US3580004A - Apparatus for defrosting cooling units of absorption refrigeration systems - Google Patents

Apparatus for defrosting cooling units of absorption refrigeration systems Download PDF

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US3580004A
US3580004A US776535A US3580004DA US3580004A US 3580004 A US3580004 A US 3580004A US 776535 A US776535 A US 776535A US 3580004D A US3580004D A US 3580004DA US 3580004 A US3580004 A US 3580004A
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liquid
vapor
pump
absorption
heat
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US776535A
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Wilhelm Georg Kogel
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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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/027—Defrosting cycles for defrosting sorption type 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 vapor expulsion unit having a [3 l] 15818/67 heat receiving part from which heat is derived for expelling refrigerant vapor from absorption liquid.
  • the vapor expulsion unit includes a first pump for lifting liquid by vapor-liquid lift action to effect normal circulation of absorption liquid during operation of the system.
  • the heat receiving part is heated by a [54] APPARATUS FOR DEFROSTING COOLING UNlTS source of lies ⁇ : cplntlzolled by a thermostat affected by the tem- OF ABSORPTION REFRIGERATION SYSTEMS pet-Store o!
  • the present invention relates to apparatus for achieving defrosting in an absorption refrigerating apparatus operation with inert and having a thermosiphon pump which praises fluid from the absorption liquid circuit to the evaporator system.
  • the apparatus is provided with a connecting conduit between the vapor space of the boiler system and the evaporator system, part of the conduit having the shape of a U-pipe.
  • the present invention has for its purpose to provide apparatus for defrosting in shorter periods following close to each other and, particularly, being to some extent adapted to the need of defrosting. Further, it is an object of the invention to provide an improved defrosting arrangement by simple and cheap but reliable means.
  • the intended purpose is achieved according to the invention mainly thereby that apump other than the absorption liquid circulation pump is supplied with absorption solution intermittently and automatically and operated by the heat receiving part of the boiler system of the apparatus from which heat is derived to effect operation of the apparatus.
  • FIG 1 illustrates an absorption refrigerating apparatus embodying the invention which operates with inert gas and is provided with an analyzer
  • FIGS. 2 to 4 are fragmentary views of the refrigerating apparatus shown in FIG. I to illustrate other embodiments of the invention
  • FIG. 4a is a fragmentary sectional view taken at line 40-441 of FIG. 4
  • FIG. 5 is another fragmentary view of the refrigeration apparatus illustrated in FIG. l which shows the invention used in an absorption refrigerating apparatus without an analyzer.
  • FIG. 1 shows mainly schematically an absorption refrigerating apparatus which is well known but which is furthermore provided with a means for defrosting according to the invention.
  • the refrigerating apparatus can operate with ammonia as refrigerant, water as absorption medium and hydrogen as inert gas.
  • Absorption solution rich in refrigerant passes from the absorber vessel through the outer conduit of the liquid heat exchanger 11.
  • the rich solution from an end of the liquid heat 5 exchanger is supplied to the liquid circulation pump 12 of the apparatus, the pump with its suction side 13 being connected to the lower part of the heat exchanger.
  • the pump 12 is heat conductively connected to a sleeve 14 which functions as a heat receiving part and in which an electric heating cartridge 9 is placed.
  • This sleeve can also be replaced by a flue for a burner operable by gas or kerosene.
  • the rich solution is pumped up to a standpipe 15 from which the weak absorption solution is conducted through the inner conduit of the liquid heat exchanger 11 and a conduit 16 and flows over into the upper part of the absorber 17.
  • the weak solution flows down through the absorber 17 in countercurrent to inert gas rich in refrigerant and coming from the evaporator system and which washed out of refrigerant, whereafter the rich solution is collected in the absorber vessel 10.
  • the liquid heat exchanger 11 has an essentially horizontal portion 18 placed at a comparatively high level which is situated lower (about 25 mm.) than the liquid level I which, on account of the level of the heat conductive connection between the pump 12 and the sleeve 14, is normal for the liquid in the absorber vessel 10 when the apparatus is in operation.
  • the ammonia vapors generated in the pump 12 are separated in the standpipe 15 from the lifted solution and pass through a vapor conduit 19 which discharges into the horizontal portion 18 of the liquid heat exchanger where the vapor bubbles through the rich solution which flows from the absorber vessel 10 and is somewhat preheated in the liquid heat exchanger 11. Thereafter, the vapor is conducted through a vapor conduit 20 to a rectifier or water separator 21 and a condenser 22.
  • the refrigerant is condensed in the condenser 22 and then flows through a conduit 23 into a low temperature part 24 of the evaporator system where the refrigerant is again evaporated into weak inert gas flowing from the gas heat exchanger 25 of the apparatus.
  • the gas mixture and unevaporated liquid refrigerant flow down into a high temperature part 26 of the evaporator system where further evaporation takes place before the gas mixture is conducted into the gas heat exchanger 25 and a conduit 27 to the absorber vessel 10.
  • a conduit 28 is arranged because the connection between these parts through the conduit 23 is filled with liquid.
  • the refrigeration system is controlled by a thermal bulb 8 which is affected by a temperature condition of the higher temperature evaporator part 26.
  • the thermal bulb 8 which is arranged to be influenced by the temperature of air which is cooled by the higher temperature evaporator part 26, is connected by a conduit 7 to a control device 6 operatively associated with a switch 5 connected in one of the conductors 4 for supplying electrical energy to heating element 9.
  • the thermal bulb 8 and conduit 7 form part of an expansible fluid thermostat which is charged with a suitable volatile fluid and responds to changes in a temperature condition affected by the higher temperature evaporator part 26 to operate control device 6 and the switch 5 operatively associated therewith to close and open the switch with increase and decrease, respectively, of the temperature of the air cooled by the higher temperature evaporator part 26.
  • a pipe 29 is connected to the vapor conduit 19 at a point 30' the pipe 29 extends down from the lower end of the sleeve for a distance which is longer than the distance between the liquid level 1 in the absorber vessel and the level of the connection of the vapor conduit 19 to the liquid heat exchanger 11 at the horizontal portion 18 thereof.
  • a second pump 31 is connected to the lower part of the pipe 29. This pump discharges into the upper part of a pipe 32 which is inclined downward and connected to the inlet to the high temperature evaporator element 26 of the apparatus.
  • the second pump 31 has an inner diameter which is smaller than the diameter of pump 12 of the apparatus which is employed to circulate absorption liquid in its circuit. With about the same location and length as the heat conductive contact between the liquid circulation pump 12 and the sleeve 14, the second pump 31 is arranged in heat conductive connection with the liquid circulation pump 12.
  • the liquid level in the pipe 29 stands at a low point 33.
  • the liquid is in direct connection with the low pressure side of the apparatus and extends up to a level 34 which is as much higher situated than the level 33 in the conduit 29 as the height difference between the liquid level 1 in the absorber vessel 10 and the inlet of the vapor pipe 19 to the liquid heat exchanger portion 18. Since the liquid levels 33 and 34 are situated under the heat source of the apparatus, the defrosting pump is out of action. Because the pump 31 has a heat conductive connection to the heat source of the apparatus in the sleeve 14 only by the intermediation of the circulation pump 12, the temperature of the defrosting pump 31 will never exceed the temperature of the circulation pump 12.
  • conduit 29 forms a stationary component of the refrigeration system and provides a passageway for conducting liquid downward from the point or part 30 to the pump 31 when the part 30 is below the liquid level ll in the absorption liquid circuit which occurs when the normal circulation or absorption liquid stops.
  • the circulation pump 12 ceases to operate after a few minutes.
  • the flow from the absorber coil 17, however, continues some minutes more and, because the rest of the liquid circulation has ceased, the liquid level in the absorber vessel and the conduits connected thereto will rise. 1n the vapor conduits 19 and 20, the liquid contents communicate through the outer conduit of the liquid heat exchanger 11 with the absorber vessel 10. Therefore, a corresponding rise of the liquid level will occur also in the two conduits 19 and 20 up to the level 11.
  • the conduit 29 at the vapor conduit 19 is placed at a point 30, which is located below the level ll of the liquid in the absorber vessel 10 and in the vapor conduits 19, 20, when the apparatus is inoperative, the conduit 29 will be filled with hot rich solution which also fills up the lower part of the pump conduit 31 to a corresponding level.
  • the circulation pump 12 starts after a few minutes delay and begins operating the liquid circulation. The vapors generated in the circulation pump press down the liquid in the vapor pipe 19 to the inlet of the portion 18 of the liquid heat exchanger and at the same time a corresponding depressing of liquid in the conduit 29 occurs.
  • the defrosting pump 31 which is heat conductively connected to the circulation pump 12, almost simultaneously with the circulation pump reaches boiling temperature, whereby a mixture of vapor and liquid is supplied to the high temperature part 26 of the evaporator system and defrosting is started. Since the defrosting pump 31 has a smaller diameter than the circulation pump 12 and is connected to the low pressure side of the apparatus, the defrosting pump will have a fast start when the heat source is connected.
  • Boiler systems provided with an analyzer are subject to a pressure difference between the parts which corresponds to the difference in height between the liquid level I in the absorber vessel 10 and the inlet of the vapor conduit 19 to the conduit 18 of the liquid heat exchanger. If this difference in height is 30 mm. for example, the overpressure in the vapor space of the boiler compared with other parts of the apparatus will be 30 mm. water column. This condition prevails as long as the apparatus is in normal operation. lf the operation is interrupted, for instance when the thermostat disconnects the heat source, the temperature in the boiler system falls and therewith the pressure of the ammonia vapor also falls.
  • frost deposits on the evaporator cause serious problems. If a long time is allowed to elapse between defrostings it may occur that such large quantities of frost and ice are formed on the high temperature evaporator that the air circulation around this apparatus part in the refrigerator cabinet is so heavily reduced tat the temperatures in the cabinet itself will be too high in spite of the fact that the evaporator keeps the intended low temperature. This causes the thermostat to have to be adjusted to a higher step in order to compensate for the impaired cabinet temperatures. In this way the operation of the apparatus requires higher costs then would be required under ideal conditions.
  • defrosting can be effected manually by disconnecting the refrigerating apparatus entirely but, then, the low temperature evaporator also is put out of operation which is not at all desirable.
  • a fast defrosting at each thermostat cut-in occurs. Since this happens comparatively often, there will not be time for much frost to accumulate and it is therefore sufficient with successive very short defrosting periods.
  • the apparatus is operating under unfavorable. conditions, for instance at high ambient temperatures or high humidity in the air, the frost formation on the evaporator flanges 35 increases. Then the thermostat of the refrigerating apparatus has to be adjusted to a higher step in order to maintain the intended cabinet temperature, which results in shorter cutoff periods. Therewith, also a greater number of defrostings per 24 hours is obtained, which under these more difficult operating conditions is an advantage.
  • FIG. 2 illustrates another embodiment of how the invention which differs from the embodiment of FIG. 1 in that the connecting conduit 32 to the high temperature evaporator element 26 extends downward from the connecting point 36 of the defrosting pump 31 to n. eonnectin g point 37 of the standpipe 15.
  • the point 37' is s tuated below the liquid level in the standpipe 15 and, therefore, the lower part 37 of the connecting conduit 32 will contain weak absorption solution since it is in communication with solution in the standpipe
  • the connecting point 36 between the defrosting pump 31 and the connecting conduit 32 is situated above the liquid level in the part 37 of the connecting conduit.
  • the defrosting pump 31 is supplied with rich solution from the liquid quantity which during the off-period of the apparatus has accumulated in the pipe 29.
  • the vapors generated in the defrosting pump 31 are conducted through the connecting conduit 32 to the high temperature part 26 of the evaporator while the weak solution lifted in the defrosting pump 31 will flow into the standpipe through the conduit part 37 from which this solution, together with weak solution from the circulation pump 12 will flow through the liquid heat exchanger and the conduit 16 to the top of the absorber 17.
  • the defrosting effect will be smaller than in the embodiment of FIG. 1' provided they otherwise are similar.
  • the absorption solution lifted by the defrosting pump 31 will be useful for the apparatus in its normal operation.
  • connection of the high temperature evaporator 26 to the defrosting pump 31 comprises a U-shaped conduit 38, 39, the leg 38 of which is connected to the high temperature evaporator and the leg 39 of which is connected to the vapor conduit or leg 38 of the apparatus'at a point 40 which is located somewhat higher than the connection of the connecting conduit 38 to the high temperature evaporator 26.
  • the defrosting pump 31 is connected to the leg 39 of the connecting conduit at a point 39' which is located above the liquid level in the 'conduit 39 and just below the connecting point 40 of the leg 39 to the vapor conduit 20.
  • a heat conductive metal sheet 41 connects the vapor conduit to the leg 39 in the connecting conduit.
  • the conductive metal sheet 41 functions to raise the temperature of the right hand leg 39 of the connecting conduit during the on-period and thereby prevent vapors from the vapor pipe 20 from condensing in this part of the connecting conduit. In this way a certain defrosting effect in the evaporator part 26 can be effected and this effect can be varied by changing the height of the liquid seal formed by liquid in the U-shaped conduit 38, 39 while at the same time the vapors lifted in the defrosting pump 31 are used for the normal operation of the apparatus.
  • FIG. 4 illustrates another embodiment of the invention which differs from the embodiment of FIG. 3 in that the liquid to the defrosting pump 31 is supplied from the absorber side instead of from the boiler side of the absorption liquid circuit.
  • the liquid to the defrosting pump 31 is supplied from the absorber side instead of from the boiler side of the absorption liquid circuit.
  • the concentration of refrigerant in that part of the absorber vessel which serves as an accumulating vessel will always be higher than the refrigerant concentration of the solution which drips down into the absorber vessel from the absorber coil.
  • the absorber vessel 50 in FIG. 4 is divided by a partition wall 51 into a circulation vessel 52, to which rich solution flows from the absorber 17 and an accumulating vessel 53, to which unevaporated refrigerant from the evaporator system is introduced through the conduit 27.
  • the refrigerant from the evaporator also contains a certain percentage of water which has accompanied the ammonia vapors from the boiler or vapor expulsion unit to the condenser 22.
  • rich absorption solution flows from the circulation vessel 52 through the outer conduit of the liquid heat exchanger 11 and the circulation pump 12 to the standpipe 15 in order to flow by gravity therefrom through the inner pipe of the liquid heat exchanger 11 and the conduit 16 to the top of the absorber 17.
  • conduit 54 leads, the connecting point of which is located above the liquid level I which prevails in the circulation vessel 52 and the accumulating vessel 53 when the apparatus is in operation.
  • the other end of the conduit 54 extends into the boiler insulation somewhat below the lower end of the sleeve 14.
  • the conduit 54 is connected to the defrosting pump 31 which has its upper end connected to a connecting conduit 39; 38 to the high temperature evaporator 26 in a manner similar to that shown in FIG. 3.
  • the liquid level I in the vessel parts 52, 53 is below the connection of the conduit 54 to the accumulating vessel 53. Since this vessel is supplied with very rich liquid overflowing from the evaporator through the conduit 27, the liquid in the vessel part 53 is somewhat higher than in the other part 52.
  • the liquid level in the conduit 54 is located at a point 55 which lies just below the lower level of the sleeve 14.
  • the liquid level in the vessel parts 52 and 53 during the on-period of the apparatus is located at the line I but rises after cessation of the liquid circulation to the level II which is located higher than the connecting point for the conduit 54. Therefore, occasionally very rich solution is supplied into the conduit 54. Before the thermostat cuts in the heat supply of the apparatus the next time, the conduit 54 is completely filled with very rich solution. Also, very rich solution is present in the conduit 27 and in the vessel part 53. One can count with an ammonia concentration of about 6070 percent in the conduit 54 and in the upper part of the vessel part 53.
  • the ammonia concentration is about 3035 percent. Because the vessel part 53 communicates with the defrosting pump 31, a very rich solution is fed also into this pump. In the circulation pump 12, which is in heat conductive connection with the sleeve 14, a liquid column is present and has an ammonia concentration of about 30-35 percent. In the defrosting pump 31, which is in heat conductive connection with the circulation pump 12,'a liquid column having a concentration of about 6070 percent is present. If the working pressure of the refrigerating apparatus is for instance 25 kg./cm. boiling in the circulation pump 12 is obtained at a temperature of about 150 C, whereas boiling can be obtained in the defrosting pump 31 already at a temperature of about C.
  • the circulation pump 12 When the thermostat cuts in the heat supply of the apparatus, the circulation pump 12 will supply heat and start the defrosting pump 31 without itself starting to function immediately.
  • the ammonia vapors generated in the defrosting pump 31 which are obtained under very favourable conditions, are supplied through the vapor pipe 20 and the condenser 22, as shown in FIG. 1, to the low temperature .evaporator part 24.
  • the solution lifted is, on the other hand, supplied through the connecting conduit 39, 38 to the high temperature evaporator 26 of the apparatus to effect defrosting.
  • the operating height in the vertical part of the conduit 54 will have decreased to such an extent that the pumping in the defrosting pump 31 ceases.
  • the temperature now very rapidly increases in the circulation pump 12 whereby the normal liquid circulation is started.
  • thermosiphon pump 31 in the apparatus, which solution in the embodiment of FIG. 4 just described can very well be richer in refrigerant than the absorption solution conducted to the liquid circulation pump 12 of the apparatus.
  • the quantity of liquid supplied to the separate pump 31 at each occasion is in certain instances larger than the quantity of solution required for the heat transport from the boiler system to the evaporator system.
  • the quantity of working medium lifted by the pump can be divided into vapor and solution and only vapor or only hot solution can be supplied to the evaporator part 26 and the rest be allowed to pass into another apparatus part.
  • the weak solution is conducted into the normal circulation circuit and according to FIGS. 3 and 4, the ammonia vapor is conducted to the condenser.
  • the heat quantities taken out of the boiler system or through the separate pump 31 for defrosting but not used for defrosting, thus do not form an extra source of losses but are instead used to perform useful work in the apparatus.
  • FIG. An embodiment of the invention in such a refrigerating apparatus is shown in FIG. in which the boiler system comprises a shell boiler.
  • the boiler system in FIG. 5 is built around a central pipe 60 in which an electric heating cartridge 9 can be arranged.
  • the central pipe can also fonn a flue for a burner which can be driven by gas or kerosene.
  • a shell 61 surrounds the central pipe 60 and forms the boiler of the apparatus.
  • the liquid circulation pump 62 of the apparatus is arranged inside the shell 61, which contains weak solution.
  • the pump 62 passes through the boiler 61 and is supplied with heat from the surrounding weak solution present in the shell.
  • Rich solution from the absorber coil 63 flows down into the circulation vessel 64 and is thereafter conducted through the outer conduit 65 of the liquid heat exchanger to the liquid circulation pump 62.
  • the weak and boiling solution in the shell 61 transfers heat to the richer solution in the pump pipe 62 whereby liquid and vapor are raised by vapor-liquid lift action to a standpipe 66 and raised liquid flows by gravity through the boiler shell 61, the inner pipe 67 of the liquid heat exchanger upward in a conduit 68 to the top of the absorber 63.
  • a part of the absorber vessel is made to form an accumulating vessel 69 for accumulation of very rich solution overflowing from the evaporator.
  • a conduit 70 is connected to the accumulating vessel 69 at a lever which is situated over the liquid level I present in the vessel when the apparatus is in normal operation and is connected to a separate pump 71 to effect defrosting.
  • the defrosting pump 71 is by welding arranged in heat conductive connection with the boiler shell 61.
  • the upper end of the pump 71 is connected by a conduit 72 to the high temperature evaporator 73.
  • This boiling temperature is much higher than the temperature required for pumping the very rich solution in the conduits 70 and 71 and, since the defrosting pump 61 is arranged in heat conductive connection with the shell of the boiler, the defrosting pump will very quickly supply the quantity of vapor and liquid required to effect defrosting of the high temperature evaporator 73.
  • FIG. 5 only illustrates how the normal operation of the apparatus by the thermostat 6, 7, 8, can be used for supplying rich absorption liquid to the separate pump 71 for transferring heat from the boiler system to the evaporator part 73.
  • the separate pump 71 for transferring heat from the boiler system to the evaporator part 73.
  • An absorption refrigeration system of the inert gas type comprising:
  • an absorption liquid circuit comprising a plurality of said components including a vapor-expulsion unit with a heat receiving part from which heat is derived for expelling refrigerant vapor from absorption liquid;
  • said vapor expulsion unit including a first pump for lifting liquid by vapor-liquid lift action to effect normal circulation of absorption liquid in its circuit during operation of the system;
  • said components further including a condenser and cooling structure having low and higher temperature cooling elements;
  • first conduit means including said condenser for conducting refrigerant fluid from said vapor-expulsion unit to said cooling structure
  • control means including a thermostat affected by the temperature of said higher temperature cooling element for controlling said source of heat to supply heat to said heat receiving part at a rate which will render said first pump operable to raise liquid by vapor-liquid lift action to normally circulate absorption liquid in its circuit during operation of the system or to substantially stop the supply of heat from said heat source to said heat receiving part to render said first pump substantially ineffective to raise liquid by vapor-liquid lift action and substantially stop the normal circulation of absorption liquid in its circuit;
  • said absorption liquid circuit having at least one part at a level which is normally free of liquid and above the liquid level therein when normal circulation of absorption liquid is effected during operation of the system and below the liquid level in said circuit when the normal circulation of absorption liquid has substantially stopped due to said first pump being substantially ineffective to raise liquid by vapor-liquid lift action;
  • second conduit means forming a stationary component of said system and providing a passageway for conducting liquid downward from said one part to said second pump when said one part is below the liquid level in said absorption liquid circuit;
  • An absorption refrigeration system as set forth in claim 1 which includes means for separating the raised liquid and lifting vapor passing from an upper portion of said third conduit means and conducting the separated vapor to said condenser and conducting the raised liquid to said higher temperature cooling element.
  • absorption refrigeration system as set forth in claim I in which said absorption liquid circuit includes said vapor-expulsion unit and an absorber, the absorption liquid normally circulating through and between said unit and said absorber,
  • said absorption liquid circuit includes said vapor-explusion unit and an absorber and a vessel disposed therebetween which is divided by a partition into first and second spaces for holding two bodies of liquid in communication with one another beneath their liquid surface levels, the first space having an inlet and outlet and forming a part of the path of flow of absorption liquid from said absorber to said vapor-expulsion unit, conduit means for conducting refrigerant fluid from said evaporator structure to the second space, and said second conduit means conducting absorption liquid downward to said second pump from the second space of said vessel at a level thereof which functions as said one part of said absorption liquid circuit and at which region the absorption liquid has a higher concentration of refrigerant than in other parts of the absorption liquid circuit.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)
US776535A 1967-11-17 1968-11-18 Apparatus for defrosting cooling units of absorption refrigeration systems Expired - Lifetime US3580004A (en)

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SE15818/67A SE311665B (enrdf_load_stackoverflow) 1967-11-17 1967-11-17

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US (1) US3580004A (enrdf_load_stackoverflow)
CH (1) CH486677A (enrdf_load_stackoverflow)
DE (1) DE1809427A1 (enrdf_load_stackoverflow)
GB (1) GB1226976A (enrdf_load_stackoverflow)
IL (1) IL31016A0 (enrdf_load_stackoverflow)
LU (1) LU57332A1 (enrdf_load_stackoverflow)
SE (1) SE311665B (enrdf_load_stackoverflow)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4870134A (enrdf_load_stackoverflow) * 1971-12-22 1973-09-22
US3807189A (en) * 1971-09-03 1974-04-30 Sarlab Ag Method of and apparatus for defrosting absorption
US6393855B1 (en) * 2001-04-24 2002-05-28 Maytag Corporation Methods and devices for retaining a heating element within a refrigeration cabinet
US20090000488A1 (en) * 2004-01-30 2009-01-01 Johann Magg Method and Electronic Control Device for Controlling Heating Processes in a Coffee Machine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2402413A (en) * 1941-05-28 1946-06-18 Kogel Wilhelm Georg Absorption refrigerating apparatus
US2881598A (en) * 1952-06-17 1959-04-14 Electrolux Ab Heat transfer system of the vaporization-condensation type
US3163997A (en) * 1959-07-10 1965-01-05 Stierlin Hans Method of and apparatus for defrosting absorption cooling systems
US3277665A (en) * 1964-12-03 1966-10-11 Borg Warner Defrost system for gas absorption type refrigerators

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2402413A (en) * 1941-05-28 1946-06-18 Kogel Wilhelm Georg Absorption refrigerating apparatus
US2881598A (en) * 1952-06-17 1959-04-14 Electrolux Ab Heat transfer system of the vaporization-condensation type
US3163997A (en) * 1959-07-10 1965-01-05 Stierlin Hans Method of and apparatus for defrosting absorption cooling systems
US3277665A (en) * 1964-12-03 1966-10-11 Borg Warner Defrost system for gas absorption type refrigerators

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3807189A (en) * 1971-09-03 1974-04-30 Sarlab Ag Method of and apparatus for defrosting absorption
JPS4870134A (enrdf_load_stackoverflow) * 1971-12-22 1973-09-22
US6393855B1 (en) * 2001-04-24 2002-05-28 Maytag Corporation Methods and devices for retaining a heating element within a refrigeration cabinet
US20090000488A1 (en) * 2004-01-30 2009-01-01 Johann Magg Method and Electronic Control Device for Controlling Heating Processes in a Coffee Machine

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Publication number Publication date
SE311665B (enrdf_load_stackoverflow) 1969-06-23
DE1809427A1 (de) 1969-07-17
LU57332A1 (enrdf_load_stackoverflow) 1969-02-26
CH486677A (de) 1970-02-28
GB1226976A (enrdf_load_stackoverflow) 1971-03-31
IL31016A0 (en) 1969-01-29

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