EP0028343A2 - Method and heat exchanger for directing a heating medium into a sorption heat pump - Google Patents
Method and heat exchanger for directing a heating medium into a sorption heat pump Download PDFInfo
- 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
- heating medium
- heat
- heat exchanger
- 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- Withdrawn
Links
- 238000010438 heat treatment Methods 0.000 title claims abstract description 45
- 238000000034 method Methods 0.000 title claims abstract description 21
- 238000001179 sorption measurement Methods 0.000 title claims abstract description 15
- 239000006096 absorbing agent Substances 0.000 claims abstract description 41
- 239000003507 refrigerant Substances 0.000 claims abstract description 11
- 239000002904 solvent Substances 0.000 claims abstract description 6
- 239000000463 material Substances 0.000 abstract description 2
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 16
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 12
- 229910021529 ammonia Inorganic materials 0.000 description 8
- 239000008236 heating water Substances 0.000 description 7
- 239000003990 capacitor Substances 0.000 description 6
- 150000003839 salts Chemical class 0.000 description 6
- 239000000126 substance Substances 0.000 description 6
- 238000010521 absorption reaction Methods 0.000 description 4
- OKKJLVBELUTLKV-UHFFFAOYSA-N Methanol Chemical compound OC OKKJLVBELUTLKV-UHFFFAOYSA-N 0.000 description 3
- 150000001298 alcohols Chemical class 0.000 description 3
- 150000001412 amines Chemical class 0.000 description 3
- 230000007613 environmental effect Effects 0.000 description 3
- BAVYZALUXZFZLV-UHFFFAOYSA-N Methylamine Chemical compound NC BAVYZALUXZFZLV-UHFFFAOYSA-N 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- AMXOYNBUYSYVKV-UHFFFAOYSA-M lithium bromide Chemical compound [Li+].[Br-] AMXOYNBUYSYVKV-UHFFFAOYSA-M 0.000 description 2
- HSZCZNFXUDYRKD-UHFFFAOYSA-M lithium iodide Chemical compound [Li+].[I-] HSZCZNFXUDYRKD-UHFFFAOYSA-M 0.000 description 2
- VNDYJBBGRKZCSX-UHFFFAOYSA-L zinc bromide Chemical compound Br[Zn]Br VNDYJBBGRKZCSX-UHFFFAOYSA-L 0.000 description 2
- 230000009102 absorption Effects 0.000 description 1
- 239000003570 air Substances 0.000 description 1
- CDQSJQSWAWPGKG-UHFFFAOYSA-N butane-1,1-diol Chemical compound CCCC(O)O CDQSJQSWAWPGKG-UHFFFAOYSA-N 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 229940102001 zinc bromide Drugs 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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)
Abstract
Description
Die Erfindung betrifft Verfahren zur Gegenstrom-Führung des Heizmediums zu dem in einer Sorptionswärmepumpe im Kreislauf geführten Lösungs- und/oder Kältemittel und Wärmetauscher zur Durchführung der Verfahren.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.
Sorptionswärmepumpen der genannten Art, die oft als Absorptions- beziehungsweise Resorptionswärmepumpen bezeichnet werden, sind an sich bekannt. Im Gegensatz zu den ebenfalls bekannten Kompressionswärmepumpen haben sie bisher nur wenig Anwendung gefunden, da ihre Heizleistung geringer als die der Kompressionswärmepumpen ist.Sorption heat pumps of the type mentioned, which are often referred to as absorption or absorption heat pumps, are known per se. In contrast to the 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.
Bei den Sorptionswärmepumpen erfolgt die Abgabe der zu nutzenden Wärme am Absorber und Kondensator beziehungsweise Resorber. Bei den bisher bekannten Sorptionswärmepumpen strömt das Heizmedium, zum Beispiel Heizungswasser, durch je einen als Wärmetauscher ausgebildeten Absorber und Kondensator bzw. Resorber, wobei die Reihenfolge, in der die beiden Wärmetauscher vom Heizmedium durchströmt werden, unterschiedlich ist. Die Wärmetauscher dieser bekannten Sorptionswärmepumpen sind im allgemeinen als Rohrbündeltauscher ausgebildet.In the case of sorption heat pumps, the heat to be used is transferred to the absorber and condenser or resorber. In the previously known sorption heat pumps, the heating medium, for example heating water, flows through an absorber and a condenser or resorber each designed as a heat exchanger, the sequence in which the heating medium flows through the two heat exchangers being different. The heat exchangers of these known sorption heat pumps are generally designed as tube bundle exchangers.
Mit dieser bekannten Verfahrensweise und derartigen Wärmetauschern ist es nicht möglich, die verfügbaren Wärmemengen vollständig und optimal zu nutzen, die dem Lösungs-/oder Kältemittel, im folgenden Kreislaufmedium genannt, in Desorber und Verdampfer durch Beheizung sowie Umwelt-Wärme aus Luft oder Wasser zugeführt werden.With this known procedure and such heat exchangers, it is not possible to use the available amounts of heat completely and optimally, which are supplied to the solvent or refrigerant, hereinafter referred to as the circulating medium, in desorbers and evaporators by heating and environmental heat from air or water .
Die Betriebsbedingungen von Sorptionswärmepumpen können sehr unterschiedlich sein: Einerseits kann die gewünschte maximale Temperatur des mit ihrer Hilfe zu erwärmenden Heizmediums unterschiedlich sein, je nachdem ob dieses durch konventionelle Raum-Heizkörper oder ein Fußboden-Heizungssystem geführt wird oder ggf. zusätzlich oder allein zur Brauchwasser-Erwärmung dient. Andererseits kann die aus der Umgebung (Luft, Wasser, Erdboden) gewinnbare Wärme in unterschiedlicher Menge und mit verschiedenen Temperaturniveaus zur Verfügung stehen. - Die Maßnahmen zur Nutzung von Umweltwärme beim Betrieb von Sorptionswärmepumpen sind bekannt. Auf ihre Beschreibung wird verzichtet, da sie nicht Gegenstand dieser Erfindung sind.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.
Aufgabe der Erfindung ist es, gattungsgemäße Verfahren und Wärmetauscher zu deren Durchführung zu entwickeln, die bei allen Betriebsweisen eine optimale Nutzung der verfügbaren Wärmemengen ermöglichen und bei denen das Heizmedium auf eine möglichst hohe Temperatur erwärmt wird.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.
Diese Aufgabe wird durch die in den Ansprüchen 1 bis 7 angegebenen Maßnahmen gelöst.This object is achieved by the measures specified in claims 1 to 7.
Die erfindungsgemäßen Verfahrensweisen und die Ausbildung der Wärmetauscher zu deren Durchführung werden nachfolgend näher erläutert. - Der Aufbau und die Funktionsweise einer Sorptionswärmepumpe wird als bekannt vorausgesetzt und nicht mehr beschrieben. - Bei einer Sorptionswärmepumpe sind bekanntlich Absorber und Kondensator bzw. Resorber als Wärmetauscher ausgebildet und stellen so die Verbindungselemente zum Heizsystem dar. In den Wärmetauschern strömen üblicherweise das Kreislaufmedium und das Heizmedium im Gegenstrom zueinander.The procedures according to the invention and the design of the heat exchangers for carrying them out are explained in more detail below. - The structure and mode of operation of a sorption heat pump is assumed to be known and is no longer described. - In a sorption heat pump, it is known that the absorber and the condenser or resorber are designed as heat exchangers and thus represent the connecting elements to the heating system. The circulating medium and the heating medium usually flow in countercurrent to one another in the heat exchangers.
Die Temperaturen in diesen Anlagenteilen bzw. die Verdampfungs-, Kondensations- und Absorptionstemperaturen sind abhängig vom Lösungs- und/oder Kältemittel, das heißt vom verwendeten Stoffpaar, den Konzentrationen der Stoff - paar-Komponenten und den herrschenden Drücken, so daß abhängig von den Betriebsbedingungen entweder die maximale Temperatur im Absorber höher ist als die im Kondensator bzw. Resorber oder die maximale Temperatur im Kondensator bzw. Resorber höher ist als die im Absorber.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.
Bei Versuchen wurde festgestellt, daß es in den Fällen, bei denen im Kondensator bzw. Resorber höhere Temperaturen als im Absorber vorliegen - was meistens bei Verwendung des Stoffpaares Ammoniak/Wasser zutrifft - thermodynamisch am günstigsten ist, den Kältemitteldampf mit dem in den Heizkörpern abgekühlten Heizmedium am Kondensatoraustritt sehr weit herunterzukühlen, ebenso wie die reiche Lösung am Absorberaustritt, danach ggf. mit dem Heizmedium einen weiteren Teil des Kondensators und den übrigen Absorberteil zu kühlen und zum Schluß am Kondensator das Heizmedium auf die höchstmögliche Temperatur zu erwärmen.Experiments have shown that in cases where the condenser or resorber has higher temperatures than the absorber - which is usually the case when using the ammonia / water pair - thermodynamically the most favorable is the refrigerant vapor with the heating medium cooled in the radiators to cool down very far at the condenser outlet, as well as the rich solution at the absorber outlet, then, if necessary, to cool another part of the condenser and the remaining absorber part with the heating medium and finally to heat the heating medium to the highest possible temperature at the condenser.
Daher soll nach dem erfindungsgemäßen Verfahren entsprechend Anspruch 1 das Heizmedium, zum Beispiel Wasser, immer als erstes und letztes durch einen Kondensator- bzw. Resorber-Wärmetauscherbereich strömen. Dazwischen strömt es - je nach Anzahl der Tauscherbereiche - entweder durch einen Absorber-Tauscherbereich oder abwechselnd durch mehrere Absorber- und Kondensator- bzw. Resorber-Tauscherbereiche hintereinander.Therefore, according to the method according to the invention, the heating medium, for example water, 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.
Um bei möglichst allen vorkommenden Betriebsbedingungen eine optimale Wärmenutzung zu erreichen, ist es notwendig, von Fall zu Fall das am besten geeignete Stoffpaar, dessen Konzentrationen sowie die anzuwendenden bzw. zulässigen Drücke mit Hilfe der aus der Fachliteratur bekannten Daten auszuwählen.In order to achieve optimal heat utilization in as many operating conditions as possible, it is necessary to select the most suitable pair of substances, their concentrations and the pressures to be used or permitted using the data known from the specialist literature.
Als Stoffpaare kommen neben Ammoniak/Wasser hauptsächlich Salz/Wasser, Salz/Alkohole oder Salz/Amine zur Anwendung. Als Salze werden insbesondere Lithiumbromid oder Lithiumjodid/Zinkbromid, als Alkohole zum Beispiel Methanol oder Butandiol und als Amine zum Beispiel Methylamin verwendet.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.
Bei Verwendung der genannten Stoffpaare, bei denen Wasser, Alkohole oder Amine das Kältemittel bilden, tritt bei geringer Kältemittelkonzentration und entsprechender Festlegung der Drücke und wenn ein innerer Wärmetausch zwischen der reichen Lösung aus dem Absorber und dem Kältemitteldampf vor dem Kondensator stattfindet, die höchste Temperatur im Absorber im Eingangsbereich des Kältemittels auf. In diesem Bereich des Absorber-Wärmetauschers kann also das Heizwasser auf die höchstmögliche Temperatur erhitzt werden.When using the above-mentioned pairs of substances, in which water, alcohols or amines form the refrigerant, 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. In this area of the absorber heat exchanger, the heating water can be heated to the highest possible temperature.
Daher soll nach dem erfindungsgemäßen Verfahren entsprechend Anspruch 2 das Heizmedium mindestens vier getrennte Wärmetauscherbereiche durchströmen. Dabei tritt es zuerst in den Kondensatortauscherbereich ein und fließt dann abwechselnd je nach Anzahl der Tauscherbereiche zwischen Absorber und Kondensator. Das Heizmedium verläßt den Wärmetauscher aus dem Absorbertauscherbereich, in dem das Heizmedium auf seine höchste Tempertatur gebracht wird.Therefore, according to the inventive method according to claim 2, 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.
Zur Durchführung des erfindungsgemäßen Verfahrens ist es notwendig, die Absorber- und Kondensator- beziehungsweise Resorber-Wärmetauscher, die vom Heizmedium durchströmt werden, in mehrere Bereiche aufzuteilen. Die Anzahl der Wärmetauscherbereiche soll gemäß Anspruch 1 insgesamt nindestens drei betragen: Zwei Bereiche für den Kondensator bzw. Resorber und ein Bereich für den Absorber. Nach oben 1in ist die Zahl der Tauscherbereiche nicht begrenzt, da sie von der Anlagengröße bzw. -leistung abhängt. In Anbetracht ies sich mit steigender Anzahl der Bereiche stark vergrößernden apparativen Aufwands, wird eine Zahl von ingesamt fünf oder sieben Bereichen als optimal angesehen. Zur Durchführung des Verfahrens nach Anspruch 2 ist eine Aufteilung des Absorbers und Kondensators bzw. Resorbers in mindestens vier Tauscherbereiche nötig, und zwar mindestens je zwei Absorber- und zwei Kondensatortauscherbereiche. Hier ist eine Zahl von insgesamt vier oder sechs Bereichen als optimal anzusehen. Die Länge bzw. die Abmessungen der einzelnen Bereiche hängt von der AnlagengröBe ab. Jeder Absorber-Wärmetauscherbereich ist jedoch mindestens gleich groß, vorzugsweise größer, als der größte Kondensator-Wärmetauscherbereich.To carry out the method according to the invention, it is necessary to divide the absorber and condenser or resorber heat exchangers through which the heating medium flows into several areas. 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. To carry out the method according to claim 2, 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. Here, a total of four or six areas can be regarded as optimal. The length or the dimensions of the individual areas depends on the size of the system. However, each absorber heat exchanger area is at least the same size, preferably larger than the largest condenser heat exchanger area.
Bei dem häufig verwendeten Stoffpaar Ammoniak/Wasser liegt die höchste Temperatur im Kondensator bzw. Resorber praktisch immer oberhalb der höchsten Temperatur im Ab-sorber, das heißt die höchstmögliche Temperatur würde das Heizwasser unter der Voraussetzung des Gegenstromprinzips im letzten Kondensator-Tauscherbereich - dort, wo der Ammoniak-Dampf in den Kondensator eintritt -, erreichen. Bei Anwendung des Stoffpaares Ammoniak/Wasser als Kreislaufmedium ist zwischen Austreiber und Kondensator jedoch üblicherweise ein Dephlegmator angeordnet, der zur Kondensation und Rückführung (in den Austreiber) des mit dem Ammoniak-Dampf verdampften Wassers dient. Die Temperatur der Dämpfe im Dephlegmator ist jedoch immer höher als die Eintrittstemperatur des Ammoniak-Dampfes in den Kondensator. Eine vorteilhafte weitere Ausbildung des erfindungsgemäßen Verfahrens nach Anspruch 2 besteht darin, daß das Heizmedium als letzte Stufe (vor der Abführung zum Verbraucher) in Wärmetausch mit dem Dephlegmator (soweit dieser nicht durch inneren Wärmetausch gekühlt wird) gebracht wird, wo es seine höchste Temperatur annimmt. Dadurch, daß der Dephlegmator-Wärmetauscher zur Erhitzung des Heizmediums benutzt wird, wird gleichzeitig die Temperatur des vom Dephlegmator zum Kondensator strömenden Ammoniak-Dampfes gesenkt, so daß die höchste Temperatur im Kondensator nicht höher, sondern vorzugsweise niedriger liegt als die höchste Absorber-Temperatur. - Bei Salzen als Bestandteil des Stoffpaares ist ein Dephlegmator nicht notwendig, da Salze bei den in Sorptionswärmepumpen herrschenden Drücken und Temperaturen nicht verdampfen können.In the case of the frequently used ammonia / water pair, 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. When using the ammonia / water pair of substances as the circulating medium, however, 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. However, 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.
Die Art des verwendeten Wärmetauschers hängt vom Heizmedium ab. Ist das Heizmedium eine Flüssigkeit, sind erfindungsgemäß Koaxialrohre vorteilhaft. Um die Wärmeaustauschfläche zu vergrößern, können auch statt des üblicherweise verwendeten einen Innenrohres zwei oder mehrere Innenrohre vorgesehen werden. Wird Luft als Heizmedium verwendet, sind zum Beispiel Rippenrohre zweckmäßiger.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 und 2 stellen schematisch die beispielsweise Anordnung und Ausführung der Rohre des Kondensator- und Absorber-Wärmetauschers einer Absorptionswärmepumpe entsprechend dem Verfahren nach Anspruch 1 dar.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.
Die Wärmetauscher werden mit Wasser als Heizmedium betrieben und sind aus-Koaxialrohren aufgebaut. Diese sind platzsparend in drei konzentrische Ringe unterschiedlichen Durchmessers gebogen und in mehreren Lagen übereinander angeordnet.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.
Das Kreislaufmedium fließt im inneren Rohr, das im äußeren Rohr befindliche Heizungswasser fließt in Gegenrichtung dazu. Die Außenrohre der Kondensator- und Absorber-Wärmetauscher sind erfindungsgemäß in mehrere voneinander getrennte Bereiche aufgeteilt, und zwar im vorliegenden Beispiel der Kondensatorteil in drei und der Absorber-Teil in zwei Bereiche.The circulating medium flows in the inner pipe, the heating water in the outer pipe flows in the opposite direction. According to the invention, 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.
Die vier übereinanderliegenden äußersten Ringe und die fünf Ringe mittleren Durchmessers bilden den Absorber-Wärmetauscher, der, wie schon beschrieben, heizwasserseitig in zwei Bereiche A1 und A2 - einmal zwei und einmal sieben Ringe - unterteilt ist. Die übrigen vier Ringe mit dem kleinsten Durchmesser bilden die drei Kondensator-Wärmetauscherbereiche; der unterste Ring ist als Wärmetauscherbereich K1 abgeteilt, die darüber liegenden zwei Ringe als Bereich K2. Der darüberliegende oberste innere Ring bildet den Wärmetauscherbereich K3.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 dient zur Veranschaulichung des Heizwasserkreislaufes im Außenrohr. Die Reihenfolge, in der die Rohre vom Heizmedium durchströmt werden, ist durch die alphabetische Reihenfolge der kleinen Buchstaben gegeben.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.
Bei dem vorliegenden Ausführungsbeispiel strömt das noch unerwärmte bzw. abgekühlte Heizwasser erfindungsgemäß als erstes durch den Kondensator-Wärmetauscherbereich K1 (a), dann durch den Absorber-Wärmetauscherbereich A1 (b, c), danach durch einen weiteren Kondensator-Wärmetauscherbereich K2 (d, e), durch den zweiten Absorber-Wärmetauscherbereich A2 (f bis 1), um zum Schluß aus dem letzten Kondensatorbereich K3 (m) auszutreten.In the present embodiment, 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).
In Fig. 2 ist dargestellt, wie das Kreislaufmedium durch Absorber und Kondensator fließt. Die Reihenfolge ist wie bei Fig. 1 durch die alphabetische Reihenfolge der kleinen Buchstaben gegeben. In die vier mit K bezeichneten Kondensator-Tauscherrohre tritt das Kreislaufmittel in den obersten Ring mit dem kleinsten Durchmesser ein (a), durchströmt die darunter liegenden drei Ringe (b, c, d) und verläßt den Kondensator-Tauscher.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. In the four condenser exchanger tubes labeled K, 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.
In den mit "A" bezeichneten Absorber-Wärmetauscher tritt das Kreislaufmedium in den obersten Ring mit dem größten Durchmesser (a) ein und durchströmt in der angegebenen Reihenfolge (a bis i) alle Tauscherrohre. In allen Innenrohren fließt das Kreislaufmedium immer im Gegenstrom zum Heizmedium.In the absorber heat exchanger labeled "A", 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.
Mit den neuen Verfahren und den Wärmetauschern zu deren Durchführung ist es erstmals möglich, die aus Heiz- und Umweltenergie bestehenden verfügbaren Wärmemengen vollständig und optimal zu nutzen, das heißt die Gesamtheizleistung wird erhöht. Diese Erhöhung betrug bei Versuchen etwa 10 %. Daraus resultiert eine Erhöhung der Heizziffer. Diese ist definiert als Verhältnis der erzielten Nutzwärme zur zugeführten Wärmemenge in Form von Brennstoff. Bei einer vergleichbaren bekannten Sorptions-Wärmepumpe beträgt die bei Versuchen festgestellte Heizziffer etwa 1,15. Diese konnte bei Anwendung der erfindungsgemäßen Verfahren und der neuen Wärmetauscher auf etwa.1,26 erhöht werden.With the new processes and the heat exchangers for their implementation, it is now possible for the first time to make full and optimal use of the available heat quantities from heating and environmental energy, i.e. 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.
Claims (7)
dadurch gekennzeichnet,
daß das Heizmedium wechselweise im Wärmeaustausch mit Teilen des Absorbers und des Kondensators bzw. Resorbers geführt wird derart,
daß das Heizmedium mindestens drei, vorzugsweise fünf getrennte Wärmeaustauschbereiche durchströmt, in deren erstem und letztem ein Wärmeaustausch mit dem Kondensator bzw. Resorber erfolgt, während in dem bzw. den dazwischenliegenden Wärmeaustauschbereich(en) der Wärmeaustausch allein mit dem Absorber bzw. bei mehr als drei Wärmeaustauschbereichen wechselweise mit Absorber- und Kondensator- bzw. Resorberzonen erfolgt.1. A method for countercurrent flow of the heating medium to the solvent and / or refrigerant circulated in a sorption heat pump,
characterized,
that the heating medium is alternately guided in heat exchange with parts of the absorber and the condenser or resorber,
that the heating medium flows through at least three, preferably five separate heat exchange areas, in the first and last of which there is a heat exchange with the condenser or resorber, while in the heat exchange area (s) in between, the heat exchange alone with the absorber or with more than three Heat exchange areas alternate with absorber and condenser or resorber zones.
dadurch gekennzeichnet,
daß das Heizmedium wechselweise im Wärmetausch
mit Teilen des Absorbers und des Kondensators bzw. Resorbers geführt wird, derart, daß das Heizmedium mindestens vier getrennte Wärmetauscherbereiche durchströmt, in deren erstem ein Wärmetausch mit dem Kondensator bzw. Resorber und in deren letztem ein Wärmetausch mit dem Absorber erfolgt.2. Method for countercurrent flow of the heating medium to the solvent and / or refrigerant circulated in a sorption heat pump,
characterized,
that the heating medium alternately in heat exchange
is performed with parts of the absorber and the condenser or resorber, such that the heating medium flows through at least four separate heat exchanger areas, in the first of which there is a heat exchange with the condenser or resorber and in the latter a heat exchange with the absorber.
dadurch gekennzeichnet,
daß das Heizmedium zusätzlich als letzte Stufe in Wärmeaustausch mit einem Dephlegmator gebracht wird.3. The method according to claim 2,
characterized,
that the heating medium is additionally brought into heat exchange with a dephlegmator as the last stage.
dadurch gekennzeichnet,
daß die Bereiche der Absorber- und Kondensator- bzw. Resorber-Wärmetauscher, die vom Heizmedium durchströmt werden, in insgesamt mindestens drei, vorzugsweise fünf oder sieben Abschnitte aufgeteilt sind, wobei der Kondensator-Wärmetauscher in mindestens zwei Wärmetauscherbereiche unterteilt ist.4. Heat exchanger for performing the method according to claim 1,
characterized,
that the areas of the absorber and condenser or resorber heat exchangers through which the heating medium flows are divided into a total of at least three, preferably five or seven sections, the condenser heat exchanger being subdivided into at least two heat exchanger areas.
dadurch gekennzeichnet,
daß der Absorber und der Kondensator bzw. Resorber in mindestens je zwei Tauscherbereiche unterteilt sind.5. Heat exchanger for performing the method according to claim 2 or 3,
characterized,
that the absorber and the condenser or resorber are divided into at least two exchanger areas.
daß jeder Absorber-Wärmetauscherbereich mindestens gleich groß, vorzugsweise größer als der größte Kondensator-Wärmetauscherbereich ist.6. Heat exchanger according to claim 4 or 5, characterized in
that each absorber heat exchanger area is at least the same size, preferably larger than the largest condenser heat exchanger area.
dadurch gekennzeichnet,
daß die Wärmetauscher aus Koaxialrohren gebildet werden, die in Ringe unterschiedlichen Durchmessers gebogen und in mehreren Lagen übereinander angeordnet sind.7. Heat exchanger according to claim 4 to 6
characterized,
that the heat exchangers are formed from coaxial tubes which are bent into rings of different diameters and are arranged one above the other in several layers.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2944654 | 1979-11-06 | ||
| DE19792944654 DE2944654A1 (en) | 1979-11-06 | 1979-11-06 | Counterflow heat exchanger system for heat pump - uses concentric tubes forming multiple heat exchange zones with absorber and condenser |
| DE19803010601 DE3010601A1 (en) | 1980-03-20 | 1980-03-20 | Counterflow heat exchanger system for heat pump - uses concentric tubes forming multiple heat exchange zones with absorber and condenser |
| DE3010601 | 1980-03-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0028343A2 true EP0028343A2 (en) | 1981-05-13 |
| EP0028343A3 EP0028343A3 (en) | 1981-05-27 |
Family
ID=25781840
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP80106362A Withdrawn EP0028343A3 (en) | 1979-11-06 | 1980-10-20 | Method and heat exchanger for directing a heating medium into a sorption heat pump |
Country Status (1)
| Country | Link |
|---|---|
| EP (1) | EP0028343A3 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2536513A1 (en) * | 1982-11-22 | 1984-05-25 | Gaz De France | IMPROVEMENTS TO A HEATING FACILITY EQUIPPED WITH AN ABSORPTION HEAT PUMP |
Citations (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR723901A (en) * | 1931-10-06 | 1932-04-18 | Automatic refrigeration unit with continuous action by absorption and with cold control device | |
| 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 (en) * | 1952-02-15 | 1954-02-25 | Methods and devices relating to absorption refrigeration machines | |
| DE1021389B (en) * | 1953-03-05 | 1957-12-27 | Eugen Bucher | Method and device for operating a continuously acting absorption refrigeration machine |
| DE1027216B (en) * | 1955-04-04 | 1958-04-03 | Borsig Ag | Method and device for operating a heat pump |
| 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 |
| US3466893A (en) * | 1968-04-05 | 1969-09-16 | Whirlpool Co | Absorber-condenser apparatus |
| US3509732A (en) * | 1965-10-20 | 1970-05-05 | Whirlpool Co | Absorption refrigeration system |
| 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 (en) * | 1974-01-22 | 1975-07-24 | Reinhard F Dr Hoehne | Reversible heat pump for room heating - ammonia condenses under high pressure at 75 deg. C |
| JPS5483159A (en) * | 1977-12-16 | 1979-07-03 | Hitachi Ltd | Absorbing type freezer |
| DE2854055A1 (en) * | 1978-12-14 | 1980-07-03 | Linde Ag | Heat transfer medium in absorption heating system - stops supply of refrigerating medium to absorber below set temp. |
-
1980
- 1980-10-20 EP EP80106362A patent/EP0028343A3/en not_active Withdrawn
Patent Citations (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR723901A (en) * | 1931-10-06 | 1932-04-18 | Automatic refrigeration unit with continuous action by absorption and with cold control device | |
| 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 (en) * | 1952-02-15 | 1954-02-25 | Methods and devices relating to absorption refrigeration machines | |
| DE1021389B (en) * | 1953-03-05 | 1957-12-27 | Eugen Bucher | Method and device for operating a continuously acting absorption refrigeration machine |
| DE1027216B (en) * | 1955-04-04 | 1958-04-03 | Borsig Ag | Method and device for operating a heat pump |
| 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 (en) * | 1974-01-22 | 1975-07-24 | Reinhard F Dr Hoehne | Reversible heat pump for room heating - ammonia condenses under high pressure at 75 deg. C |
| JPS5483159A (en) * | 1977-12-16 | 1979-07-03 | Hitachi Ltd | Absorbing type freezer |
| DE2854055A1 (en) * | 1978-12-14 | 1980-07-03 | Linde Ag | Heat transfer medium in absorption heating system - stops supply of refrigerating medium to absorber below set temp. |
Non-Patent Citations (1)
| Title |
|---|
| PATENTS ABSTRACTS OF JAPAN, Band 3, Nr. 108, 11. September 1979, Seite 76 M 72, Tokyo, JP, & JP-A-54 083 159 (HITACHI SEISAKUSHO KK). * |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2536513A1 (en) * | 1982-11-22 | 1984-05-25 | Gaz De France | IMPROVEMENTS TO A HEATING FACILITY EQUIPPED WITH AN ABSORPTION HEAT PUMP |
| EP0110763A1 (en) * | 1982-11-22 | 1984-06-13 | Gaz De France | Heating plant equipped with an absorption heat pump |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0028343A3 (en) | 1981-05-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| DE69315700T2 (en) | Absorption heat pump with direct heat exchange between the expeller of a second circuit and the absorber and condenser of a first circuit | |
| DE3739831C2 (en) | Method of absorbing heat by an absorption refrigerator and device for use as an absorption refrigerator | |
| DE2754626C2 (en) | Refrigeration system operating with an energy source at a relatively low temperature, in particular solar energy | |
| DE69230588T2 (en) | ABSORPTION CIRCUIT WITH TRIPLE-EFFECT DEVICE | |
| DE102007034710B4 (en) | Two-stage absorption cooler | |
| DE2900153C2 (en) | Spray generator for heating the solution in an absorption refrigeration system | |
| DE69107168T2 (en) | Air conditioner. | |
| DE69414970T2 (en) | Heat pipe and gas-liquid contact device with heat exchange, with heat pipes, and plate heat exchanger with gas-liquid contact | |
| DE69509870T2 (en) | HEAT EXCHANGE DEVICE AND METHOD FOR HEAT EXCHANGE BETWEEN OUTPUT AND ABSORBER AND APPLICATION THEREOF IN A HEAT PUMP | |
| DD284081A5 (en) | PROCESS FOR COOLING A FLUID | |
| DE3808257C1 (en) | ||
| EP0028343A2 (en) | Method and heat exchanger for directing a heating medium into a sorption heat pump | |
| DE69507944T2 (en) | A INTERMEDIATE LIQUID HEAT EXCHANGE DEVICE AND METHOD FOR EXCHANGING HEAT BETWEEN OUTPUTERS AND ABSORBERS AND USE THEREOF IN AN ABSORPTION HEAT PUMP | |
| DE2043459A1 (en) | Heat transfer tube - for steam condensation | |
| DE2839638A1 (en) | DRY COOLING SYSTEM FOR POWER PLANTS | |
| DE2219083C3 (en) | Absorption refrigeration system | |
| DE3541375A1 (en) | ABSORPTION COOLING SYSTEM | |
| DE2248124A1 (en) | DISTILLATION PLANT | |
| DE2944654A1 (en) | Counterflow heat exchanger system for heat pump - uses concentric tubes forming multiple heat exchange zones with absorber and condenser | |
| DE3101857A1 (en) | "Process for the regenerative use of the heat content of lean solutions" | |
| EP0130404A2 (en) | Multi-stage heat exchanger | |
| DE3010601A1 (en) | Counterflow heat exchanger system for heat pump - uses concentric tubes forming multiple heat exchange zones with absorber and condenser | |
| DE2507886A1 (en) | Exhaust steam precipitation in steam turbines - closed cycle for heat exchange fluid passes through condenser and cooling tower | |
| DE612962C (en) | Absorption refrigeration apparatus with inert gas | |
| DE625571C (en) | Process for the operation of absorption refrigerators |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
| AK | Designated contracting states |
Designated state(s): AT BE CH FR GB IT NL |
|
| AK | Designated contracting states |
Designated state(s): AT BE CH FR GB IT NL |
|
| 17P | Request for examination filed |
Effective date: 19811024 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
| 18D | Application deemed to be withdrawn |
Effective date: 19830901 |
|
| RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: MUEHLMANN, HEINRICHDR. RER. NAT. DIPL.-CHEM. Inventor name: SOMMERS, HANS, DIPL.-ING. |