US3683640A - Inert gas type absorption refrigeration apparatus employing secondary refrigeration system - Google Patents

Inert gas type absorption refrigeration apparatus employing secondary refrigeration system Download PDF

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US3683640A
US3683640A US94298A US3683640DA US3683640A US 3683640 A US3683640 A US 3683640A US 94298 A US94298 A US 94298A US 3683640D A US3683640D A US 3683640DA US 3683640 A US3683640 A US 3683640A
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mixture
temperature
refrigerant
refrigeration system
cooling element
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Nicolas Eber
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Electrolux AB
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Electrolux AB
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/10—Sorption machines, plants or systems, operating continuously, e.g. absorption type with inert gas
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/62—Absorption based systems

Definitions

  • a secondary refrigeration system partly filled with [a mixture of volatile liquids has an evaporation portion to abstract heat from the objective of cooling and a condensation portion which, along its length, is in thermal exchange relation with the cooling element.
  • the mixture of volatile liquids forms a refrigerant fluid mixture which possesses suchphysical properties that the refrigerant fluids will vaporize in the evaporation portion or condense in the condensation portion or vaporize and condense in both portions, respectively, at different temperatures between the first and second higher temperatures prevailing in the cooling element.
  • the circulation of the refrigerant fluid mixture in the secondary refrigeration system is effected solely by vapor bubbles resulting from the vaporization and boiling of the mixture of refrigerant fluids in the evaporation portion.
  • cooling unit In absorption refrigeration apparatus of the inert gas type the construction of the cooling unit is dependent on several conditions which makes it difficult to fabricate the cooling unit in the most desirable way in each given situation.
  • the cooling unit must be positioned a sufficient distance below the condenser to promote gravity flow of condensed refrigerant to the cooling unit, such flow being dependent upon the hydrostatic pressure of a column of liquid refrigerant.
  • the cooling unit and condenser must be vertically spaced a sufficient distance so that, when the refrigeration apparatus is initially started, the light refrigerant condensate formed in the condenser will displace heavy absorption solution present in the con 7 densate line at such time. Further, the cooling unit must be so constructed that liquid traps, which prevent unobstructed circulation of inert gas, are avoided.
  • the cooling unit piping employed desirably has a comparatively large diameter.
  • the size of this piping in turn has a direct bearing with respect to the difficulties encountered in bending the piping. This is so because the smallest bending radius of piping is dependent upon the diameter of the piping.
  • the cooling unit must be located sufficiently high above the absorber to produce and develop a force within the apparatus to promote proper circulation of gas in the inert gas circuit.
  • liquid refrigerant evaporates into inert gas circulating therethrough.
  • the temperature at which liquid refrigerant evaporates into inert gas, at different regions along the path of flow of circulating inert gas, is dependent upon the partial pressure of refrigerant vapor in the inert gas.
  • the partial pressure of refrigerant vapor in the inert gas and the temperature at which liquid refrigerant evaporates will both constantly increase.
  • the quantity of liquid refrigerant that can be evaporated per degree of temperature increases with increasing temperature in relation to the saturation curve for pressure and temperature of the refrigerant,
  • the uniform cooling temperature in the secondary refrigeration system corresponds to the highest temperature prevailing in the cooling unit of the primary absorption refrigeration apparatus. If it is desired to operate such a secondary system at a low temperature the total cooling effect of the primary absorption refrigeration apparatus has to be effected at a temperature which is at a value below the temperature at which it is desired to operate the secondary system. Under these conditions the operation of the primary absorption refrigeration apparatus involves a considerable consumption of effect and a correspondingly low efficiency of the entire refrigerating structure.
  • the aforementioned combination 0 primary and secondary refrigerating structures has been employed only when the range of operating temperatures of the cooling unit of the primary absorption refrigeration apparatus under all operating conditions encountered will be small, such as, for example, in refrigerators primarily employed for freezing purposes.
  • My invention relates to absorption refrigeration apparatus of the inert gas type having a secondary refrigeration system associated therewith which includes a condensation portion capable of operating at a plurality of temperatures, that is, in a temperature range rather than at one temperature which is characteristic of secondary refrigerating systems heretofore provided.
  • the evaporation characteristic of the mixture of refrigerants in the evaporation portion of the secondary system which may be two refrigerants, for example, depends upon a number of factors which includes the physical characteristics of the individual refrigerants in the mixture, the composition or make-up of the mixture, the working pressure of the secondary system, and the relation between the quantity of volatile liquid circulating in the secondary system and the quantity of vapor formed in the system. This last-mentioned relation in turn depends on the refrigerating load on the secondary system and the resistance offered in the system to flow of fluids therein which is determined, among other things, by the cross-sectional areas of the condensation and evaporation portions and conduits connecting these parts.
  • the circulation of volatile liquids in the secondary system is promoted by vapor formed in the system.
  • a mixture of refrigerants can be formed more or less theoretically by selecting individual refrigerants whose thermo-dynamic properties are well known and available, for example, from an enthalphy mixture diagram. Under these conditions, a more or less arbitrary assumption of the composition of the mixture of volatile liquids and the operating pressure of the system is made. The evaporation characteristic obtained for the mixture is compared, preferably graphically, with the corresponding characteristic of the cooling element of the primary absorption refrigeration apparatus. Then the assumptions initially made are corrected until a satisfactory correspondence is obtained between the characteristic of the mixture of volatile liquids and that of the cooling element of the primary refrigeration apparatus.
  • a mixture of volatile liquids that can be employed in secondary refrigerating systems embodying my invention are available under the trademark Freon" and include Freon 12" and Freon 13 with Freon 13 comprising approximately 30 percent by weight of the mixture.
  • FIG. 1 is a viewmore or less diagrammatically illustrating an absorption refrigeration apparatus of the inert gas type to which the invention has been applied;
  • FIG. 2 is a vertical sectional view of a refrigerator and a cooling arrangement therefor provided by a secondary refrigeration system which embodies the invention and is associated with primary absorption refrigeration apparatus like that shown in FIG. 1;
  • FIG. 3 is a view similar to FIG. 2 illustrating another embodiment of the invention.
  • FIG. 4 illustrates temperature curves obtained in accordance with the invention of a cooling element of primary absorption refrigeration apparatus and the condensation portion of a secondary refrigeration system associated therewith.
  • FIG. 1 l DESCRIPTION OF THE PREFERRED EMBODIMENT
  • a refrigeration system comprises a generator or boiler 10 containing a refrigerant, such as ammonia, in solution in a body of absorption liquid, such as water.
  • a refrigerant such as ammonia
  • the heating tube 11 may be heated in any suitable manner, as by an electrical heating element or a liquid or gaseous fuel burner 12, for example, which is adapted to project its flame into the lower end of the tube.
  • the heat supplied to the boiler 10 and its contents expels refrigerant vapor out of solution, and the vapor thus generated flows to an air-cooled condenser 14 in which it is condensed and liquefied.
  • Liquid refrigerant flows from condenser 14 through a conduit 15 into a cooling element 16 in which it evaporates and diffuses into an inert pressure equalizing gas, such as hydrogen, which enters the lower part thereof from a gas heat exchanger 17. Due to evaporation of refrigerant fluid into inert gas, a refrigerating effect is produced and heat is abstracted from the surroundings.
  • the rich gas mixture of refrigerant vapor and inert gas formed in cooling element 16 flows from the upper part thereof through a conduit 18, gas heat exchanger 17, conduit 19 and absorber vessel 20 into the lower part of an absorber coil 21.
  • absorber coil 21 the rich gas mixture flows countercurrent to downwardly flowing absorption liquid which enters through a conduit 22.
  • the absorption liquid absorbs refrigerant vapor from inert gas, and inert gas weak in refrigerant flows from the upper part of absorber coil 21 in a path of flow including conduit 23 and gas heat exchanger 17 into the lower part of cooling element 16.
  • the circulation of gas in the gas circuit just described is due to the difference in specific weight of the columns of gas rich and weak, respectively, in refrigerant vapor. Since the column of gas rich in refrigerant vapor and flowing from the upper end of the cooling element 16 to the absorber coil 21 is heavier than the column of gas weak in refrigerant vapor and flowing from absorber coil 21 to the lower end of the cooling element 16, a force is produced or developed within the system for causing circulation of gas in the manner described.
  • Absorption solution flows downwardly through coil 21 into the absorber vessel.20, and such solution, which is enriched in refrigerant, passes from the vessel through a conduit 24 and an inner passage or pipe 25 of liquid heat exchanger 26 into the lower end of a vapor lift pipe or tube 27 which is in thermal exchange relation with the heating tube 11, as by welding. Liquid is raised by vapor-liquid lift action through pipe 27 into the upper part of boiler 10.
  • the outlet end of condenser 14 is connected by an upper extension of conduit and a conduit 28 to a part of the gas circuit, as to the upper part of conduit 19, for example, so that any inert gas which may pass through the condenser 14 can flow into the gas circuit.
  • the absorption liquid from which refrigerant vapor has been expelled flows from the boiler 10 through a connection 29, an outer pipe or passage 30 of the liquid heat exchanger 26 and conduit 22 into the upper part of the absorber coil 21.
  • the circulation of absorption solution in the liquid circuit just described is effected by raising of liquid through pipe 27.
  • a hermetically sealed secondary refrigerating system 34 in FIG. 2 which has a condensation portion 35 in thermal exchange relation with the cooling element 16 and evaporation or vaporization portions 36 and 37 arranged to abstract heat from the spaces 31 and 32.
  • the spaces 31 and 32 respectively serve as a freezer section and a section for storing foods, as will be explained presently.
  • the lower end of the condensation portion 35 is connected by a conduit 38 to the lower end of the vaporization portion 36, the upper end of which is connected to the upper end of a standpipe 39 disposed exteriorly of the cabinet 33.
  • the upper end of standpipe 39 is connected by a conduit 40 to the upper end of the condensation portion 35.
  • the lower end of the vaporization portion 37 is connected to the lower end of the standpipe 39 and the upper end thereof is connected to an intermediate region of the standpipe between its upper and lower ends.
  • the secondary condenser 35, vaporization portions 36 and 37, standpipe 39 and connecting conduits 38 and 40 form a closed fluid circuit which, after being evacuated, is partly filled with a mixture of volatile liquids, such as Freon 12 and Freon 13", for example, in the proportions referred to above.
  • the secondary refrigerating system is initially charged with the mixture of volatile liquids so that the liquid surface level in the standpipe 39 will reach the level 41, as shown in FIG. 2.
  • inert gas weak in refrigerant and flowing from the gas heat exchanger 17 is introduced into the lower end of the cooling element 16 at 42.
  • Inert-gas flows upward through the cooling element 16 in counter flow to downwardly flowing liquid refrigerant which flows into the cooling element through the conduit 15.
  • Inert gas saturated with refrigerant vapor passes from the upper end of the cooling element 16 at 43.
  • the cooling element 16 comprises a conduit which provides an elongated path of flow for the inert gas and has a temperature gradient in which the temperature progressively increases from a first temperature at .its lower end at 42 to a second higher temperature at its opposite upper end 43 in the path provided by flow of the cooling element.
  • the inert gas flows upward in the cooling element 16 from its lower end 42 to its upper end 43, the gas in the lower end contains a lesser amount of refrigerant'vapor than the gas in the upper end.
  • the partial vapor pressure of the refrigerant is a gradient, so that the temperature of liquid refrigerant in the cooling element 16 also is a gradient, the evaporating temperature being lower at the lower end 42 of the cooling element and higher at the upper end 43 thereof.
  • the conduit forming the condensation portion 35 extends lengthwise of the cooling element 16 and is in thermal exchange relation therewith in any suitable manner, as by welding, for example.
  • the cooling effect produced'by the cooling element 16 is transmitted to the condensation portion 35 which causes evaporation of the volatile liquids in the vaporization portions 36 and 37, thereby taking up heat from air in the freezer and'storage sections 31 and 32, respectively.
  • the vapor bubbles formed in both vaporization por tions 36 and 37 flow through the upper part of standpipe 39 and conduit 40 into the condensation portion 35 in which it is condensed and liquefied by the cooling element 16. Condensation of vapor in the condensation portion 35 takes place in such manner that the mixture of refrigerant fluids in the secondary system is in the form of condensate at the lower end of the condensation portion. Vapor components having different evaporating temperatures are condensed in different parts of the condensation portion 35. Vapor components with a high evaporating temperature, or vapor components which for the most part have a high evaporating temperature, are initially condensed in the upper part of the condensation portion. The condensation of vapor components remaining in the vapor mixture and having lower evaporating temperatures is effected at an increasingly higher rate toward the lower end of the condensation portion 35.
  • Condensate formed in the condensation portion 35 flows therefrom into the lower end of the vaporization portion 36.
  • Components of the refrigerant fluid mixture having low evaporating temperatures vaporize in the vaporization portion 36.
  • the vapor bubbles formed in the vaporization portion 36 function to force and raise liquid therein for gravity flow from the upper end of the portion 36 into the standpipe 39, the internal diameter of the vaporization portion 36 being sufficiently small to effect such raising of liquid.
  • Vapor is separated from liquid in the standpipe 39, the vapor flowing through the conduit 40 to the condensation portion 35 and the liquid refrigerant flowing into the lower end of the vaporization portion 37.
  • Components of the refrigerant fluid mixture having a high evaporating temperature evaporate in the vaporization portion 37.
  • the vapor bubbles formed in the vaporization portion 37 also function to force and raise liquid therein, the internal diameter of the vaporization portion 37 being sufficiently small to effect such raising of liquid by vapor-liquid lift action in a manner similar to that described above in describing the manner in which the vaporization portion 36 functions. It will be seen in FIG. 2 that liquid and lifting vapor from the upper end of the vaporization portion 37 flows into the standpipe 39 and the vaporization portions 36 and 37 provide two paths of flow for circulating refrigerant fluid having a part common to both of them.
  • the secondary refrigerating system 34 is partly filled with a mixture of volatile liquids which form the refrigerant fluid mixture.
  • the circulation of the refrigerant fluid mixture in the secondary system 34 is effected solely by the vapor bubbles formed in the vaporization portions 36 and 37 in the manner just explained. This is so because, in the secondary system 34 of FIG. 2, an inert gas is not relied upon to effect circulation of the refrigerant fluid mixture.
  • the vapor bubbles are formed as the result of evaporation of the refrigerant fluid mixture which takes up heat thereby transmitting cooling effect and cooling the separate compartments 36 and 37.
  • the vapor bubbles resulting from the vaporization and boiling of the volatile fluid itself which is a boiling mixture of at least two volatile fluids, effects circulation of the refrigerant fluid mixture in the secondary refrigerating system 34.
  • the condensation portion and vaporization portions 36 and 37 Since there is unobstructed communication between the condensation portion and vaporization portions 36 and 37, these portions will all operate at substantially the same pressure.
  • the vaporization portion 36 In view of the fact that the liquid refrigerant mixture flowing to the low temperature vaporization portion 36 contains more components having a low evaporating temperature than the liquid refrigerant mixture flowing to the higher temperature vaporization portion 37, the vaporization portion 36 inherently will operate at a lower temperature than the vaporization portion 37 which is disposed below the vaporization portion 36. Further, liquid refrigerant will evaporate in each of the vaporization portions 36 and 37 at increasingly higher temperatures from their lower ends to their upper ends. This is an advantage rather than a disadvantage because the secondary refrigeration system in its entirety can operate at an exceptionally high efficiency.
  • the vaporization portions 36 and 37 may assume different shapes and heat transfer members or fins may be provided to promote heat transfer from the objective of cooling, that is, the air in the thermally segregated spaces 31 and 32 and the meat and food products stored therein.
  • the vaporization portions 36 and 37 can be heat conductively connected to inner metallic liners or wall surfaces of the spaces 31 and 32, either at their inner exposed sides or at the opposite outer sides at which regions they are enveloped in insulation.
  • FIG. 3 diagrammatically illustrates another embodiment of my invention in which parts similar to those shown in FIG. 2 are referred to by the same reference numeral to which is added.
  • all of the parts of the secondary refrigeration system 134 are connected in series to provide a single path of flow for the refrigerant fluid mixture.
  • the vaporization portion 137 in the bottom space 132 operates at a lower temperature than the vaporization portion 136 in the top space 131.
  • the bottom space 132 serves as a freezer while the top space 131 serves as a storage compartment for storing foods at a temperature which preferably is above the freezing temperature.
  • the refrigerant fluid mixture is condensed in the condensation portion in the same manner that refrigerant is condensed in the condensation portion 35 in FIG. 2, as explained above; and the condensate, which comprises fluid components having dif' ferent evaporating temperatures, flows into the standpipe 139 to the level 141 therein. From the standpipe 139 condensate flows into the lower end of vaporization portion 137. Components of the refrigerant fluid mixture having low evaporating temperatures vaporize in the vaporization portion 137. The vapor bubbles formed in the vaporization portion 137 flow upwardly therethrough.
  • Components of the refrigerant fluid mixture having high evaporating temperatures vaporize in the vaporization portion 136. While both the vaporization portions 137 and 136 may be of the flooded-type, as determined by the liquid level 141 in the standpipe 139, the internal diameter of the vaporization portion 136 also can be sufficiently small to force and raise liquid therein by vapor-liquid lift action. Refrigerant vapor, together with any unevaporated refrigerant, will then flow through conduit 144 from the upper end of vaporization portion 136 to the condensation portion 135. As in the first described embodiment, all of the parts of the secondary refrigeration system shown in FIG. 3 operate at substantially the same pressure.
  • the vaporization portion 137 Since the liquid refrigerant mixture flowing to the low temperature vaporization portion 137 contains more components having a low evaporating temperature than the liquid refrigerant mixture flowing to the higher temperature vaporization portion 136, the vaporization portion 137 inherently will operate at a lower temperature than the vaporization portion 136 which is disposed above the vaporization portion 137. As in the first-described embodiment, liquid will evaporate in each of the vaporization portions 136 and 137 at increasingly higher temperatures from their lower ends to their upper ends.
  • temperature curves A and B show the manner in which the secondary refrigeration system embodying my invention functions. More particularly, temperature curves A and B show the temperature conditions prevailing lengthwise of the cooling element 16 of the primary absorption refrigeration apparatus and the condensation portion 35,135 of the secondary refrigeration system which is in heat exchange relation therewith.
  • Curve A a solid line, illustrates the temperatures prevailing in the cooling element 16 along the length L from its lower end 42 to its upper end 43.
  • CurveB a dotted line, illustrates the temperatures prevailing in the condensation portions 35 and 135 along their lengths between regions at the same levels as the lower and upper ends 42 and 43, respectively, of the cooling element 16.
  • curves A and B are essentially parallel throughout their lengths.
  • a given temperature differential prevails between the temperature of the cooling element 16 and the condensation portions 35 and 135, thus maintaining the parallelism of the curves A and B.
  • Deviations of the parallelism of the curves A and B which depend on the refrigerant fluids forming components or constituents of the refrigerant fluid mixture in the secondary system,
  • Absorption refrigeration apparatus having a. a circuit for circulation of inert gas including a cooling element comprising first conduit means in which refrigerant fluid evaporates in the presence of such gas,
  • said first conduit means providing an elongated path of flow for the inert gas and having a temperature gradient in which the temperature progressively increases from a first temperature at one end to a second higher temperature at the opposite end in the path of flow of said cooling element,
  • said secondary refrigeration system being partly filled with a mixture of volatile liquids which form a refrigerant fluid mixture that boils and vaporizes in said evaporation portion and forms vapor bubbles, the heat of vaporization to form the vapor bubbles being abstracted from the objective of heating whereby cooling thereof is effected,
  • condensation portion comprising second conduit means which, along its length,is in thermal exchange relation with said first conduit means
  • said mixture of refrigerant fluids possessing such physical properties that said refrigerant fluids will vaporize and condense in said evaporation and condensation portions, respectively, at different temperatures between the first and second higher temperatures prevailing in said cooling element, and
  • Apparatus as set forth in claim 1 including structure providing atleast two insulated spaces which are thermally segregated from one another and define the objective of cooling, said evaporation portion of said secondary refrigeration system including at least two sections which operate at different temperatures and each of which is arranged to abstract heat from a different one of said insulated spaces.
  • Apparatus as set forth in claim 1 including structure providing at least two insulated spaces which are thermally segregated from one another and define the objective of cooling, said secondary refrigeration system comprising first and second branches connected to receive said mixture of volatile liquids, and said first branch including one section of said evaporation portion which operates at a first mean temperature and is arranged to abstract heat from one of said two insulated spaces and said second branch including another section of said evaporation portion which operates at a second higher mean temperature and is arranged to abstract heat from the other of said two insulated spaces.
  • Absorption refrigeration apparatus having a. a circuit for circulation of inert gas including a cooling element comprising first conduit means in which refrigerant fluid evaporates in the presence of such gas,
  • said first conduit means providing an elongated path of flow for the inert gas and having a temperature gradient in which the temperature progressively increases from a first temperature at one end to a second higher temperature at the opposite end in the path of flow of said cooling element,
  • a secondary refrigeration system which includes an evaporation portion and a condensation portion
  • said secondary refrigeration system being partly filled with a mixture of volatile liquidswhich form a refrigerant fluid mixture that boils and vaporizes in said evaporation portion and forms vapor bubbles, the heat of vaporization to form the vapor bubbles being abstracted from the objective of heating whereby cooling thereof is effected,
  • said condensation portion comprising second conduit means which, along its length, is in thermal exchange relation with said first conduit means
  • Absorption refrigeration apparatus having a. a circuit for circulation of inert gas including a cooling element comprising first conduit means in which refrigerant fluid evaporates in the presence of such gas,
  • said first conduit means providing an elongated path of flow for the inert gas and having a temperature gradient in which the temperature progressively increases from a first temperature at one end to a second higher temperature at the opposite end in the path of flow ofsaid cooling element,
  • a secondary refrigeration system which includes an evaporation portion and a condensation portion
  • said secondary refrigeration system being partly said condensation portion comprising second conduit means which, along its length, is in thermal exchange relation with said first conduit means,
  • said mixture of refrigerant fluids possessing such physical properties that said refrigerant fluids will condense in said condensation portion at different temperatures between the first and second higher temperatures prevailing in said cooling element

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
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US94298A 1969-12-04 1970-12-02 Inert gas type absorption refrigeration apparatus employing secondary refrigeration system Expired - Lifetime US3683640A (en)

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CH (1) CH532231A (enrdf_load_stackoverflow)
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GB (1) GB1268325A (enrdf_load_stackoverflow)
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Cited By (6)

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US4922730A (en) * 1988-02-03 1990-05-08 Sibir Ag Absorption refrigerating unit
WO1990009003A1 (en) * 1989-02-06 1990-08-09 Nim, Incorporated Phase modulated spectrophotometry
US5400615A (en) * 1991-07-31 1995-03-28 Thornliebank Industrial Estate Cooling system incorporating a secondary heat transfer circuit
US20050160744A1 (en) * 2002-03-14 2005-07-28 Michael Frank Superconducting device with a cold head of a refrigeration unit with a thermosyphon effect thermally coupled to a rotating superconducting winding
WO2008142412A1 (en) * 2007-05-22 2008-11-27 4Energy Ltd. Temperature-controlled cabinet
US20130061629A1 (en) * 2011-03-08 2013-03-14 Atwood Mobile Products Llc Helium charged refrigerator

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CH668633A5 (de) * 1986-02-04 1989-01-13 Nicolas Dr Sc Techn Eber Kuehlbar mit absorptionskuehlaggregat.
GB9612445D0 (en) * 1996-06-14 1996-08-14 Star Refrigeration Thermosyphon refrigeration apparatus
RU2186303C2 (ru) * 2000-08-04 2002-07-27 Сибирская аэрокосмическая академия Способ получения холода в абсорбционно-диффузионном холодильном агрегате

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Cited By (10)

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US4922730A (en) * 1988-02-03 1990-05-08 Sibir Ag Absorption refrigerating unit
WO1990009003A1 (en) * 1989-02-06 1990-08-09 Nim, Incorporated Phase modulated spectrophotometry
US5400615A (en) * 1991-07-31 1995-03-28 Thornliebank Industrial Estate Cooling system incorporating a secondary heat transfer circuit
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US20050160744A1 (en) * 2002-03-14 2005-07-28 Michael Frank Superconducting device with a cold head of a refrigeration unit with a thermosyphon effect thermally coupled to a rotating superconducting winding
US7272938B2 (en) * 2002-03-14 2007-09-25 Siemens Aktiengesellschaft Superconducting device with a cold head of a refrigeration unit with a thermosyphon effect thermally coupled to a rotating superconducting winding
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US20130061629A1 (en) * 2011-03-08 2013-03-14 Atwood Mobile Products Llc Helium charged refrigerator

Also Published As

Publication number Publication date
CH532231A (de) 1972-12-31
GB1268325A (en) 1972-03-29
SE336141B (enrdf_load_stackoverflow) 1971-06-28
DE2058161A1 (de) 1971-06-09

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