US3389572A - Multiple-effect absorption refrigeration systems - Google Patents

Multiple-effect absorption refrigeration systems Download PDF

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Publication number
US3389572A
US3389572A US642370A US64237067A US3389572A US 3389572 A US3389572 A US 3389572A US 642370 A US642370 A US 642370A US 64237067 A US64237067 A US 64237067A US 3389572 A US3389572 A US 3389572A
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low pressure
refrigerant
solution
high pressure
absorber
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US642370A
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English (en)
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James A Papapanu
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Carrier Corp
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Carrier Corp
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Priority to US642370A priority Critical patent/US3389572A/en
Priority to GB20488/68A priority patent/GB1205989A/en
Priority to FR1563600D priority patent/FR1563600A/fr
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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
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/008—Sorption machines, plants or systems, operating continuously, e.g. absorption type with multi-stage operation
    • 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

  • ABSTRACT OF THE DISCLGSURE A double-effect absorption refrigeration system having a primary absorber, a primary evaporator, a high pressure generator, a low pressure generator, a high pressure condensing section, and a low pressure condenser, connected to provide refrigeration. A plurality of auxiliary absorber stages are connected in a weak solution line between the primary absorber and the high pressure generator.
  • a plurality of auxiliary evaporator stages are connected in an intermediate solution line between the high pressure generator and the low pressure generator, and a plurality of auxiliary evaporator stages are connected in a strong solution line between the low pressure generator and the primary absorber. Stages of the auxiliary evaporators are connected by refrigerant vapor passages with the auxiliary absorbers so as to simultaneously concentrate and cool absorbent solution leaving the generator while also simultaneously heating and diluting weak solution passing to the generators.
  • a low pressure refrigerant economizer is employed to evaporate a portion of the refrigerant condensed in the low pressure condenser to cool the remainder thereof.
  • High pressure refrigerant liquid is passed directly from the high pressure condenser into the low pressure refrigerant economizer to evaporate a portion thereof and cool the remainder.
  • the vapor formed in the economizer is passed to another auxiliary absorber to cool and dilute weak solution.
  • This invention relates to multiple-effect absorption refrigeration systems wherein the heat of the high pressure refrigerant vapor formed in the high pressure generator is reused to form additional low pressure refrigerant vapor, and to further concentrate absorbent solution in the low pressure generator. Both the high pressure refrigerant vapor and the low pressure refrigerant vapor are condensed and passed into the primary evaporator for evaporation therein to produce the refrigeration effect from the system.
  • the large volume of refrigerant vapor produced by flashing in the primary evaporator may entrain droplets of liquid refrigerant which, if carried into the primary absorber, represents a significant loss of refrigeration capacity.
  • the liquid droplets, which reach the absorber are unevaporated refrigerant, which do not produce useful cooling and 3,389,572 Patented June 25, 1968 ice which dilute the absorbent solution in the absorber, thereby reducing the capacity of the system and its efliciency and increasing the heat input required to the generators.
  • a multiple-effect absorption refrigeration system wherein a significant amount of heat is recovered from the refrigerant condensed in the low pressure generator, while, at the same time, the refrigerant is cooled to a lower temperature and pressure than that in the low pressure condenser, so as to reduce loss of capacity and efficiency due to excessive flashing in the primary evaporator.
  • This invention achieves the advantages thereof by utilizing a low pressure refrigerant economizer having a pressure therein intermediate the pressures in the low pressure condenser and the primary absorber.
  • the refrigerant condensed in the condenser section of the low pressure generator is passed directly from the low pressure generator into the low pressure refrigerant economizer.
  • the refrigerant condensed in the low pressure condenser is also passed directly into the low pressure refrigerant economizer.
  • a portion of the refrigerant in the low pressure refrigerant economizer is evaporated to cool the remaining refrigerant down to a temperature only slightly above that of the primary evaporator.
  • the refrigerant vapor thus formed is passed into an auxiliary absorber where it is absorbed in weak solution passing from the primary absorber to the high pressure generator.
  • the drawing illustrates a schematic crosssection through a double-effect absorption refrigeration system in accordance with a preferred embodiment of this invention.
  • a multipleeifect absorption refrigeration system of a type having two effects which may use water as a refrigerant and an aqueous solution of hygroscopic salt, such as lithium bromide, as an absorbent.
  • hygroscopic salt such as lithium bromide
  • Various additives may be added to the solution, such as 2-ethyl hexanol, to enhance heat transfer, and lithium hydroxide to inhibit corrosion.
  • weak solution refers to a solution weak in absorbent salt and absorbing power
  • strong solution refers to a solution strong in absorbent salt and absorbing power.
  • the double-effect absorption system comprises a high pressure generator 7, a low pressure 8 having a high pressure condenser section associated therewith, a low pressure condenser 9, a primary absorber 11 and a primary evaporator 10.
  • Primary evaporator 10 and primary absorber 11 are preferably disposed within a single low pressure shell 16.
  • An internal partition 12 forms a primary absorber chamher and an internal partition 13 forms a primary evaporator chamber within shell 16.
  • a plurality of evaporator heat exchange tubes 14 are arranged within partition 13 for passage of a fluid medium, such as water, to be chilled by the refrigeration system.
  • a plurality of absorber heat exchange tubes 15 are disposed within partition 12 and arranged for passage of a cooling medium, such as water, to a suitable heat rejection location, such as a conventional cooling tower.
  • Liquid refrigerant is distributed over evaporator tubes 14 and is evaporated to cool the fluid passing through the evaporator tubes.
  • the unevaporated refrigerant liquid passes from the bottom of a sump formed by partition 13 through an evaporator recirculation pump 17 and recirculation passage 18 from which it is again distributed over evaporator tubes 14.
  • Cool, concentrated, strong absorbent solution is distributed over absorber tubes 15 and cooled by heat exchange with the medium passing therethrough.
  • a portion of the absorbent solution collected in the bottom of a sump formed by partition 12 is recirculated by absorber recirculation pump 19 through recirculation line 20 from which it is again discharged over absorber tubes 15.
  • a single electric motor 21 may operate both pumps 17 and 19.
  • the absorbent solution in primary absorber 11 is diluted by absorption of refrigerant vapor therein from primary evaporator 10.
  • Cold, moderately weak absorbent solution passes through moderately weak solution passage 25 from the bottom of partition 12 and shell 16 into the first stage 27 of a low pressure auxiliary absorber. From there, the moderately weak solution passes into second stage 28, third stage 29, and fourth stage 30 of the low pressure auxiliary absorber.
  • Each of the stages may be substantially similar and preferably comprises a plurality of perforated liquid distribution pans 31 arranged for cascading flow of liquid from one pan to the succeeding pan throughout each stage.
  • a connecting passage 32 passes solution from first stage 27 to second stage 28 and similar connecting passages are provided between the succeeding stages.
  • a refrigerant vapor inlet passage 33 admits refrigerant vapor to be absorbed into first stage 27, and similar refrigerant vapor inlet passages 34, 35 and 36 admit refrigerant vapor into their respective succeeding stages of the low pressure auxiliary absorber.
  • a low pressure weak solution pump 40 passes warm weak solution from the last stage 30 of the low pressure auxiliary absorber through weak solution passage 41 to the first stage of a high pressure auxiliary absorber.
  • First stage 50 of the high pressure auxiliary absorber may be similar in construction to first stage 27 of the low presto a second stage 53 of the high pressure auxiliary absorber.
  • Second stage 53 is provided with a refrigerant vapor passage 54 for admitting refrigerant vapor into the stage for absorption into absorbent solution therein.
  • the resulting very weak, very warm, absorbent solution is passed through very weak solution line 55 by very Weak solution pump into high pressure generator 7 for concentration therein.
  • Pumps 44) and 60 may be driven by a single electric motor 61.
  • High pressure generator 7 includes generator heat exchange tubes for passing steam in heat exchange relation with absorbent solution therein. Other heating media may be employed, or alternatively, the generator may be directly fired by a combustible gas.
  • the absorbent solution in generator 7 is boiled to vaporize refrigerant and to concentrate the solution.
  • Hot intermediate strength absorbent solution passes from high pressure generator 7 through float valve 66 and intermediate solution passage 7 0, to the first stage 71 of a high pressure auxiliary evaporator.
  • Stage 71 may comprise a hollow vessel in which the incoming solution is discharged against one wall thereof to prevent carryover of liquid droplets into the vapor outlet passage.
  • Refrigerant vapor passage 54 terminates in the vapor space within high pressure auxiliary evaporator stage 71. This passage conducts refrigerant vapor evaporated in high pressure auxiliary evaporator first stage 71 to the last stage 53 of the high pressure auxiliary absorber.
  • Intermediate solution passes from the first stage 71 of the high pressure auxiliary absorber through a solution trap 74 in passage 75 to second stage 78 of the auxiliary high pressure evaporator, which may be similarly constructed to that of the first stage 71.
  • Refrigerant vapor passage 51 conducts refrigerant vapor from second stage 78 of the auxiliary high pressure evaporator to first stage 50 of the high pressure auxiliary absorber.
  • Refrigerant vapor is evaporated from the intermediate absorbent solution in the stages of the high pressure auxiliary evaporator, thereby simultaneously concentrating and cooling the hot intermediate strength solution to form moderately hot, concentrated intermediate solution.
  • the concentrated intermediate solution passes through intermediate solution passage 79 and solution trap 80 into low pressure generator 8.
  • the various solution traps such as traps 74 and 80, are designed to have a vertical height, such that the level of solution in the leg thereof connecting with the next lower pressure stage, balances the solution level and the pressure difference from the previous higher pressure zone to prevent vapor from passing between the stages.
  • Low pressure generator 8 comprises a combined generator-condenser and is provided with heat exchange tubes 83 which form a high pressure condenser section therein.
  • the hot refrigerant vapor formed in high pressure generator 7 passes through high pressure refrigerant vapor passage 67 and heat exchange tubes 83 to boil the solution in the lower pressure generator while condensing the vapor within heat exchange tubes 83.
  • the refrigerant vapor formed in the low pressure generator passes through low pressure refrigerant vapor passage 84 to low pressure condenser 9.
  • the strong absorbent solution formed in low pressure generator 8 passes through solution trap 35 and strong solution passage 87 to the first stage 90 of an auxiliary low pressure evaporator.
  • the refrigerant condensed in high pressure condenser tubes 83 passes through steam trap 96 to low pressure refrigerant economizer 110.
  • First stage 90 and the succeeding stages of the low pressure auxiliary evaporator may be constructed similarly to first stage 71 of the high pressure auxiliary evaporator.
  • Refrigerant vapor passage 36 extends from the last stage 30 of the low pressure auxiliary absorber and terminates in the vapor space in first stage 90 of the low pressure auxiliary evaporator to conduct refrigerant vapor formed in first stage 90 to last stage 30.
  • the strong absorbent solution passes from first stage 90 of the low pressure auxiliary evaporator through solution trap 89 into second stage 92 in which additional refrlgerant is evaporated from the solution.
  • the solution then passes 1nto succeeding stages 93 and 94 where still further evaporation of refrigerant vapor takes place.
  • the concentrated strong absorbent solution passes from last stage 94 through a solution trap into concentrated strong solution line 95 from which it is discharged over absorber heat exchange tubes in primary absorber 11.
  • the low pressure refrigerant vapor passes from low pressure refrigerant vapor passage 84 into low pressure condenser 9 and is condensed therein by heat exchange with a suitable cooling medium passing through condenser heat exchange tubes 97.
  • the cooling medium re ects heat from low pressure condenser 9 to a suitable location, such as a cooling tower.
  • high pressure liquid refrlgerant passes from high pressure refrigerant l quid passage 8 5 into low pressure refrigerant economizer 110 and 1s partially evaporated therein by flashing, thereby cooling the remainder thereof upon being discharged in the low pressure condenser.
  • the resulting vapor is recondensed in condenser 9.
  • Condensed refrigerant passes from low pressure condenser 9 through restriction 98 in low pressure refrigerant passage 99 and is discharged over evaporator heat exchange tubes 14 in primary evaporator 10.
  • a low pressure refrigerant economizer 110 is disposed in low pressure refrigerant liquid passage
  • Low pressure refrigerant economizer 110 may be slmilar in construction to auxiliary evaporator stage 71. Vapor formed in economizer 110 passes through vapor passage 112 and passage 33 into first stage 27 of the low pressure absorber.
  • Low pressure refrigerant restriction 111 and restriction 98 are disposed in the inlet and discharge passages associated with low pressure refrigerant economizer 110 to maintain a pressure zone therein, intermediate the pressure in low pressure condenser 9 and primary evaporator 10.
  • Economizer 110 may be built into the low pressure auxiliary absorber if desired and may comprise an open pan or tray therein through which the refrigerant flows to the primary evaporator 10.
  • the pressures in serially connected low pressure auxiliary absorber stages 27, 28, 29 and 30 successively increase in the direction of solution flow therethrough from primary absorber 11 toward the high pressure auxiliary absorber and high pressure generator 7.
  • the low pressure auxiliary absorber stages from successively increasing pressure zones intermediate the pressures in primary absorber 11 and first stage 50 of the high pressure auxiliary absorber.
  • the pressure in second stage 53 of the high pressure auxiliary absorber is greater than the pressure in first stage 50 thereof.
  • Moderately weak, cold, absorbent solution from primary absorber 11 is successively diluted and heated in the stages of the low pressure auxiliary absorber by absorption of refrigerant vapor therein, to form warm weak solution which passes to the high pressure auxiliary absorber.
  • the warm weak solution is successively further diluted and further heated by absorption of refrigerant vapor therein, as it passes through the stages of the high pressure auxiliary absorber to form very warm, very weak absorbent solution which passes to high pressure generator 7.
  • the intermediate strength absorbent solution from the high pressure generator is further concentrated as it passes through the high pressure auxiliary evaporators by the evaporation of refrigerant vapor therein. At the same time, not only is the concentration of the solution increased, but its temperature is reduced so that only moderately hot but concentrated intermediate solution passes into the low pressure generator.
  • the absorbent solution is further cooled and concentrated by evaporation of refrigerant therefrom in the low pressure generator and the moderately cool strong solution is serially passed through the stages of the low pressure auxiliary evaporator. Still further, refrigerant vapor is evaporated from the strong solution in the low pressure auxiliary evaporator stages. The solution is further cooled, .due to the evaporation of refrigerant therefrom and the cool concentrated strong solution is passed to the primary absorber to absorb refrigerant. vapor therein.
  • both the refrigerant condensed in high pressure condenser 83 and low pressure condenser 9 is passed directly from the condensers into low pressure refrigerant economizer 110.
  • Low pressure refrigerant economizer forms an evaporating zone of pressure intermediate the pressures in low pressure condenser 9 and primary evaporator 10. Consequently, a portion of each of the refrigerant streams passing to the low pressure economizer is evaporated therein and the remaining refrigerant liquid is cooled down to a temperature and pressure relatively close to that existing in primary evaporator 10.
  • the vaporized refrigerant carries the heat of vaporization thereof through refrigerant vapor passages 112 and 33 into first stage 27 of the low pressure auxiliary absorber.
  • the refrigerant vapor is absorbed in the auxiliary absorber into weak solution passing from primary absorber 11 to high pressure generator 7,. thereby both heating and diluting the weak absorbent solution.
  • the cooled refrigerant remaining in low pressure refrigerant economizer 110 passes through a suitable restriction 111 and refrigerant liquid passage 99,. from which it is discharged over heat exchange tubes 14 in the primary evaporator. Since this refrigerant is cooled at a relatively low temperature and pressure, the amount of flashing taking place in the primary evaporator is greatly reduced. Since less refrigerant is required to flash in the primary evaporator, less refrigerant vapor and less non-useful cooling is required in the primary evaporator, and the absorber load is decreased.
  • the problems, attendant flashing of refrigerant in the primary evaporator, such as refrigerant liquid carryover into the absorber, are reduced, as is the amount of heat which must be rejected to the cooling fluid passing through absorber heat exchange tubes 15.
  • the temperature level and heat input to the generator is reduced because the diluted solution boils at a lower temperature and is preheated by absorption of vapor, so the system is more efficient and corrosion is reduced.
  • the heat contained in the refrigerant condensate is re-used in the refrigeration system to provide useful preheating of weak solution and the efiiciency and capacity of the system are improved in comparison with prior arrangements.
  • the absorption refrigeration system may utilize more than two effects and consequently the terms high pressure, low pressure, strong, weak and intermediate and other similar terms are used merely for clarity to distinguish relative relationship of the components, solutions, temperatures or pressures and not as a limitation on the number of effects in the cycle.
  • conventional heat exchangers may be substituted for some or all the stages of the auxiliary evaporators and auxiliary absorbers if desired, although it is desirable to employ a low pressure auxiliary absorber in any event for absorption of refrigerant vapor from the low pressure refrigerant economizer. Accordingly, this invention may be otherwise embodied in the scope of the following claims.
  • An absorption refrigeration system comprising:
  • (M) a low pressure refrigerant economizer having a pressure therein intermediate the pressures in said low pressure condenser and said primary evaporator and substantially the same as the pressure in said auxiliary absorber;
  • (N) high pressure refrigerant liquid passage means for passing refrigerant condensed in said high pressure condenser directly from said high pressure condenser into said low presure refrigerant economizer, for evaporating a portion of said high pressure refrigerant liquid to cool the remainder thereof;
  • (P) refrigerant vapor passage means connecting said refrigerant economizer and said auxiliary absorber for passing refrigerant vapor evaporated in said refrigerant economizer to said auxiliary absorber for absorption therein to thereby heat and dilute the weak solution in said auxiliary absorber prior to passage thereof to said high pressure generator.

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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)
US642370A 1967-05-31 1967-05-31 Multiple-effect absorption refrigeration systems Expired - Lifetime US3389572A (en)

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GB20488/68A GB1205989A (en) 1967-05-31 1968-04-30 Multiple-effect absorption refrigeration systems
FR1563600D FR1563600A (forum.php) 1967-05-31 1968-05-31

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4551991A (en) * 1984-02-22 1985-11-12 Hitachi, Ltd. Multi-effect absorption refrigerating machine
FR2572793A1 (fr) * 1984-11-05 1986-05-09 Carrier Corp Systeme de refrigeration/pompe a chaleur a absorption, a desorbeur-resorbeur, a effet variable
WO2025155735A1 (en) * 2024-01-19 2025-07-24 Advanced Liquid Cooling Technologies Inc. Integrated data center absorption system

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2283213A (en) * 1939-06-17 1942-05-19 Katzow Abram Refrigerating system
US3266266A (en) * 1963-08-02 1966-08-16 American Radiator & Standard Double effect absorption refrigeration machine
US3273350A (en) * 1964-09-14 1966-09-20 Robert S Taylor Refrigeration systems and methods of refrigeration
US3287928A (en) * 1964-04-14 1966-11-29 American Radiator & Standard Decrystallizer means for double effect absorption refrigeration system
US3316727A (en) * 1964-06-29 1967-05-02 Carrier Corp Absorption refrigeration systems

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2283213A (en) * 1939-06-17 1942-05-19 Katzow Abram Refrigerating system
US3266266A (en) * 1963-08-02 1966-08-16 American Radiator & Standard Double effect absorption refrigeration machine
US3287928A (en) * 1964-04-14 1966-11-29 American Radiator & Standard Decrystallizer means for double effect absorption refrigeration system
US3316727A (en) * 1964-06-29 1967-05-02 Carrier Corp Absorption refrigeration systems
US3273350A (en) * 1964-09-14 1966-09-20 Robert S Taylor Refrigeration systems and methods of refrigeration

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4551991A (en) * 1984-02-22 1985-11-12 Hitachi, Ltd. Multi-effect absorption refrigerating machine
FR2572793A1 (fr) * 1984-11-05 1986-05-09 Carrier Corp Systeme de refrigeration/pompe a chaleur a absorption, a desorbeur-resorbeur, a effet variable
WO2025155735A1 (en) * 2024-01-19 2025-07-24 Advanced Liquid Cooling Technologies Inc. Integrated data center absorption system

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GB1205989A (en) 1970-09-23
FR1563600A (forum.php) 1969-04-11

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