EP0152931A2 - Procédé pour actionner une installation de chauffage à générateur-pompe de chaleur d'absorption pour le chauffage des locaux, la préparation d'eau chaude et pareil et installation de chauffage générateur-pompe de chaleur d'absorption - Google Patents

Procédé pour actionner une installation de chauffage à générateur-pompe de chaleur d'absorption pour le chauffage des locaux, la préparation d'eau chaude et pareil et installation de chauffage générateur-pompe de chaleur d'absorption Download PDF

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Publication number
EP0152931A2
EP0152931A2 EP85101699A EP85101699A EP0152931A2 EP 0152931 A2 EP0152931 A2 EP 0152931A2 EP 85101699 A EP85101699 A EP 85101699A EP 85101699 A EP85101699 A EP 85101699A EP 0152931 A2 EP0152931 A2 EP 0152931A2
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EP
European Patent Office
Prior art keywords
heating
absorber
generator
heat
temperature
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.)
Granted
Application number
EP85101699A
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German (de)
English (en)
Other versions
EP0152931B1 (fr
EP0152931A3 (en
Inventor
Karl Friedrich Dr.-Ing. Prof. Knoche
Dieter Stehmeier
Heinz-Bernd Grabenhenrich
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.)
Knoche Karl-Friedrich Prof Dr-Ing
Original Assignee
Knoche Karl-Friedrich Prof Dr-Ing
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Application filed by Knoche Karl-Friedrich Prof Dr-Ing filed Critical Knoche Karl-Friedrich Prof Dr-Ing
Priority to AT85101699T priority Critical patent/ATE58225T1/de
Publication of EP0152931A2 publication Critical patent/EP0152931A2/fr
Publication of EP0152931A3 publication Critical patent/EP0152931A3/de
Application granted granted Critical
Publication of EP0152931B1 publication Critical patent/EP0152931B1/fr
Anticipated expiration legal-status Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/006—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the sorption type system

Definitions

  • the invention relates to a method for operating a generator absorption heat pump heating system and such a heating system for space heating, water heating, and. Like. Up to a heating power of about 20 kW according to the preamble of claims 1 and 3.
  • the object of the invention is to reduce the number of apparatuses and, if possible without the need for vulnerable, maintenance-consuming and energy-consuming components or units.
  • the invention provides the method for operating a generator absorption heat pump heating system characterized in claim 1 and the generator absorption heat pump heating system characterized in claim 4.
  • Embodiments of the invention are characterized in the subclaims.
  • the invention enables heating energy to be provided with a minimal number of apparatuses and without a solution pump.
  • the disadvantage of periodically operating absorption systems which is that large parts of the system and the working solution consisting of solvent (s) and refrigerant (s) must be heated and cooled intermittently, thereby avoiding expulsion and absorption on the one hand and evaporation and condensation on the other hand, in separate apparatus run so that the greater part of the overall system remains constantly in the range of the useful temperature level and thus the heat losses through insulation can be kept well low.
  • the apparatus volumes and heat exchange surfaces are comparatively small, operation takes place at widely differing pressure levels due to a periodic change in the operating phase expulsion and absorption. In contrast to continuously operating absorption heat pumps, the operating phases expulsion with condensation and evaporation with absorption take place at different times.
  • the heating system according to the invention benefits during the total operating time, because either useful heat is given off as condensation heat in the condenser or useful heat is given off as absorption heat in the absorber to the heating water to be heated.
  • the condenser, a container below the condenser or the evaporator can be designed as a refrigerant store, so that all part-load operating points are then possible at sliding working temperatures with optimal heat coupling from the environment (low-temperature heat).
  • the heating output of the system is adjusted to the heat demand via the ratio generator (burner) operating time to evaporator (absorber) operating time, whereby it is advisable to adhere to certain minimum runtimes.
  • the exemplary embodiment describes a generator absorption heat pump for the heating supply of buildings with direct heating of the expeller or generator with high temperature heat, which is generated by a burner, and the evaporator with the surroundings of extracted low temperature heat, e.g. is brought up with a fan.
  • a generator 1 (expeller) which is bi-heated directly by means of a burner, the exhaust gas cooler 2 integrated with this, a hot water-cooled condenser 3, a hot water-cooled absorber 4 and an evaporator 5 with direct heat coupling from a low-temperature heat source, namely, for example the outside air.
  • Generator 1 and absorber 4 form a communicatively connected system which is filled with a suitable working fluid solution (refrigerant and solvent, eg CH 3 0HlH 2 0-LiBr), the majority of the working fluid solution being accommodated in the absorber 4.
  • a suitable working fluid solution eg CH 3 0HlH 2 0-LiBr
  • the generator 1 is equipped with a burner, e.g. B. an oil or gas burner, heated directly. Its heat exchanger, through which the working fluid flows from bottom to top, has a small volume, which is why the evaporation of the more volatile component (s) (refrigerant) starts after a very short time, for example after half a minute.
  • the communicating connection of the heat exchanger of the generator 1 with the absorber 4 takes place via a low-lying connection line 10 for the incoming rich solution and an elevated connection line 11 for the outflowing poor solution.
  • the formation of vapor bubbles in the vertical boiler tubes of the heat exchanger of the generator 1, which is thus designed as a thermosiphon, sets in motion a natural circulation of the refrigerant-rich solution between the generator 1 and the absorber 4, which ensures a sufficiently high heat and material exchange in the generator 1.
  • the refrigerant vapor itself is deposited in the higher-lying condenser 3 and stored or throttled into the evaporator 5 for later evaporation.
  • the upper end of the heat exchanger of the generator 1 is connected to the vapor space of the condenser 3 by a connecting line 12.
  • the condensation heat released when the refrigerant vapor is precipitated is given off as useful heat to a heating water flow that is to be heated and returned by a heating system, which is then passed through passes through the exhaust gas cooler 2.
  • the exhaust gas cooler which is arranged in the upper part of the generator, uses the remaining exhaust gas heat that has not been transferred to the heat exchanger of the generator 1 up to almost the useful temperature.
  • the liquefied refrigerant is first stored in the lower part of the condenser 3, in a refrigerant store or directly in the evaporator 5 for later evaporation.
  • the condenser 3 is connected to the heat exchanger of the evaporator 5 through a condensate line 13 with a built-in shut-off valve 14.
  • the vapor space of the heat exchanger of the evaporator 5 is connected to a connecting line 15 with a built-in one-way valve 16 with an overhead steam connection of the absorber 4.
  • the one-way valve 16 can be a non-return valve, which only allows the steam to pass from the evaporator 5 to the absorber 4 and also prevents the working agent solution from overflowing from the absorber 4 into the evaporator 5.
  • the absorber 4 is connected to the lower part of the condenser 3 by means of a connecting line 17 in order to allow condensate to pass directly from the condenser 3 into the absorber 4 in direct or continuous heating mode, that is to say when the condensate store or evaporator is completely full.
  • the return water flowing back from a heating system can be conveyed with the usual heating water pump 20 via a line 21 to the heat exchanger of the condenser 3 and via a line 22 to the heat exchanger of the absorber 4.
  • the heating water emerging from the condenser 3 passes via a line 23 to the exhaust gas cooler 2 and a line 24 to a changeover valve 25 and, in the position shown in FIG. 1, into the heating water supply line 26
  • Absorber operation FIG. 2
  • the heating water now emerging from the absorber 4 passes via a line 27 directly to the changeover valve 25 and, in the position shown in FIG. 2, into the flow line 26.
  • the one-way valve 14 in the line 13 between the condenser 3 and the evaporator 5, which can be designed as a float valve, ensures that the refrigerant reservoir of the condenser is filled to the maximum permissible level 3 or the evaporator that the condensate still accumulating in the condenser 3 runs back directly into the absorber 4.
  • the working fluid solution serves as a pure heat transfer fluid and continuous heating operation (boiler operation), as shown in FIG. 3, with the maximum nominal heating output is possible.
  • the generator-absorption heat pump heating system which could also be called a boiler with a periodically acting absorber part, is therefore a monovaltent heating system, which covers the maximum heating requirements of the building without any additional heating device.
  • the generator operation is stopped, which means that the burner is switched off when the rising flow or return temperature of the heating system signals that there is no further heat requirement. This can be done with a simple heating water thermostat or with a temperature sensor in the solution.
  • the generator operation automatically switches to the continuous heating mode according to FIG. 3, which can be continued for as long as desired. If heat demand is signaled again after the burner has been switched off, the absorber operation is initiated automatically by reversing the changeover valve 25, because the solution temperature now drops due to the heat being withdrawn by the heating water and the solution thus becomes absorbable and the absorption process can thus begin.
  • the absorber operation is as shown in FIG. 2 and in which the System can pass after the burner is switched off, characterized by low pressure.
  • the changeover valve 25 By switching the changeover valve 25, the heating water flow from the condenser 3 and exhaust gas cooler 2 is directed to the heat exchanger of the absorber 4 and thereby the vapor pressure of the solvent is reduced by heat extraction and associated cooling below the vapor pressure of the refrigerant (mixture) in the evaporator, so that evaporation the same is made possible at low temperatures.
  • a device for example a fan, for transporting the low-temperature heat carrier, that is to say the air, is put into operation.
  • the fan can be switched on via a temperature difference sensor.
  • the cold steam from the evaporator 5 passes through the one-way valve 16 in the form of a non-return flap in the connecting line 15 to the absorber 4 and is absorbed in it above the useful temperature level, see FIG. 2.
  • Outside air, exhaust air, groundwater, running water, absorber roof, etc. come as a low-temperature heat source. in question.
  • the heat of absorption generated during absorption is now fed to the heating system via the heat exchanger of the absorber 4, through which the heating water now flows.
  • Numerous measures can be provided in the absorber 4 itself in order to optimally design the heat and mass exchange and to utilize the solvent until its initial concentration is reached.
  • the minimum required temperature increase in absorber or heat pump operation can be set by the refrigerant concentration of the filled solution within the limits specified by the material system. But beyond that, the Abspei - insurance a certain amount of refrigerant evaporation at sliding, thus dependent on the necessary temperature elevation, absorber temperature can be achieved. In this way there is any difference between the outside temperature and the heating water temperature maximum utilization of the degassing range of the working material system and thus maximum use of low temperature heat possible.
  • refrigerant mixtures e.g. water and methanol
  • the lower-boiling component remains partially stored at low outside temperatures, e.g. 0 ° C, while at higher outside temperatures, e.g. 12 ° C, their advantageous thermodynamic properties come into play.
  • the continuous heating operation of the heating system with nominal heating output described with reference to Fig. 3 is possible if the condensate accumulated during the expulsion is returned directly to the absorber 4 .
  • the working fluid solution which serves as heat transfer fluid in this operating phase, gives off the heating energy via the condenser 3 to the heating water.
  • This periodically acting absorption heat pump thus represents a full-fledged heating system, which can provide both the base load and the peak load of the heating demand.
  • the thermostat switches the burner out of operation again.
  • the heating water flow is then switched over by means of the switching valve 25 to the heat exchanger of the absorber 4, when a renewed heat requirement is reported by falling below the predetermined heating water temperature.
  • the absorption phase can be continued until the temperature of the heating water is no longer sufficient and the heating water temperature drops below a predetermined low heating water temperature, triggering the burner to start again.
  • the heating capacity of the system is a function of the heat requirement thus on the ratio of the burner running time (generator - operation time) to the absorber operating time adjusted continuously. In contrast to continuous systems, this results in particularly good heat conditions in part-load operation, because with increasing outside temperatures, the possible absorption of refrigerant vapor in the working fluid solution increases.
  • the centerpiece of the directly heated generator 1 is a vertically arranged, cross-finned finned tube bundle, the finned tubes of which end in the lower part in an inlet distributor which is located in the immediate vicinity of the heating device (gas burner, oil burner or the like).
  • the pipes open into a vapor-liquid separator, which has the task of separating the boiled-out solution from the refrigerant that is drawn off.
  • a special, asymmetrical arrangement of baffles between the finned tubes ensures that the hot fuel gases are evenly applied to the tubes up to their upper end that the exhaust gas has largely cooled down and leaves the generator or expeller.
  • the head of the generator is additionally designed as an exhaust gas cooler 2, so that the fuel can be used up to the calorific value.
  • the vertical arrangement of the pipes with the horizontal guidance of the fuel gases along the fins, together with the solution delivery in the pipes caused by the vapor bubbles, ensures highly efficient heat or material exchange.
  • the tubes are roughened on the inside to promote the formation of vapor bubbles.
  • the absorber 4 is designed as a bubble absorber, i.e. the refrigerant vapor is introduced into the absorptive solution in such a way that thorough mixing thereof is achieved and concentration differences in this apparatus remain small during the absorption phase.
  • Other measures to improve heat and material exchange include the use of e.g. by milling profiled tube bundle heat exchanger to achieve an increase in surface area, weight saving and the generation of turbulence in the solution, the installation of a circulation device, with the aid of which spray solution is collected and fed again at the bottom of the container, so that a natural circulation of the absorber operation Solution is guaranteed.
  • This arrangement prevents mixing of the solution in the generator phase, so that a largely constant degassing width can be achieved on the generator 1 during the entire expulsion time.
  • Another advantage is that only a small amount of solution has to be heated for a short operation of the generator 1.
  • the condenser 3 is designed as a spiral tube condenser, a drainage channel for the condensate being provided at the bottom of the cylindrical jacket.
  • the apparatus itself is installed in such a way that the condensate drainage is made possible by gravity.
  • the outside air evaporator 5 can be a flooded finned tube bundle (refrigerant in the tubes), in which a special distributor device ensures that the condensate is applied evenly over all tubes. This is achieved with the help of a distributor trough with overflow hole attached to the side of each finned tube row, which doses the amount of refrigerant per row.
  • the container wall, on which the steam outlet openings of the pipes converge, is also inclined towards the vertical so that refrigerant from the upper rows, which splashes over during evaporation, flows back to the lower rows.
  • the evaporator can also be operated as a dry evaporator if the supply line between a condensate store 3 and evaporator 5 is equipped with a distribution device for the finned tubes and an automatic control element for metering the required amount of refrigerant.
  • the connecting line 15 between the evaporator 5 and the absorber 4 is equipped with an independently acting non-return valve 16, which has the task of preventing the condensation of refrigerant vapor in the evaporator during generator operation and also of avoiding an overflow of solution into the evaporator.
  • the steam line 12 between the generator (expeller) 1 and the condenser 2 is kinked several times in order to avoid over-splashing of solution into the condenser 3 when the generator is operating violently.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Sorption Type Refrigeration Machines (AREA)
EP85101699A 1984-02-17 1985-02-15 Procédé pour actionner une installation de chauffage à générateur-pompe de chaleur d'absorption pour le chauffage des locaux, la préparation d'eau chaude et pareil et installation de chauffage générateur-pompe de chaleur d'absorption Expired - Lifetime EP0152931B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85101699T ATE58225T1 (de) 1984-02-17 1985-02-15 Verfahren zum betreiben einer generatorabsorptionsw|rmepumpen-heizanlage fuer die raumheizung, warmwasserbereitung und dergl. und generator-absorptionswaermepumpen-heizanlage.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3405800A DE3405800C2 (de) 1984-02-17 1984-02-17 Verfahren zum Betreiben einer Generator-Absorptionswärmepumpen-Heizanlage für die Raumheizung und/oder Warmwasserbereitung und Generator-Absorptionswärmepumpen-Heizanlage
DE3405800 1984-02-17

Publications (3)

Publication Number Publication Date
EP0152931A2 true EP0152931A2 (fr) 1985-08-28
EP0152931A3 EP0152931A3 (en) 1987-05-20
EP0152931B1 EP0152931B1 (fr) 1990-11-07

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EP85101699A Expired - Lifetime EP0152931B1 (fr) 1984-02-17 1985-02-15 Procédé pour actionner une installation de chauffage à générateur-pompe de chaleur d'absorption pour le chauffage des locaux, la préparation d'eau chaude et pareil et installation de chauffage générateur-pompe de chaleur d'absorption

Country Status (3)

Country Link
EP (1) EP0152931B1 (fr)
AT (1) ATE58225T1 (fr)
DE (2) DE3405800C2 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995025934A1 (fr) * 1994-03-21 1995-09-28 Cryotherm Engineering Limited Machine de chauffage/refroidissement a absorption
WO2010078957A2 (fr) 2008-12-19 2010-07-15 Invensor Gmbh Élément limiteur de pression permettant de diviser le débit volumique de condensation dans des machines à sorption
WO2009119695A3 (fr) * 2008-03-27 2012-12-20 Honda Motor Co., Ltd. Unité de pompe à chaleur à absorption
IT201800007258A1 (it) * 2018-07-17 2020-01-17 Macchina di riscaldamento ad attivazione termica
EP3842710A1 (fr) * 2019-12-23 2021-06-30 Technische Universität Berlin Procédé de fonctionnement d'une installation de sorption et installation de sorption

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10154032B4 (de) * 2001-11-02 2005-06-23 Bbt Thermotechnik Gmbh Diffusionsabsorptionsanlage
DE102013222658A1 (de) * 2013-11-07 2015-05-07 Robert Bosch Gmbh Absorptionswärmepumpe

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE427278C (de) * 1922-06-17 1926-03-29 Siemens Schuckertwerke G M B H Absorptionsmaschine
DE842352C (de) * 1945-06-13 1952-06-26 Electrolux Ab Absorptionskaelteapparat
DE2748415C2 (de) * 1977-10-28 1986-10-09 Naamloze Vennootschap Nederlandse Gasunie, Groningen Heizverfahren und bimodales Heizsystem zum Heizen von Gebäuden
DE2758773C2 (de) * 1977-12-29 1981-12-17 Ask August Schneider Gmbh & Co Kg, 8650 Kulmbach Bivalente Heizanlage
DE2938203A1 (de) * 1979-09-21 1981-04-02 Knoche, Karl-Friedrich, Prof. Dr.-Ing., 5100 Aachen Verfahren und vorrichtung zur nutzung von bei niedriger temperatur aufgenommener waerme
DE3140003C2 (de) * 1981-10-08 1984-07-05 Buderus Ag, 6330 Wetzlar Heizungsanlage
DE3149005A1 (de) * 1981-12-10 1983-06-16 Buderus Ag, 6330 Wetzlar Verfahren und vorrichtung zum betreiben einer monovalent alternativen absorptionsheizanlage
DE3200436A1 (de) * 1982-01-09 1983-07-21 Buderus Ag, 6330 Wetzlar Verfahren zum betreiben einer absorptionswaermepumpe und waermepumpe zur druchfuehrung des verfahrens
DE3204288A1 (de) * 1982-02-06 1983-08-11 Joh. Vaillant Gmbh U. Co, 5630 Remscheid Sorptionswaermepumpe

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995025934A1 (fr) * 1994-03-21 1995-09-28 Cryotherm Engineering Limited Machine de chauffage/refroidissement a absorption
WO2009119695A3 (fr) * 2008-03-27 2012-12-20 Honda Motor Co., Ltd. Unité de pompe à chaleur à absorption
WO2010078957A2 (fr) 2008-12-19 2010-07-15 Invensor Gmbh Élément limiteur de pression permettant de diviser le débit volumique de condensation dans des machines à sorption
IT201800007258A1 (it) * 2018-07-17 2020-01-17 Macchina di riscaldamento ad attivazione termica
WO2020016767A1 (fr) * 2018-07-17 2020-01-23 Ariston Thermo Innovative Technologies S.R.L. Machine de chauffage activée thermiquement
EP3842710A1 (fr) * 2019-12-23 2021-06-30 Technische Universität Berlin Procédé de fonctionnement d'une installation de sorption et installation de sorption
WO2021130003A1 (fr) 2019-12-23 2021-07-01 Technische Universität Berlin Système à sorption et son procédé de mise en fonctionnement
US12018864B2 (en) 2019-12-23 2024-06-25 Technische Universität Berlin Sorption system and method for operating same

Also Published As

Publication number Publication date
EP0152931B1 (fr) 1990-11-07
ATE58225T1 (de) 1990-11-15
DE3580377D1 (de) 1990-12-13
DE3405800A1 (de) 1985-08-22
DE3405800C2 (de) 1986-11-20
EP0152931A3 (en) 1987-05-20

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