EP0028343A2 - Procédé et échangeur de chaleur pour diriger un fluide de chauffage dans une pompe de chaleur à sorption - Google Patents

Procédé et échangeur de chaleur pour diriger un fluide de chauffage dans une pompe de chaleur à sorption Download PDF

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Publication number
EP0028343A2
EP0028343A2 EP80106362A EP80106362A EP0028343A2 EP 0028343 A2 EP0028343 A2 EP 0028343A2 EP 80106362 A EP80106362 A EP 80106362A EP 80106362 A EP80106362 A EP 80106362A EP 0028343 A2 EP0028343 A2 EP 0028343A2
Authority
EP
European Patent Office
Prior art keywords
condenser
absorber
heat
heating medium
resorber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP80106362A
Other languages
German (de)
English (en)
Other versions
EP0028343A3 (fr
Inventor
Hans Dipl.-Ing. Sommers
Heinrich Dr. rer. nat. Dipl.-Chem. Mühlmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
EOn Ruhrgas AG
Original Assignee
Ruhrgas AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19792944654 external-priority patent/DE2944654A1/de
Priority claimed from DE19803010601 external-priority patent/DE3010601A1/de
Application filed by Ruhrgas AG filed Critical Ruhrgas AG
Publication of EP0028343A2 publication Critical patent/EP0028343A2/fr
Publication of EP0028343A3 publication Critical patent/EP0028343A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/04—Heat pumps of the sorption type

Definitions

  • the invention relates to methods for countercurrent flow of the heating medium to the solvent and / or refrigerant circulated in a sorption heat pump and heat exchanger for carrying out the method.
  • Sorption heat pumps of the type mentioned which are often referred to as absorption or absorption heat pumps, are known per se.
  • compression heat pumps which are also known, they have so far found little use because their heating output is lower than that of the compression heat pumps.
  • the heat to be used is transferred to the absorber and condenser or resorber.
  • the heating medium for example heating water
  • the heat exchangers of these known sorption heat pumps are generally designed as tube bundle exchangers.
  • the operating conditions of sorption heat pumps can be very different: On the one hand, the desired maximum temperature of the heating medium to be heated with the help of it can vary, depending on whether this is led through conventional room radiators or a floor heating system or, if necessary, additionally or solely for domestic hot water. Heating serves. On the other hand, the heat that can be obtained from the environment (air, water, soil) can be available in different amounts and at different temperature levels. - The measures for the use of environmental heat when operating sorption heat pumps are known. Their description is omitted because they are not the subject of this invention.
  • the object of the invention is to develop generic methods and heat exchangers for their implementation, which enable optimal use of the available heat quantities in all operating modes and in which the heating medium is heated to the highest possible temperature.
  • the temperatures in these parts of the plant or the evaporation, condensation and absorption temperatures depend on the solvent and / or refrigerant, that is to say on the pair of substances used, the concentrations of the pair of substances and the prevailing pressures, so that they depend on the operating conditions either the maximum temperature in the absorber is higher than that in the capacitor or resorber or the maximum temperature in the capacitor or resorber is higher than that in the absorber.
  • the heating medium for example water
  • the heating medium should always flow first and last through a condenser or resorber heat exchanger area. In between, depending on the number of exchanger areas, it flows either through an absorber-exchanger area or alternately through several absorber and capacitor or resorber-exchanger areas in succession.
  • salt / water In addition to ammonia / water, mainly salt / water, salt / alcohols or salt / amines are used as material pairs.
  • Lithium bromide or lithium iodide / zinc bromide are used in particular as salts, for example methanol or butanediol as alcohols and methylamine as amines.
  • the highest temperature in the case of a low refrigerant concentration and appropriate determination of the pressures and if an internal heat exchange takes place between the rich solution from the absorber and the refrigerant vapor upstream of the condenser Absorber in the entrance area of the refrigerant.
  • the heating water can be heated to the highest possible temperature.
  • the heating medium should flow through at least four separate heat exchanger areas. It first enters the condenser exchanger area and then flows alternately between the absorber and the condenser, depending on the number of exchanger areas. The heating medium leaves the heat exchanger from the absorber exchange area, in which the heating medium is brought to its highest temperature.
  • the total number of heat exchanger areas should be according to claim 1 nindestens three are: Two areas for the capacitor or R esorber and a region for the absorber.
  • the number of exchanger areas is not limited upwards 1 in, since it depends on the size and performance of the system. In view of the fact that the expenditure on apparatus increases greatly with the increasing number of areas, a total of five or seven areas is regarded as optimal.
  • a division of the absorber and capacitor or resorber into at least four exchanger regions is necessary, namely at least two absorber and two capacitor exchanger regions.
  • each absorber heat exchanger area is at least the same size, preferably larger than the largest condenser heat exchanger area.
  • the highest temperature in the condenser or resorber is practically always above the highest temperature in the A b sorber, i.e. the highest possible temperature would be the heating water under the condition of the counterflow principle in the last condenser exchanger area - there, where the ammonia vapor enters the condenser.
  • a dephlegmator is usually arranged between the expeller and the condenser, which serves to condense and return (to the expeller) the water evaporated with the ammonia vapor.
  • the temperature of the vapors in the dephlegmator is always higher than the entry temperature of the ammonia vapor into the condenser.
  • An advantageous further embodiment of the inventive method according to claim 2 is that the heating medium as the last stage (before discharge to the consumer) in heat exchange with the dephlegmator (as far as the is not cooled by internal heat exchange) where it reaches its highest temperature. Because the dephlegmator heat exchanger is used to heat the heating medium, the temperature of the ammonia vapor flowing from the dephlegmator to the condenser is simultaneously lowered, so that the highest temperature in the condenser is not higher, but preferably lower than the highest absorber temperature. - A dephlegmator is not necessary for salts as part of the pair of substances, since salts cannot evaporate at the pressures and temperatures prevailing in sorption heat pumps.
  • the type of heat exchanger used depends on the heating medium. If the heating medium is a liquid, coaxial pipes are advantageous according to the invention. In order to increase the heat exchange surface, two or more inner tubes can also be provided instead of the one inner tube that is usually used. If air is used as the heating medium, finned tubes, for example, are more appropriate.
  • FIG 1 and 2 schematically illustrate the example arrangement and design of the tubes of the condenser and absorber heat exchanger of an absorption heat pump according to the method of claim 1.
  • the heat exchangers are operated with water as the heating medium and are made up of coaxial pipes. These are bent into three concentric rings of different diameters to save space and arranged in several layers one above the other.
  • the circulating medium flows in the inner pipe, the heating water in the outer pipe flows in the opposite direction.
  • the outer tubes of the condenser and absorber heat exchangers are divided into several separate areas, specifically the condenser part in three and the absorber part in the present example in two areas.
  • the four superimposed outer rings and the five rings of medium diameter form the absorber heat exchanger, which, as already described, is divided into two areas A1 and A2 on the heating water side - once two and once seven rings.
  • the remaining four rings with the smallest diameter form the three condenser heat exchanger areas; the lowest ring is divided as the heat exchanger area K1, the two rings above it as area K2.
  • the uppermost inner ring forms the heat exchanger area K3.
  • Fig. 1 serves to illustrate the heating water circuit in the outer tube.
  • the order in which the heating medium flows through the pipes is given by the alphabetical order of the small letters.
  • the still unheated or cooled heating water flows according to the invention first through the condenser heat exchanger area K1 (a), then through the absorber heat exchanger area A1 (b, c), and then through a further condenser heat exchanger area K2 (d, e ), through the second absorber heat exchanger area A2 (f to 1) to finally exit the last condenser area K3 (m).
  • FIG. 2 shows how the circulating medium flows through the absorber and the condenser.
  • the order is given as in Fig. 1 by the alphabetical order of the small letters.
  • the circulating agent enters the uppermost ring with the smallest diameter (a), flows through the three rings below (b, c, d) and leaves the condenser exchanger.
  • the circulating medium enters the uppermost ring with the largest diameter (a) and flows through all exchanger tubes in the order given (a to i).
  • the circulating medium always flows in countercurrent to the heating medium in all inner pipes.
  • the total heating output is increased. This increase was about 10% in tests. This results in an increase in the heating rate. This is defined as the ratio of the useful heat achieved to the amount of heat supplied in the form of fuel. In the case of a comparable known sorption heat pump, the heating rate determined in tests is approximately 1.15. This could be increased to approximately 1.26 using the methods according to the invention and the new heat exchangers.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)
EP80106362A 1979-11-06 1980-10-20 Procédé et échangeur de chaleur pour diriger un fluide de chauffage dans une pompe de chaleur à sorption Withdrawn EP0028343A3 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19792944654 DE2944654A1 (de) 1979-11-06 1979-11-06 Verfahren und waermetauscher zur fuehrung des heizmediums in einer sorptionswaermepumpe
DE2944654 1979-11-06
DE3010601 1980-03-20
DE19803010601 DE3010601A1 (de) 1980-03-20 1980-03-20 Verfahren und waermetauscher zur fuehrung des heizmediums in einer sorptionswaermepumpe

Publications (2)

Publication Number Publication Date
EP0028343A2 true EP0028343A2 (fr) 1981-05-13
EP0028343A3 EP0028343A3 (fr) 1981-05-27

Family

ID=25781840

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80106362A Withdrawn EP0028343A3 (fr) 1979-11-06 1980-10-20 Procédé et échangeur de chaleur pour diriger un fluide de chauffage dans une pompe de chaleur à sorption

Country Status (1)

Country Link
EP (1) EP0028343A3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2536513A1 (fr) * 1982-11-22 1984-05-25 Gaz De France Perfectionnements a une installation de chauffage equipee d'une pompe a chaleur a absorption

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR723901A (fr) * 1931-10-06 1932-04-18 Groupe frigorifique automatique à action continue par absorption et à dispositif de contrôle du froid
US2003310A (en) * 1932-06-04 1935-06-04 Standard Oil Co Refrigeration
US2112537A (en) * 1935-11-23 1938-03-29 Servel Inc Refrigeration
US2212869A (en) * 1938-09-27 1940-08-27 Herbert W Prafcke Reversible heating and cooling means and method
US2552071A (en) * 1947-09-11 1951-05-08 Mills Ind Inc Absorption refrigeration apparatus
FR1056314A (fr) * 1952-02-15 1954-02-25 Procédé et dispositifs concernant les machines frigorifiques à absorption
DE1021389B (de) * 1953-03-05 1957-12-27 Eugen Bucher Verfahren und Vorrichtung zum Betrieb einer kontinuierlich wirkenden Absorptionskaeltemaschine
DE1027216B (de) * 1955-04-04 1958-04-03 Borsig Ag Verfahren und Vorrichtung zum Betrieb einer Waermepumpe
US3041843A (en) * 1958-09-08 1962-07-03 Nat Tank Co Absorption type refrigeration system
US3273350A (en) * 1964-09-14 1966-09-20 Robert S Taylor Refrigeration systems and methods of refrigeration
US3509732A (en) * 1965-10-20 1970-05-05 Whirlpool Co Absorption refrigeration system
US3466893A (en) * 1968-04-05 1969-09-16 Whirlpool Co Absorber-condenser apparatus
US3638452A (en) * 1969-10-20 1972-02-01 Whirlpool Co Series water-cooling circuit for gas heat pump
US3828575A (en) * 1973-04-13 1974-08-13 Columbia Gas Syst Service Corp Compact heating and cooling system
DE2402777A1 (de) * 1974-01-22 1975-07-24 Reinhard F Dr Hoehne Raumwaermepumpe
JPS6025709B2 (ja) * 1977-12-16 1985-06-19 株式会社日立製作所 吸収式冷凍機
DE2854055A1 (de) * 1978-12-14 1980-07-03 Linde Ag Verfahren zum erhitzen eines waermetraegers mit einer absorptionswaermepumpe

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2536513A1 (fr) * 1982-11-22 1984-05-25 Gaz De France Perfectionnements a une installation de chauffage equipee d'une pompe a chaleur a absorption
EP0110763A1 (fr) * 1982-11-22 1984-06-13 Gaz De France Perfectionnements à une installation de chauffage équipée d'une pompe à chaleur à absorption

Also Published As

Publication number Publication date
EP0028343A3 (fr) 1981-05-27

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Inventor name: MUEHLMANN, HEINRICHDR. RER. NAT. DIPL.-CHEM.

Inventor name: SOMMERS, HANS, DIPL.-ING.