passing through the inner heat exchanger 93 is connected to the evaporator 85.
the evaporator 85 constitutes the cascade heat exchanger 56 together with the high pressure side evaporator 59 of the high temperature side refrigerant circuit 52 as described above.
the refrigerant piping line exiting from the evaporator 85 is connected to a low temperature side dehydrator (a dry core) 87 and the capillary tube 88.
the dehydrator 87 is water removal means for removing water from the low temperature side refrigerant circuit 82.
the capillary tube 88 is passed through a part (a piping line 102A) of a suction piping line 102 exiting from the evaporator 83 and returning to the compressor 84.
the capillary tube 88 is passed through the piping line 102A as a part of the suction piping line 102 positioned on the discharge side of the evaporator 83 and on the suction side of the inner heat exchanger 93, to constitute the double tube structure as shown in FIG. 3 .
the double tube structure it is possible to perform heat exchange between the refrigerant flowing through the capillary tube 88 inside a double tube 95 (hereinafter referred to as the double tube structure) and the refrigerant flowing from the evaporator 83 through the piping line 102A outside the capillary tube.
the double tube structure 95 is manufactured by a method similar to that of the double tube structure 25 described above in Embodiment 1. That is, first, the linearly tubular capillary tube 88 is passed through the linearly tubular piping line 102A having a comparatively large diameter. Next, such a double tube is spirally wound as much as a plurality of stages. At this time, the tube is wound so that the axial center of the piping line 102A coincides with the axial center of the capillary tube 88 as much as possible, to form the spiral double tube. In consequence, a gap is formed between the inner wall surface of the piping line 102A and the outer wall surface of the capillary tube 88 as consistently as possible.
the double tube is spirally wound as much as the plurality of stages to form the spiral double tube structure, thereby enabling miniaturization while sufficiently acquiring the length of the capillary tube 88 and sufficiently acquiring such a heat exchange portion of the double tube structure.
connection piping lines (not shown) having both end holes and side holes are attached to both ends of the piping line 102A, the ends of the capillary tube 88 are drawn from the side holes, respectively, and then the side holes are welded and sealed. Furthermore, one end of the connection piping line attached to the one end of the piping line 102A and a connecting portion of the piping line 102A are welded, the other end of the connection piping line is connected to the suction piping line 102 connected to the evaporator 83 on the discharge side thereof, and this connecting portion is welded.
connection piping line 102A attached to the other end of the piping line 102A and a connecting portion of the piping line 102A are welded, the other end of the connection piping line is connected to the suction piping line 102 leading to the inner heat exchanger 93, and this connecting portion is welded.
the outer periphery of the piping line 102A formed in such a double tube structure is surrounded with an insulating material 105, whereby the double tube structure 95 of the present embodiment can be obtained.
the capillary tube 88 is passed through the suction piping line 102 (the piping line 102A) to constitute the double tube structure, thereby performing heat exchange between the refrigerant flowing through the capillary tube 88 and the refrigerant flowing through the suction piping line 102 (the piping line 102A) by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube 88.
a heat exchange performance can remarkably be improved as compared with a conventional structure in which the capillary tube is attached to the outer peripheral surface of the suction piping line.
the whole outer periphery of the piping line 102A having the double tube structure is surrounded with the insulating material 105 as described above, whereby the structure is not easily influenced by the heat from the outside. Moreover, it is possible to further improve the ability of the heat exchange between the refrigerant in the piping line 102A and the refrigerant in the capillary tube 88. Furthermore, the refrigerant is allowed to flow through the capillary tube 88 inside the double tube structure and through the suction piping line 102 (the piping line 102A) outside the capillary tube 88 so as to form the counter flow of the refrigerant, whereby the heat exchange ability in the double tube structure 95 can further be improved.
the double tube structure 95 is removably received in the insulating material 7 under the inner box 4 on the back surface side thereof in the same manner as in the double tube structure 25 of Embodiment 1.
the refrigerant piping line 102 exiting from the capillary tube 95 is connected to the compressor 84 on the suction side through the inner heat exchanger 93.
the compressor 84 is further connected to a refrigerant piping line 106, and the refrigerant piping line 106 is connected to expansion tanks 107 in which the refrigerant is stored at the stop of the compressor 84 through a capillary tube 108 as a pressure reducing unit.
R508A is introduced as the refrigerant.
R508A comprises R23 (trifluoromethane: CHF 3 ) and R116 (hexafluoroethane: CF 3 CF 3 ), and a composition thereof includes 39% by weight of R23 and 61% by weight of R116.
This mixed refrigerant has a boiling point of -85.7°C.
the refrigerant introduced in the low temperature side refrigerant circuit 82 is not limited to R508A described in the present embodiment.
R508B R23/R116:46/54 having a different mixture ratio of R23 and R116 is used in place of R508A, the present invention is effective.
solid-line arrows show the flow of the refrigerant circulating through the low temperature side refrigerant circuit 82.
the flow of the refrigerant in the low temperature side refrigerant circuit 82 will specifically be described.
the high temperature gaseous refrigerant discharged from the compressor 84 is once discharged from the sealed container to the disperse heater 90 through a refrigerant discharge tube on a disperse heater 90 side, radiates heat and again returns into the shell of the sealed container.
the inside of the sealed container can be cooled by the refrigerant which has radiated the heat in the disperse heater 90 to lower the temperature thereof.
such a high temperature gaseous refrigerant is discharged from the sealed container through the refrigerant discharge tube 101, radiates the heat in the preliminary condenser 91, and flows into the oil separator 92.
a large part of the lubricant oil of the compressor 84 mixed with the refrigerant in the oil separator 92 and a part of the refrigerant condensed and liquefied in the preliminary condenser 91 are returned to the compressor 84 through the oil return tube 103.
the refrigerant discharged from the oil separator 92 is condensed to radiate the heat and is liquefied by the inner heat exchanger 93 and the evaporator 85.
the water contained in the refrigerant is removed by the low temperature side dehydrator 87, and the refrigerant flows into the capillary tube 88.
the heat exchange between the refrigerant in the capillary tube 88 and the refrigerant flowing through the suction piping line 102 (the piping line 102A) disposed along the whole periphery of the capillary tube 88 is performed by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube 88.
the refrigerant has a pressure thereof reduced while lowering the temperature, and flows into the evaporator 83. Subsequently, in the evaporator 83, the refrigerant R508A absorbs the heat from the ambient atmosphere to evaporate.
the refrigerant R508A evaporates in the evaporator 83 to exert a cooling function, thereby cool the periphery of the evaporator 83 to an ultralow temperature in a range of -86°C to -87°C.
the evaporator (the refrigerant piping line) 83 is wound along the inner box 4 on the insulating material 7 side in the heat exchange manner as described above, whereby the inside of the storage chamber 8 of the ultralow temperature refrigerator 1 is set to an in-chamber temperature below -80°C by such cooling of the evaporator 83.
the refrigerant evaporated in the evaporator 83 is discharged from the evaporator 83 through the suction piping line 102, and returns to the compressor 84 through the double tube structure 95 and the inner heat exchanger 93 as described above.
the ON-OFF control of the compressor 84 constituting the low temperature side refrigerant circuit 82 is performed by a control apparatus (not shown) based on the in-chamber temperature of the storage chamber 8.
the control apparatus based on the in-chamber temperature of the storage chamber 8.
the mixed refrigerant in the low temperature side refrigerant circuit 82 is collected in the expansion tanks 107 through the refrigerant piping line 106 and the capillary tube 108.
the pressure in the refrigerant circuit 82 can be prevented from rising.
the compressor 84 is started by the control apparatus, the refrigerant is gradually returned from the expansion tanks 107 into the compressor 84, which can alleviate a start load on the compressor 84.
the capillary tube 88 is passed through the suction piping line 102 (the piping line 102A) through which the refrigerant returning from the evaporator 83 to the compressor 84 flows, to constitute the double tube structure, whereby the efficiency of the heat exchange between the refrigerant in the piping line 102A and the refrigerant in the capillary tube 88 can be enhanced to improve the performance.
the capillary tube 88 is passed through the piping line 102A of the suction piping line 102 just exiting from the evaporator 83, to constitute the double tube structure which enables the heat exchange by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube 88.
the refrigerant returning from the evaporator 83 can efficiently cool the refrigerant having the lowest boiling point, and hence the performance can remarkably be improved. Therefore, the present invention is especially effective in the ultralow temperature refrigerator 1 of the present embodiment.
the piping line 102A formed in the double tube structure by passing the capillary tube 88 therethrough is surrounded with the insulating material 105, whereby the heat exchange efficiency can further be enhanced.
the flow of the refrigerant through the capillary tube 88 and the flow of the refrigerant through the piping line 102A outside the capillary tube 88 form the counter flow, whereby the heat exchange ability can further be improved.
the capillary tube 58 as pressure reducing means of the high temperature side refrigerant circuit 52 is also formed in the double tube structure in the same manner as in capillary tube 88 of the low temperature side refrigerant circuit 82, and the piping line 72A having such a double tube structure is surrounded with the insulating material. Furthermore, the flow of the refrigerant becomes the counter flow in the capillary tube 58 inside the double tube structure and the suction piping line 72 (the piping line 72A) outside the capillary tube 58. In consequence, the refrigerant returning from the evaporator 59 can efficiently cool the refrigerant in the capillary tube 58. Consequently, the heat exchange efficiency can further be enhanced to further improve the performance.
the ultralow temperature refrigerator 1 in which the inside of the storage chamber 8 can more efficiently be cooled to a desirable ultralow temperature.
energy saving of about 15% to 20% can be achieved as compared with a similarly used conventional refrigerating apparatus.
the ambient temperature of the evaporator 13 has heretofore been about -83°C, but according to the above structure of the present invention, a lower temperature in a range of -86°C to -87°C can be realized.
FIG. 7 is a refrigerant circuit diagram of the embodiment having a constitution of the refrigerating apparatus for the ultralow temperature refrigerator 1 of FIG. 1 .
a compressor 114 and the like constituting the refrigerant circuit of a refrigerating apparatus R3 are installed in a mechanical chamber (not shown) positioned in the lower part of an insulating box member 2 of the ultralow temperature refrigerator 1, and an evaporator (a refrigerant piping line) 113 is attached to the peripheral surface of an inner box 4 on an insulating material 7 side in a heat exchange manner.
the refrigerant circuit of the refrigerating apparatus R3 of the present embodiment is constituted of a single unit multistage (two stages) refrigerant circuit 112 comprising the compressor 114, a condenser 115, an evaporator 113, a single intermediate heat exchanger 116 connected so that a refrigerant returning from the evaporator 113 circulates therethrough and a plurality of capillary tubes 118 and 135.
the compressor 114 constituting the refrigerant circuit 112 is an electromotive compressor using a single phase or three phase alternator in the same manner as in the above embodiments.
a refrigerant discharge tube 131 connected to the compressor 114 on a discharge side thereof is connected to a preliminary condenser 121.
the preliminary condenser 121 is connected to a frame pipe 122 for heating the opening edge of the storage chamber 8 to prevent dew condensation, an oil cooler 114C of the compressor 114, and then the condenser 115. It is to be noted that in the present embodiment, the preliminary condenser 121 and the condenser 115 have an constitution of an integral condenser, and are cooled by a condensing fan 129 as a blower for the condenser.
the refrigerant piping line exiting from the condenser 115 is connected to a flow diverter 130 via a dehydrator (a dry core) 117.
the dehydrator 117 is water removal means for removing water from the refrigerant circuit 112.
the flow diverter 130 is a gas-liquid separator for separating a refrigerant condensed and liquefied while flowing through the preliminary condenser 121, the frame pipe 122 and the condenser 115 from a refrigerant which is not condensed yet and still has a liquid state.
a gas phase piping line 133 connected to the flow diverter 130 on a suction side (an outlet side) thereof to take a gas phase refrigerant (the non-condensed refrigerant) separated by the flow diverter 130 is connected to a condensing pipe 123.
the condensing pipe 123 constitutes the intermediate heat exchanger 116 together with a preliminary evaporator 136.
the intermediate heat exchanger 116 reduces, by the capillary tube 135, a pressure of the liquid phase refrigerant (the condensed refrigerant) separated by the flow diverter 130, and allows the refrigerant to flow through the preliminary evaporator 136 of the intermediate heat exchanger 116 to evaporate the refrigerant therein, thereby cooling the gas phase refrigerant (the non-condensed refrigerant) flowing through the condensing pipe 123 to condense the refrigerant.
the refrigerant piping line exiting from the condensing pipe 123 is connected to the evaporator 113 via the capillary tube (the capillary tube of the final stage) 118.
the capillary tube 118 is passed through a part (a piping line 132A) of a suction piping line 132 exiting from the evaporator 113 to return to the compressor 114.
the capillary tube 118 is passed through the piping line 132A as a part of the suction piping line 132 positioned on the discharge side of the evaporator 113 and on the suction side of the intermediate heat exchanger 116, to constitute the double tube structure as shown in FIG. 3 .
Such a double tube structure has a constitution which can perform heat exchange between the refrigerant flowing through the capillary tube 118 inside a double tube 125 (hereinafter referred to as the double tube structure) and the refrigerant flowing from the evaporator 113 through the piping line 132A outside the capillary tube.
the double tube structure 125 is manufactured by a method similar to that of the double tube structure 25 described above in Embodiment 1. That is, first, the linearly tubular capillary tube 118 is passed through the linearly tubular piping line 132A having a comparatively large diameter. Next, such a double tube is spirally wound as much as a plurality of stages. At this time, the tube is wound so that the axial center of the piping line 132A coincides with the axial center of the capillary tube 118 as much as possible, to form the spiral double tube. In consequence, a gap is formed between the inner wall surface of the piping line 132A and the outer wall surface of the capillary tube 118 as consistently as possible.
the double tube is spirally wound as much as the plurality of stages to form the spiral double tube structure, thereby enabling miniaturization while sufficiently acquiring the length of the capillary tube 118 and sufficiently acquiring such a heat exchange portion of the double tube structure.
connection piping lines (not shown) having both end holes and side holes are attached to both ends of the piping line 132A, the ends of the capillary tube 118 are drawn from the side holes, respectively, and then the side holes are welded and sealed. Furthermore, one end of the connection piping line attached to the one end of the piping line 132A and a connecting portion of the piping line 132A are welded, the other end of the connection piping line is connected to the suction piping line 102 connected to the evaporator 113 on the discharge side thereof, and this connecting portion is welded.
connection piping line 132A attached to the other end of the piping line 132A and a connecting portion of the piping line 132A are welded, the other end of the connection piping line is connected to the suction piping line 102 leading to the intermediate heat exchanger 116, and this connecting portion is welded.
the outer periphery of the piping line 132A formed in such a double tube structure is surrounded with an insulating material 140, whereby the double tube structure 125 of the present embodiment can be obtained.
the capillary tube 118 is passed through the suction piping line 132 to constitute the double tube structure, thereby performing heat exchange between the refrigerant flowing through the capillary tube 118 and the refrigerant flowing through the suction piping line 132 by conduction of heat transmitted along the wall surface of the whole periphery of the capillary tube 118.
a heat exchange performance can remarkably be improved as compared with a conventional structure in which the capillary tube is attached to the outer peripheral surface of the suction piping line.
the whole outer periphery of the piping line 132A having the double tube structure is surrounded with the insulating material 140 as described above, whereby the structure is not easily influenced by the heat from the outside. Moreover, it is possible to further improve the ability of the heat exchange between the refrigerant in the piping line 132A and the refrigerant in the capillary tube 118.
the refrigerant is allowed to flow through the capillary tube 118 inside the double tube structure and through the suction piping line 132 (the piping line 132A) outside the capillary tube 118 so as to form the counter flow of the refrigerant, whereby the heat exchange ability in the double tube structure 125 can further be improved.
the double tube structure 125 is removably received in the insulating material 7 under the inner box 4 on the back surface side thereof in the same manner as in the double tube structures 25 and 95 of the above embodiments.
the suction piping line 132 exiting from the evaporator 113 is connected to the preliminary evaporator 136 through the piping line 132A of the double tube structure 125. Moreover, the suction piping line 132 exiting from the preliminary evaporator 136 is connected to the compressor 114 on the suction side thereof. Furthermore, an expansion tank 137 for storing the refrigerant at the stop of the compressor 114 is interposed between the compressor 114 and the preliminary evaporator 136 along the suction piping line 132 via a capillary tube 138 as a pressure reducing unit.
a non-azeotropic mixed refrigerant constituted of a plurality of types of mixed refrigerants having different boiling points is introduced as a refrigerant in the refrigerant circuit 112.
a non-azeotropic mixed refrigerant comprising R245fa (1,1,1,-3,3-pentafluoropropane: CF 3 CH 2 CHF 2 ), R600 (butane: CH 3 CH 2 CH 2 CH 3 ), R23 (trifluoromethane: CHF 3 ) and R14 (tetrafluoromenthane: CF 4 ) is introduced in the same manner as in Embodiment 1.
the refrigerant introduced in the refrigerant circuit 112 is not limited to the above non-azeotropic mixed refrigerant including R245fa, R600, R23 and R14.
a non-azeotropic mixed refrigerant including R245fa, R600, R116 and R14, a non-azeotropic mixed refrigerant including R245fa, R600, R508A and R14 or a non-azeotropic mixed refrigerant including R245fa, R600, R508B and R14 may be introduced.
the present invention is effective.
FIG. 7 arrows show the flow of the refrigerant circulating through the refrigerant circuit 112. This will specifically be described.
a high temperature gaseous refrigerant discharged from the compressor 114 is discharged from the sealed container through the refrigerant discharge tube 131, and successively flows through the preliminary condenser 121, the frame pipe 122, the oil cooler 114C of the compressor 114 and the condenser 115.
the high temperature gaseous refrigerant discharged from the compressor 114 radiates heat while flowing through the preliminary condenser 121, the frame pipe 122, the oil cooler 114C and the condenser 115, and the refrigerants (R245fa and R600) having a high boiling point in the mixed refrigerant is condensed and liquefied.
the water contained in the mixed refrigerant discharged from the condenser 115 is removed by the dehydrator 117, and the refrigerant flows into the flow diverter 130.
R23 and R14 in the mixed refrigerant having a remarkably low boiling point, are not condensed yet and have a gas state, and R245fa and R600 having a high boiling point are condensed and liquefied. Therefore, R23 and R14 are allowed to flow through the gas phase piping line 133, and R245fa and R600 are separately allowed to flow through a liquid phase piping line 134.
the refrigerant mixture which has flowed into the gas phase piping line 133 flows into the condensing pipe 123 constituting the intermediate heat exchanger 116.
the mixed refrigerant which has flowed into the liquid phase piping line 134 has a pressure thereof reduced by the capillary tube 135, and flows into the preliminary evaporator 136 constituting the intermediate heat exchanger 116 together with the condensing pipe 123, to cool R23 and R14 flowing through the condensing pipe 123 together with the low temperature refrigerant returning from the evaporator 113.
R23 and R14 flowing through the condensing pipe 123 are condensed and liquefied.
condensed R23 and R14 then exit from the condensing pipe 123 to flow into the capillary tube 118.
heat exchange between the refrigerant in the capillary tube 118 and the refrigerant flowing through the suction piping line 132 (the piping line 132A) disposed along the whole periphery of the capillary tube 118 is performed by conduction of heat transmitted along the wall surface of the whole periphery of the capillary tube 118.
the refrigerant has a pressure thereof reduced while further lowering the temperature, and flows into the evaporator 113. Subsequently, in the evaporator 113, the refrigerants R14 and R23 take the heat from the ambient atmosphere to evaporate.
the refrigerants R14 and R23 evaporate in the evaporator 113 to exert a cooling function, thereby cooling the periphery of the evaporator 113 to an ultralow temperature of - 85°C.
the evaporator (the refrigerant piping line) 113 is wound along the inner box 4 on the insulating material 7 side in the heat exchange manner, whereby the inside of the storage chamber 8 of the ultralow temperature refrigerator 1 can be set to an in-chamber temperature below -80°C by such cooling of the evaporator 113.
the refrigerant evaporated in the evaporator 113 exits from the evaporator 113 through the suction piping line 132, flows into the preliminary evaporator 136 of the intermediate heat exchanger 116 through the double tube structure 125 described above, and then joins the refrigerants (R245fa and R600) evaporated in the preliminary evaporator 136 and having a high boiling point. Afterward, the refrigerant exits from the preliminary evaporator 136 to return to the compressor 114.
ON-OFF control of the compressor 114 constituting the refrigerant circuit 112 is performed by a control apparatus (not shown) based on the in-chamber temperature of the storage chamber 8.
the control apparatus based on the in-chamber temperature of the storage chamber 8.
the mixed refrigerant in the low temperature side refrigerant circuit 112 is collected in the expansion tank 137 through the capillary tube 138.
the pressure in the refrigerant circuit 112 can be prevented from rising.
the compressor 114 is started by the control apparatus, the refrigerant is gradually returned from the expansion tank 137 into the refrigerant circuit 112 through the capillary tube 138, which can alleviate a start load on the compressor 114.
the capillary tube 118 is passed through the suction piping line 132 (the piping line 132A) through which the refrigerant returning from the evaporator 113 to the compressor 114 flows, to constitute the double tube structure, whereby the efficiency of the heat exchange between the refrigerant in the piping line 132A and the refrigerant in the capillary tube 118 can be enhanced to improve the performance.
the capillary tube 118 is passed through the piping line 132A of the suction piping line 132 just exiting from the evaporator 113, to constitute the double tube structure which enables the heat exchange by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube 118.
the refrigerant returning from the evaporator 113 can efficiently cool the refrigerant having the lowest boiling point, and hence the performance can remarkably be improved. Therefore, the present invention is especially effective in the ultralow temperature refrigerator 1 of the present embodiment.
the piping line 132A formed in the double tube structure by passing the capillary tube 118 therethrough is surrounded with the insulating material 140, whereby the heat exchange efficiency can further be enhanced.
the flow of the refrigerant through the capillary tube 118 and the flow of the refrigerant through the suction piping line 132A outside the capillary tube 118 form the counter flow, whereby the heat exchange ability can further be improved.
the ultralow temperature refrigerator 1 in which the inside of the storage chamber 8 can more efficiently be cooled to a desirable ultralow temperature.
energy saving of about 15% to 20% can be achieved as compared with a similarly used conventional refrigerating apparatus.
the ambient temperature of the evaporator 113 can be set to a low temperature as compared with the conventional apparatus. In consequence, even when the compressor is changed to a compressor having a smaller capability than the conventional compressor, a sufficient performance can be acquired. In consequence, further decrease of power consumption and miniaturization of the apparatus can be achieved.
the only refrigerant circuit 112 described above may constitute the refrigerating apparatus R3 of the ultralow temperature refrigerator 1, but as shown in FIG. 7 , in addition to the refrigerant circuit 112, a refrigerant circuit 152 having a circuit constitution similar to the refrigerant circuit 112 may be disposed in parallel, and the two refrigerant circuits 112 and 152 may constitute the refrigerating apparatus R3 of the ultralow temperature refrigerator 1.
the circuit constitution and refrigerant flow of the refrigerant circuit 152 are similar to those of the refrigerant circuit 112 described above, and hence the constitution is denoted with the same reference numerals as those of the members constituting the refrigerant circuit 112. That is, the members denoted with the same reference numerals as those of the refrigerant circuit 112 produce the same or similar effect or function, and hence description thereof is omitted here.
a compressor 114 and the like constituting the refrigerant circuit 152 are installed in a mechanical chamber (not shown) positioned in the lower part of the insulating box member 2 of the ultralow temperature refrigerator 1 in the same manner as in the compressor 114 of the refrigerant circuit 112, and an evaporator 113 of the refrigerant circuit 152 is also attached to the peripheral surface of the inner box 4 on the insulating material 7 side in the heat exchange manner, similarly to the evaporator 113 of the refrigerant circuit 112. Furthermore, refrigerants introduced in the refrigerant circuit 152 and circulation of the refrigerants are similar to those of the refrigerant circuit 112 described above, and hence description thereof is omitted here.
the refrigerating apparatus R3 of the ultralow temperature refrigerator 1 has a constitution in which two independent refrigerant circuits 112 and 152 having substantially the same performance are arranged side by side, when one of the refrigerant circuits breaks down, the other refrigerant circuit can be used as a backup. That is, for example, even when the refrigerant circuit 112 breaks down, the refrigerant circuit 152 is operated without any trouble, and the evaporator 113 of the refrigerant circuit 152 can keep the inside of the storage chamber 8 at the ultralow temperature. In consequence, reliability of the ultralow temperature refrigerator 1 can be enhanced.
each refrigerant circuit constituting the refrigerating apparatus is described as the refrigerant circuit for the single unit two stage system refrigerating apparatus R3, comprising the compressor 114, the condenser 115, the evaporator 113, the single intermediate heat exchanger 116 connected so that the refrigerant returning from the evaporator 113 circulates therethrough and the plurality of, specifically, two capillary tubes 135 and 118.
the plurality of types of non-azeotropic mixed refrigerants are introduced, the condensed refrigerant of the refrigerants passed through the condenser 115 is allowed to join the intermediate heat exchanger 116 through the capillary tube 135, and the non-condensed refrigerant of the refrigerants is cooled in the intermediate heat exchanger 116, whereby the refrigerant having a lower boiling point is condensed, and the refrigerant having the lowest boiling point is evaporated by the evaporator 113 through the capillary tube 118 of the final stage to exert the cooling function.
the present invention is not limited to this embodiment, and, for example, a plurality of intermediate heat exchangers may be connected in series to constitute the circuit.
FIG. 8 is a refrigerant circuit diagram of the embodiment having a constitution of the refrigerating apparatus for the ultralow temperature refrigerator 1 of FIG. 1 .
compressors 214 and 254 and the like constituting the refrigerant circuit of a refrigerating apparatus R4 are installed in a mechanical chamber (not shown) positioned in the lower part of an insulating box member 2 of the ultralow temperature refrigerator 1, and an evaporator (a refrigerant piping line) 253 is attached to the peripheral surface of an inner box 4 on an insulating material 7 side in a heat exchange manner, similarly to the evaporators 13, 83 and 113 of the above embodiments.
the refrigerant circuit of the refrigerating apparatus R4 of the present embodiment is a multiunit multistage refrigerant circuit, i.e., a two-unit two-stage refrigerant circuit comprising a high temperature side refrigerant circuit 212 and a low temperature side refrigerant circuit 252 constituting independent refrigerant closed circuits, respectively.
the compressor 214 constituting the high temperature side refrigerant circuit 212 is an electromotive compressor using a single phase or three phase alternator.
a refrigerant discharge tube 231 connected to the compressor 214 on a discharge side thereof is connected to a preliminary condenser 221.
the preliminary condenser 221 is connected to a frame pipe 222 for heating the opening edge of a storage chamber 8 to prevent dew condensation.
the frame pipe 222 is connected to an oil cooler 214C of the compressor 214, and is then connected to a condenser 215. Moreover, the refrigerant piping line exiting from the condenser 215 is connected to an oil cooler 254C constituting the low temperature side refrigerant circuit 252, and is then connected to a condenser 223.
the refrigerant piping line exiting from the condenser 223 is connected to a high temperature side evaporator 213 as an evaporator portion constituting the evaporator of the high temperature side refrigerant circuit 212 successively via a drier (a dry core) 217 and a capillary tube 218 as a pressure reducing unit.
the high temperature side evaporator 213 constitutes a cascade heat exchanger 216 together with a condensing pipe 255 as a condenser of the low temperature side refrigerant circuit 252.
a suction piping line 232 exiting from the preliminary evaporator 213 is connected to an accumulator 228 as a refrigerant liquid storage, and the suction piping line 232 exiting from the accumulator 228 is connected to the oil cooler 214C on the suction side.
the preliminary condenser 221 and the condensers 215 and 223 have a constitution of an integral condenser, and are cooled by a condensing fan 229 as a blower for the condensers.
a refrigerant comprising R407D and n-pentane is charged as a non-azeotropic refrigerant in the high temperature side refrigerant circuit 212.
R407D comprises 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 of the refrigerant includes 15% by weight of R32, 15% by weight of R125 and 70% by weight of R134a.
R32 has -51.8°C
R125 has -48.57°C
R134a has -26.16°C.
n-pentane has a boiling point of +36.1°C.
a high temperature gaseous refrigerant discharged from the compressor 214 is condensed, radiates heat and is liquefied by the preliminary condenser 221, the frame pipe 222, the oil cooler 214C, the condenser 215, the oil cooler 254C of the compressor 254 of the low temperature side refrigerant circuit 252 and the condenser 223, water contained in the refrigerant is removed by the drier 217, and then the refrigerant flows into the capillary tube 218. Subsequently, the refrigerant having the pressure thereof reduced by the capillary tube 218 flows into the high temperature side evaporator 213 constituting the cascade heat exchanger 216.
the refrigerants R32, R125 and R134a absorb the heat from the refrigerant flowing through the condensing pipe 255 to evaporate.
the refrigerant of the high temperature side evaporator 213 of the high temperature side refrigerant circuit 212 evaporates, thereby cooling the refrigerant flowing through the condensing pipe 255 in the low temperature side refrigerant circuit 252.
the refrigerant evaporated by the high temperature side evaporator 213 exits from the evaporator 213 through the suction piping line 232, and then returns to the compressor 214 through the accumulator 228.
the compressor 214 has a capability of, for example, 1.5 HP, and the finally reaching temperature of the high temperature side evaporator 213 which is being operated is in a range of -27°C to -35°C.
the boiling point of n-pentane in the refrigerant is +36.1°C, and hence the refrigerant does not evaporate and still has a liquid state in the high temperature side evaporator 213. Therefore, the refrigerant hardly contributes to the cooling.
the refrigerant has a function of returning, to the compressor 214, a lubricant of the compressor 214 or mixed water which cannot be absorbed by the drier 217 in a state where the water is dissolved in the refrigerant, and the liquid refrigerant has a function of evaporating in the compressor 214 to lower the temperature of the compressor 214.
the low temperature side refrigerant circuit 252 comprises the compressor 254, the condensing pipe (the condenser) 255, the evaporator 253, a plurality of intermediate heat exchanges 262, 266, 270 and 272 connected so that the refrigerant returning from the evaporator 253 circulates therethrough, and a plurality of capillary tubes 264, 268 and 258.
the compressor 254 constituting the low temperature side refrigerant circuit 252 is an electromotive compressor using a single phase or three phase alternator in the same manner as in the compressor 214, and a refrigerant discharge tube 281 connected to the compressor 254 on the discharge side is connected to an oil separator 260 via a radiator 259 made of a wire condenser.
the oil separator 260 is connected to an oil return tube 287 returning to the compressor 254.
the refrigerant piping line connected to the oil separator 260 on the discharge side is connected to the condensing pipe 255 as a condenser constituting the cascade heat exchanger 216 together with the high temperature side evaporator 213.
the refrigerant piping line connected to the condensing pipe 255 on the discharge side is connected to a first gas-liquid separator 261 via a drier (a dry core) 257.
the gas phase refrigerant (the non-condensed refrigerant) separated by the first gas-liquid separator 261 flows through the first intermediate heat exchange 262 via a gas phase piping line 283, and flows into a second gas-liquid separator 265.
the liquid phase refrigerant (the condensed refrigerant) separated by the first gas-liquid separator 261 flows into the first intermediate heat exchange 262 via a liquid phase piping line 284 through a drier 263 and the capillary tube 268 as a pressure reducing unit.
the first intermediate heat exchange 262 allows the liquid phase refrigerant (the condensed refrigerant) separated by the first gas-liquid separator 261 to join the intermediate heat exchange 262 through the capillary tube 264.
the gas phase refrigerant (the non-condensed refrigerant) flowing through the gas phase piping line 283 is cooled, thereby condensing the refrigerant having a lower boiling point.
the liquid phase refrigerant separated by the second gas-liquid separator 265 flows through a drier 267 via a liquid phase piping line 286, and then flows into the second intermediate heat exchanger 266 through the capillary tube 268 as a pressure reducing unit. Moreover, the gas phase refrigerant separated by the second gas-liquid separator 265 flows through the second intermediate heat exchanger 266 through a gas phase piping line 285.
the second intermediate heat exchanger 266 allows the liquid phase refrigerant (the condensed refrigerant) separated by the second gas-liquid separator 265 to join the intermediate heat exchanger 266 through the capillary tube 268.
the gas phase refrigerant (the non-condensed refrigerant) flowing through the gas phase piping line 285 is cooled, thereby condensing the refrigerant having a lower boiling point.
the gas phase piping line 285 which has flowed through the second intermediate heat exchanger 266 flows into the capillary tube 258 as a pressure reducing unit through the third intermediate heat exchanger 270, the fourth intermediate heat exchanger 272 and a drier 274.
the capillary tube 258 is passed through a part (a piping line 282A) of a suction piping line 282 exiting from the evaporator 253 and returning to the compressor 254. Specifically, the capillary tube 258 is passed through the piping line 282A as a part of the suction piping line 282 positioned on a discharge side of the evaporator 253 and on a suction side of the fourth intermediate heat exchanger 272, to constitute a double tube structure as shown in FIG. 3 .
the double tube structure it is possible to perform heat exchange between the refrigerant flowing through the capillary tube 258 inside a double tube 295 (hereinafter referred to as the double tube structure) and the refrigerant flowing from the evaporator 253 through the piping line 282A outside the capillary tube.
the double tube structure 295 is manufactured by a method similar to that of the double tube structure 25 described above in Embodiment 1. That is, first, the linearly tubular capillary tube 258 is passed through the linearly tubular piping line 282A having a comparatively large diameter. Next, such a double tube is spirally wound as much as a plurality of stages. At this time, the tube is wound so that the axial center of the piping line 282A coincides with the axial center of the capillary tube 258 as much as possible, to form the spiral double tube. In consequence, a gap is formed between the inner wall surface of the piping line 282A and the outer wall surface of the capillary tube 258 as consistently as possible.
the double tube is spirally wound as much as the plurality of stages to form the spiral double tube structure, thereby enabling miniaturization while sufficiently acquiring the length of the capillary tube 258 and sufficiently acquiring such a heat exchange portion of the double tube structure.
connection piping lines (not shown) having both end holes and side holes are attached to both ends of the piping line 282A, the ends of the capillary tube 258 are drawn from the side holes, respectively, and then the side holes are welded and sealed. Furthermore, one end of the connection piping line attached to the one end of the piping line 282A and a connecting portion of the piping line 282A are welded, the other end of the connection piping line is connected to the suction piping line 282 connected to the evaporator 253 on the discharge side thereof, and this connecting portion is welded.
connection piping line 282A attached to the other end of the piping line 282A and a connecting portion of the piping line 282A are welded, the other end of the connection piping line is connected to the suction piping line 282 leading to the fourth intermediate heat exchanger 272, and this connecting portion is welded.
the piping line 282A formed in such a double tube structure is surrounded with an insulating material 297, whereby the double tube structure 295 of the present embodiment can be obtained.
the capillary tube 258 is passed through the suction piping line 282 to constitute the double tube structure, thereby performing heat exchange between the refrigerant flowing through the capillary tube 258 and the refrigerant flowing through the suction piping line 282 by conduction of heat transmitted along the wall surface of the whole periphery of the capillary tube 258.
a heat exchange performance can remarkably be improved as compared with a conventional structure in which a capillary tube is attached to the outer peripheral surface of the suction piping line.
the whole outer periphery of the piping line 282A having the double tube structure is surrounded with the insulating material 297 as described above, whereby the structure is not easily influenced by the heat from the outside. Moreover, it is possible to further improve the ability of the heat exchange between the refrigerant in the piping line 282A and the refrigerant in the capillary tube 258.
the refrigerant is allowed to flow through the capillary tube 258 inside the double tube structure and through the suction piping line 282 (the piping line 282A) outside the capillary tube 258 so as to form the counter flow of the refrigerant, whereby the heat exchange ability in the double tube structure 295 can further be improved.
the double tube structure 295 is removably received in the insulating material 7 under the inner box 4 on the back surface side thereof in the same manner as in the double tube structure 25 of Embodiment 1 described above.
the suction piping line 282 exiting from the double tube structure 295 is successively connected to the fourth intermediate heat exchanger 272, the third intermediate heat exchanger 270, the second intermediate heat exchanger 266 and the first intermediate heat exchange 262, and is then connected to the compressor 254 on the suction side.
expansion tanks 288 for storing the refrigerant at the stop of the compressor 254 are interposed between the compressor 254 and the first intermediate heat exchange 262 along the suction piping line 282, via a capillary tube 289 as a pressure reducing unit.
the capillary tube 289 is connected to a check valve 290 so that the direction of the expansion tanks 288 is a forward direction.
a non-azeotropic mixed refrigerant including R245fa 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 CH 2 CH 2 CH 3 ).
R245fa has a boiling point of +15.3°C and R600 has a boiling point of -0.5°C. Therefore, when these refrigerants are mixed at a predetermined ratio, the refrigerant can be used in place of heretofore used R21 having a boiling point of +8.9°C.
R404A comprises 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 thereof includes 44% by weight of R125, 52% by weight of R143a and 4% by weight of R134a.
the mixed refrigerant has a boiling point of -46.48°C. Therefore, the refrigerant can be used in place of heretofore used R22 having a boiling point of -40.8°C.
R508 comprises R23 (trifluoromethane: CHF 3 ) and R116 (hexafluoroethane: CF 3 CF 3 ), and a composition thereof includes 39% by weight of R23 and 61% by weight of R116.
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 -127.9°C
R50 has -161.5°C
R740 has -185.86°C.
R50 might combine with oxygen to be in danger of exploding.
the refrigerant is mixed with R14, the danger of the exploding is eliminated. Therefore, even if a leak accident of the mixed refrigerant occurs, any explosion is not caused.
R245fa and R600 and R14 and R50 are once mixed beforehand to obtain 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 then introduced in the refrigerant circuit 252.
R245fa and R600, next R404A, R508A, R14 and R50 and finally R740 are introduced in order from a higher boiling point.
composition of the respective refrigerants includes, for example, 10.3% by weight of the mixed refrigerant of R245fa and R600, 28% by weight of R404A, 29.2% by weight of R508A, 26.4% by weight of the mixed refrigerant of R14 and R50 and 5.1% by weight of R740.
n-pentane may be added to R404A (in a range of 0.5 to 2% by weight with respect to the total weight of the non-azeotropic refrigerants).
a high temperature high pressure gaseous mixed refrigerant discharged from the compressor 254 flows into the radiator 259 through the refrigerant discharge tube 281, and radiates heat in the radiator, whereby a part of n-pentane or R600 as an oil carrier refrigerant having a high boiling point in the mixed refrigerant and having a satisfactory solubility in oil is condensed and liquefied.
the mixed refrigerant discharged from the radiator 259 flows into the oil separator 260, and a large part of lubricant oil of the compressor 254 mixed with the refrigerant and a part of the refrigerant condensed and liquefied in the radiator 259 (a part of n-pentane or R600) are returned to the compressor 254 through the oil return tube 287.
a low boiling point refrigerant having a higher purity flows through the refrigerant circuit 252 behind the cascade heat exchanger 216, whereby an ultralow temperature can efficiently be obtained.
the inside of the storage chamber 8 as a cooling target having a larger capacity can be cooled to a predetermined ultralow temperature, which enables the increase of a storage capacity without enlarging the whole refrigerating apparatus R.
the refrigerant which has flowed into the oil separator 260 is once cooled in the radiator 259, and hence the temperature of the refrigerant flowing into the cascade heat exchanger 216 can be lowered.
the temperature of the refrigerant flowing into the cascade heat exchanger 216 has been about +65°C, but in the present embodiment, the temperature can be lowered to about +45°C.
the cascade heat exchanger 216 it is possible to alleviate a load added to the compressor 214 of the high temperature side refrigerant circuit 212 for cooling the refrigerant in the low temperature side refrigerant circuit 252. Moreover, the refrigerant in the low temperature side refrigerant circuit 252 can effectively be cooled, and hence it is possible to alleviate a load added to the compressor 254 constituting the low temperature side refrigerant circuit 252. In consequence, the operation efficiency of the whole refrigerating apparatus R4 can be enhanced.
the cascade heat exchanger 216 As to the other mixed refrigerants themselves, in the cascade heat exchanger 216, a part of the refrigerant (a part of R245fa, R600, R404A or R508) discharged from the high temperature side evaporator 213, cooled to about -40°C to -30°C and having a high boiling point in the mixed refrigerant is condensed and liquefied. Subsequently, the mixed refrigerant discharged from the condensing pipe 255 flows into the first gas-liquid separator 261 through the drier 257.
the mixed refrigerant discharged from the condensing pipe 255 flows into the first gas-liquid separator 261 through the drier 257.
R14, R50 and R740 in the mixed refrigerant have a remarkably low boiling point, are not condensed yet and still have a gas state, and an only part of R245fa, R600, R404A or R508 is condensed and liquefied, whereby R14, R50 and R740 are diverted to the gas phase piping line 283, and R245fa, R600, R404A and R508A are diverted to the liquid phase piping line 284.
the refrigerant mixture which has flowed into the gas phase piping line 283 is condensed by heat exchange between the mixture and the first intermediate heat exchange 262, and then reaches the second gas-liquid separator 265.
the low temperature refrigerant returning from the evaporator (the refrigerant piping line) 253 flows into the first intermediate heat exchange 262, and the liquid refrigerant which has flowed into the liquid phase piping line 284 has a pressure thereof reduced by the capillary tube 264 through the drier 263.
the refrigerant flows into the first intermediate heat exchange 262 to evaporate therein, and hence contributes to the cooling.
R14, R50, R740 or R508 is cooled, with the result that an intermediate temperature of the first intermediate heat exchange 262 becomes about -60°C. Therefore, R508 in the mixed refrigerant flowing through the gas phase piping line 283 is completely condensed and liquefied, and diverted to the second gas-liquid separator 265.
R14, R50 and R740 further have a low boiling point and still have the gas state.
R508 separated by the second gas-liquid separator 265 has water therein removed by the drier 267, has a pressure thereof reduced by the capillary tube 268, flows into the second intermediate heat exchanger 266, and then cools R14, R50 and R740 in the gas phase piping line 285 together with the low temperature refrigerant returning from the evaporator 253, to condense R14 having the highest evaporation temperature in these refrigerants.
the intermediate temperature of the second intermediate heat exchanger 266 becomes about -90°C.
the gas phase piping line 285 passing through the second intermediate heat exchanger 266 subsequently passes through the third intermediate heat exchanger 270 and the fourth intermediate heat exchanger 272.
the refrigerant just discharged from the evaporator 253 through the double tube structure 295 is returned to the fourth intermediate heat exchanger 272.
the intermediate temperature of the fourth intermediate heat exchanger 272 reaches a considerably low temperature of about -130°C.
heat exchange between the refrigerant in the capillary tube 258 and the refrigerant flowing through the suction piping line 282 (the piping line 282A) disposed along the whole periphery of the capillary tube 258 is performed by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube 258, and the refrigerant further has a pressure thereof reduced while lowering the temperature thereof, to flow into the evaporator 253. Subsequently, in the evaporator 253, the refrigerant takes the heat from the ambient atmosphere to evaporate. According to the experiment, at this time, the ambient temperature of the evaporator 253 is an ultralow temperature in a range of -160.3°C to -157.3°C.
the refrigerant still having a gas phase state is successively condensed in the intermediate heat exchanges 262, 266, 270 and 272 by use of each refrigerant evaporation temperature difference in the low temperature side refrigerant circuit 252, whereby an ultralow temperature below - 150°C can be acquired in the evaporator 253 of the final stage. Consequently, in a constitution in which the evaporator 253 is wound along the inner box 4 on the insulating material 7 side in the heat exchange manner, the inside of the storage chamber 8 can realize an in-chamber temperature below -152°C.
the refrigerant evaporated in the evaporator 253 is discharged from the evaporator 253 through the suction piping line 282, successively flows into the double tube structure 295, the fourth intermediate heat exchanger 272, the third intermediate heat exchanger 270, the second intermediate heat exchanger 266 and the first intermediate heat exchange 262, joins the refrigerant evaporated in each heat exchanger, and returns to the compressor 254.
the oil mixed in the refrigerant and discharged from the compressor 254 has a large part thereof separated by the oil separator 260 and is returned to the compressor 254, but mist-like oil discharged from the oil separator 260 together with the refrigerant is returned to the compressor 254 in a state where the oil is dissolved in R600 having a high solubility in the oil. This can prevent the compressor 254 from causing defective lubrication or locking. Moreover, R600 still having the liquid state returns to the compressor 254 to evaporate in the compressor 254, whereby the discharge temperature of the compressor 254 can be lowered.
ON-OFF control of the compressor 254 constituting the low temperature side refrigerant circuit 252 is performed by a control apparatus (not shown) based on the in-chamber temperature of the storage chamber 8.
the mixed refrigerant in the low temperature side refrigerant circuit 252 is collected in the expansion tanks 288 through the check valve 290 so that the direction of the expansion tanks 288 is a forward direction.
the pressure in the refrigerant circuit 252 can be prevented from rising.
the compressor 254 is started by the control apparatus, the refrigerant is gradually returned from the expansion tanks 288 into the refrigerant circuit 252 through the capillary tube 289, which can alleviate a start load on the compressor 254.
the refrigerant can rapidly be collected into the expansion tanks 288 at the stop of the compressor 254, whereby the pressure in the refrigerant circuit 252 can rapidly come to equilibrium.
the compressor 254 is restarted, any load is not applied to the compressor 254, but the compressor 254 can smoothly be restarted.
a time required for obtaining an equilibrium pressure in the refrigerant circuit 252 at the start of the compressor can remarkably be shortened, whereby the operation efficiency of the compressor 254 can be enhanced, and a time required in, for example, a pull-down operation can be shortened to enhance convenience.
the capillary tube 258 is passed through the suction piping line 282 (the piping line 282A) through which the refrigerant returning from the evaporator 253 to the compressor 254 flows, to constitute the double tube structure, whereby the efficiency of the heat exchange between the refrigerant in the piping line 282A and the refrigerant in the capillary tube 258 can be enhanced to improve performance.
the capillary tube 258 is passed through the piping line 282A of the suction piping line 282 just exiting from the evaporator 253 to constitute the double tube structure, thereby enabling the heat exchange by the conduction of the heat transmitted along the wall surface of the whole periphery of the capillary tube 258, whereby the refrigerant returning from the evaporator 253 efficiently can cool the refrigerant having the lowest boiling point, to remarkably improve the performance. Therefore, the present invention is especially effective in the ultralow temperature refrigerator 1 of the present embodiment.
the piping line 282A formed in the double tube structure by passing the capillary tube 258 therethrough is surrounded with the insulating material 297, whereby the heat exchange efficiency can further be enhanced.
the flow of the refrigerant through the capillary tube 258 and the flow of the refrigerant through the piping line 282A outside the capillary tube 258 form the counter flow, whereby the heat exchange ability can further be improved.
the ultralow temperature refrigerator 1 can be realized in which the inside of the storage chamber 8 can efficiently be cooled to a desirable ultralow temperature.
energy saving of about 15% to 20% can be achieved as compared with a similarly used conventional refrigerating apparatus.
a lower temperature can be realized as the ambient temperature of the evaporator 253 as compared with the conventional apparatus. In consequence, even when the compressor is changed to a compressor having a smaller capability than a conventional compressor, a sufficient performance can be acquired. In consequence, further decrease of power consumption and miniaturization of the apparatus can be achieved.
the only capillary tube 258 of the final stage of the low temperature side refrigerant circuit 252 is formed in the double tube structure of the present invention, but the present invention is not limited to this embodiment, and the present invention is effective even for a double tube structure obtained by similarly passing the capillary tube 218 of the high temperature side refrigerant circuit 212 through a part of the suction piping line 232 through which the refrigerant returning from the evaporator 213 to the compressor 214 in the high temperature side refrigerant circuit 212 flows.
the ability of the heat exchange between the refrigerant in the suction piping line 232 and the refrigerant in the capillary tube 218 can be improved.
the performance of the refrigerating apparatus R4 can further be improved.
the refrigerant circuit constituting the refrigerating apparatus has been described as the refrigerating apparatus R4 of the two unit multistage system comprising the high temperature side refrigerant circuit 212 and the low temperature side refrigerant circuit 252 to constitute independent closed refrigerant circuits, each of which condenses a refrigerant discharged from the compressor 214 or 254, reduces a pressure of the refrigerant and evaporates the refrigerant by the evaporator 213 or 253 to exert the cooling function.
the low temperature side refrigerant circuit 252 comprises the compressor 254, the condensing pipe 255, the evaporator 253, the plurality of, i.e., four intermediate heat exchangers 262, 266, 270 and 272 connected in series so that the refrigerant returning from the evaporator 253 circulates therethrough and the plurality of, i.e., three capillary tubes 264, 268 and 258.
the plurality of types of non-azeotropic mixed refrigerants are introduced.
the refrigerating apparatus allows the condensed refrigerant of the refrigerants flowing through the condensing pipe 255 to join the refrigerants in the intermediate heat exchangers through the capillary tubes, cools a non-condensed refrigerant of the refrigerants in the intermediate heat exchangers to successively condense the refrigerants having a lower boiling point, and evaporates the refrigerant having the lowest boiling point by the evaporator 253 through the capillary tube 258 of the final stage to exert the cooling function.
the evaporator 213 of the high temperature side refrigerant circuit 212 and the condensing pipe 255 of the low temperature side refrigerant circuit 252 constitute the cascade heat exchanger 216, and the evaporator 253 of the low temperature side refrigerant circuit 252 acquires the ultralow temperature.
the present invention is not limited to this embodiment, and may be a refrigerating apparatus of a multiunit multistage system. Moreover, the present invention is effective also for a refrigerating apparatus of a two-unit single-stage system including one gas-liquid separator and one intermediate heat exchanger.

Landscapes

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)

EP10015097A 2009-11-30 2010-11-29 Appareil de réfrigération Withdrawn EP2333459A3 (fr)

Applications Claiming Priority (1)

Application Number	Priority Date	Filing Date	Title
JP2009272410A JP2011112351A (ja)	2009-11-30	2009-11-30	冷凍装置

Publications (2)

Publication Number	Publication Date
EP2333459A2 true EP2333459A2 (fr)	2011-06-15
EP2333459A3 EP2333459A3 (fr)	2011-09-21

Family

ID=43805637

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP10015097A Withdrawn EP2333459A3 (fr)	2009-11-30	2010-11-29	Appareil de réfrigération

Country Status (5)

Country	Link
US (1)	US20110126575A1 (fr)
EP (1)	EP2333459A3 (fr)
JP (1)	JP2011112351A (fr)
KR (1)	KR20110060793A (fr)
CN (1)	CN102080903A (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CN1052472C (zh) *	1994-11-16	2000-05-17	新疆哈密制药厂	结合有烟酰胺和锌的乙酰水杨酸衍生物
WO2013000758A3 (fr) *	2011-06-29	2013-06-06	BSH Bosch und Siemens Hausgeräte GmbH	Appareil frigorifique
WO2015176939A1 (fr) *	2014-05-20	2015-11-26	BSH Hausgeräte GmbH	Machine frigorifique
EP3037744A4 (fr) *	2013-09-27	2016-11-02	Panasonic Healthcare Holdings Co Ltd	Dispositif de réfrigération
EP4137754A4 (fr) *	2020-06-04	2023-10-11	PHC Holdings Corporation	Dispositif de réfrigération binaire

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US9429347B2 (en) *	2011-08-04	2016-08-30	Mitsubishi Electric Corporation	Refrigeration apparatus
CN102313411B (zh) *	2011-10-14	2013-04-17	合肥美的荣事达电冰箱有限公司	冰箱及其制冷系统
JP2013144099A (ja) *	2011-12-12	2013-07-25	Toshiba Corp	磁気共鳴イメージング装置
CN102927725B (zh) *	2012-11-26	2015-07-15	合肥美的电冰箱有限公司	用于制冷设备的回气管组件及具有其的冰箱
EP3121532B1 (fr)	2014-03-17	2022-06-29	Mitsubishi Electric Corporation	Appareil à cycle frigorifique
KR101438155B1 (ko) *	2014-05-21	2014-09-05	주식회사 지엠에스	극초저온 냉동고
CN104329841B (zh) *	2014-07-01	2016-07-06	青岛海尔股份有限公司	制冷管道组件及冰箱
JP6543450B2 (ja) *	2014-09-29	2019-07-10	Ｐｈｃホールディングス株式会社	冷凍装置
EP3299433B1 (fr)	2015-05-18	2020-11-25	Nihon Freezer Co., Ltd.	Réfrigérant non azéotropique pour une température ultrabasse
BR102015023711A2 (pt) *	2015-09-15	2017-03-21	Whirlpool Sa	sistema de refrigeração de múltipla evaporação
DE102016003223A1 (de) *	2016-03-16	2017-09-21	Liebherr-Hausgeräte Lienz Gmbh	Kühl- und/oder Gefriergerät
CN109869973B (zh) *	2017-12-05	2022-03-29	松下电器产业株式会社	冷冻冷藏库
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
WO2019202645A1 (fr) *	2018-04-16	2019-10-24	株式会社テクニカン	Appareil de congélation
CN111271997B (zh) *	2018-12-05	2023-02-17	多美达(深圳)电器有限公司	一种用于热管散热器的冷凝液回流管
JP7112037B2 (ja) *	2019-06-24	2022-08-03	三菱電機株式会社	空気調和装置および空気調和システム
JP6821075B1 (ja) *	2020-04-22	2021-01-27	日立ジョンソンコントロールズ空調株式会社	冷凍サイクル装置
CN113531955A (zh) *	2021-08-26	2021-10-22	佛山市顺德区旭煌电器有限公司	一种用于微型直流变频空调或定频空调的气体换热装置
DE102022125163A1 (de) *	2022-09-29	2024-04-04	Karlsruher lnstitut für Technologie, Körperschaft des öffentlichen Rechts	Gefriergerät
DE102022125137A1 (de)	2022-09-29	2024-04-04	Liebherr-Hausgeräte Ochsenhausen GmbH	Kühl- und/oder Gefriergerät

Citations (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
JP2007107858A (ja)	2005-10-17	2007-04-26	Sanyo Electric Co Ltd	冷凍装置

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US1065663A (en) *	1912-01-20	1913-06-24	John M Cromley	Radiator.
FR1362140A (fr) *	1963-06-12	1964-05-29		Dispositifs réfrigérateurs particulièrement destinés aux frigorifiques d'usage domestique ou industriel
US3733845A (en) *	1972-01-19	1973-05-22	D Lieberman	Cascaded multicircuit,multirefrigerant refrigeration system
JPS5526769Y2 (fr) *	1975-02-18	1980-06-26
JPS5545251Y2 (fr) *	1975-02-18	1980-10-23
CA1106628A (fr) *	1976-10-27	1981-08-11	Robert B. Gelbard	Echangeur de chaleur haut rendement pour groupe tube d'aspiration et capillaire de refrigeration
JPS5581659U (fr) *	1978-12-04	1980-06-05
JPS5685672A (en) *	1979-12-12	1981-07-11	Matsushita Refrigeration	Fixing structure of capillary tube and suction pipe
JPS58133581A (ja) *	1982-02-03	1983-08-09	三菱電機株式会社	流量制御装置
DE3205359A1 (de) *	1982-02-15	1983-08-25	Austria Email - EHT AG, 1140 Wien	Waermetauscher
JPH0697123B2 (ja) *	1986-04-21	1994-11-30	三洋電機株式会社	冷凍装置
GB2180921B (en) *	1985-09-25	1990-01-24	Sanyo Electric Co	Refrigeration system
JPH047491Y2 (fr) *	1986-05-21	1992-02-27
US5497824A (en) *	1990-01-18	1996-03-12	Rouf; Mohammad A.	Method of improved heat transfer
US5065584A (en) *	1990-07-30	1991-11-19	U-Line Corporation	Hot gas bypass defrosting system
JP2003279181A (ja) *	2002-03-25	2003-10-02	Sanyo Electric Co Ltd	２元冷凍装置
KR100523035B1 (ko) *	2003-01-24	2005-10-24	삼성전자주식회사	냉장고용 일체형 흡입배관세트와 냉장고
AR039811A1 (es) *	2003-05-13	2005-03-02	Sergio Daniel Novoa	Disposicion intercambiadora de calor para sistemas de refrigeracion por compresion
KR20050096343A (ko) *	2004-03-30	2005-10-06	삼성전자주식회사	냉장고
JP4420807B2 (ja) *	2004-12-14	2010-02-24	三洋電機株式会社	冷凍装置
JP2007303794A (ja) *	2006-05-15	2007-11-22	Sanyo Electric Co Ltd	冷凍装置
EP1978317B1 (fr) *	2007-04-06	2017-09-06	Samsung Electronics Co., Ltd.	Dispositif de cycle réfrigérant

2009
- 2009-11-30 JP JP2009272410A patent/JP2011112351A/ja active Pending
2010
- 2010-09-30 CN CN2010105015965A patent/CN102080903A/zh active Pending
- 2010-09-30 KR KR1020100095244A patent/KR20110060793A/ko not_active IP Right Cessation
- 2010-10-21 US US12/909,581 patent/US20110126575A1/en not_active Abandoned
- 2010-11-29 EP EP10015097A patent/EP2333459A3/fr not_active Withdrawn

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
JP2007107858A (ja)	2005-10-17	2007-04-26	Sanyo Electric Co Ltd	冷凍装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CN1052472C (zh) *	1994-11-16	2000-05-17	新疆哈密制药厂	结合有烟酰胺和锌的乙酰水杨酸衍生物
WO2013000758A3 (fr) *	2011-06-29	2013-06-06	BSH Bosch und Siemens Hausgeräte GmbH	Appareil frigorifique
EP3037744A4 (fr) *	2013-09-27	2016-11-02	Panasonic Healthcare Holdings Co Ltd	Dispositif de réfrigération
WO2015176939A1 (fr) *	2014-05-20	2015-11-26	BSH Hausgeräte GmbH	Machine frigorifique
EP4137754A4 (fr) *	2020-06-04	2023-10-11	PHC Holdings Corporation	Dispositif de réfrigération binaire

Also Published As

Publication number	Publication date
EP2333459A3 (fr)	2011-09-21
CN102080903A (zh)	2011-06-01
US20110126575A1 (en)	2011-06-02
JP2011112351A (ja)	2011-06-09
KR20110060793A (ko)	2011-06-08

Publication	Publication Date	Title
EP2333459A2 (fr)	2011-06-15	Appareil de réfrigération
EP2019270B1 (fr)	2017-12-13	Système de réfrigération
EP2019269A1 (fr)	2009-01-28	Système de réfrigération
AU2007338832B2 (en)	2014-05-08	Fluorinated compositions and systems using such compositions
JP5674157B2 (ja)	2015-02-25	冷却器用途において用いるためのトランス−クロロ−３，３，３−トリフルオロプロペン
KR100652080B1 (ko)	2006-12-01	냉동 장치
EP2019276B1 (fr)	2020-01-08	Dispositif de congélation
EP2019271A1 (fr)	2009-01-28	Système de réfrigération
JP6543450B2 (ja)	2019-07-10	冷凍装置
US20040124394A1 (en)	2004-07-01	Non-HCFC refrigerant mixture for an ultra-low temperature refrigeration system
KR20230035461A (ko)	2023-03-13	냉장 시스템 및 방법
JPH08303882A (ja)	1996-11-22	新代替冷媒ガスｈｆｃを使用したヒートポンプの運転方法
JPH08165465A (ja)	1996-06-25	冷媒組成物及び冷凍装置
JP3327705B2 (ja)	2002-09-24	冷媒組成物及びこれを用いた冷凍装置
JP2007169331A (ja)	2007-07-05	超低温用非共沸混合冷媒及びそれを使用した超低温用一元式冷凍回路
JP2011133224A (ja)	2011-07-07	冷凍装置

Legal Events

Date	Code	Title	Description
2011-05-13	PUAI	Public reference made under article 153(3) epc to a published international application that has entered the european phase	Free format text: ORIGINAL CODE: 0009012
2011-06-15	AK	Designated contracting states	Kind code of ref document: A2 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR
2011-06-15	AX	Request for extension of the european patent	Extension state: BA ME
2011-08-19	PUAL	Search report despatched	Free format text: ORIGINAL CODE: 0009013
2011-09-21	AK	Designated contracting states	Kind code of ref document: A3 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR
2011-09-21	AX	Request for extension of the european patent	Extension state: BA ME
2011-09-21	RIC1	Information provided on ipc code assigned before grant	Ipc: F25B 41/06 20060101ALI20110812BHEP Ipc: F25B 9/00 20060101ALI20110812BHEP Ipc: F25B 7/00 20060101ALI20110812BHEP Ipc: F25B 40/00 20060101AFI20110812BHEP
2012-04-11	17P	Request for examination filed	Effective date: 20120301
2012-09-05	RAP1	Party data changed (applicant data changed or rights of an application transferred)	Owner name: PANASONIC HEALTHCARE CO., LTD.
2013-04-03	17Q	First examination report despatched	Effective date: 20130305
2015-10-02	STAA	Information on the status of an ep patent application or granted ep patent	Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN
2015-11-04	18D	Application deemed to be withdrawn	Effective date: 20150602

EP2333459A2 - Appareil de réfrigération - Google Patents

Info

Links

Images

Classifications

Definitions

Landscapes

Applications Claiming Priority (1)

Publications (2)

Family

ID=43805637

Family Applications (1)

Country Status (5)

Cited By (5)

Families Citing this family (20)

Citations (1)

Family Cites Families (22)

Patent Citations (1)

Cited By (5)

Also Published As

Similar Documents

Legal Events