EP0096822A2 - Procédé pour le fonctionnement d'une pompe à chaleur à absorption bivalente et pompe à chaleur à absorption pour la réalisation de ce procédé - Google Patents

Procédé pour le fonctionnement d'une pompe à chaleur à absorption bivalente et pompe à chaleur à absorption pour la réalisation de ce procédé Download PDF

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Publication number
EP0096822A2
EP0096822A2 EP83105566A EP83105566A EP0096822A2 EP 0096822 A2 EP0096822 A2 EP 0096822A2 EP 83105566 A EP83105566 A EP 83105566A EP 83105566 A EP83105566 A EP 83105566A EP 0096822 A2 EP0096822 A2 EP 0096822A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
absorber
cooker
line
heat pump
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
EP83105566A
Other languages
German (de)
English (en)
Other versions
EP0096822A3 (en
EP0096822B1 (fr
Inventor
Robert Dipl.-Ing. Mack
Winfried Prof. Dr.-Ing. Buschulte
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.)
Deutsches Zentrum fuer Luft und Raumfahrt eV
Original Assignee
Deutsches Zentrum fuer Luft und Raumfahrt eV
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
Application filed by Deutsches Zentrum fuer Luft und Raumfahrt eV filed Critical Deutsches Zentrum fuer Luft und Raumfahrt eV
Priority to AT83105566T priority Critical patent/ATE22612T1/de
Publication of EP0096822A2 publication Critical patent/EP0096822A2/fr
Publication of EP0096822A3 publication Critical patent/EP0096822A3/de
Application granted granted Critical
Publication of EP0096822B1 publication Critical patent/EP0096822B1/fr
Expired 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 a method for operating a bivalent-operated absorption pump, as described in the preamble of claim 1.
  • the invention relates to a bivalent absorption pump for performing this method with the features of the preamble of claim 6.
  • Can absorption heat pumps for heating purposes only be used effectively when the air temperature egg - nen certain value, for example, +3 0 C, not below. At lower temperatures, the performance figure drops sharply, especially due to the icing of the evaporator.
  • an absorption heat pump with the features of claim 6 is proposed for carrying out this method.
  • the solvent flow from the cooker to the absorber and the refrigerant flow leaving the condenser are each split into two partial flows.
  • a partial flow of the solvent and a partial flow of the refrigerant are carried out in the manner typical for pure heat pump operation, while the other other partial flows are conducted in the manner typical for pure boiler operation.
  • the absorber is divided into a low-pressure absorber, which is used purely for heat pump operation, and a high-pressure absorber, which serves purely for boiler operation.
  • the heat exchange with the heating system takes place in the condenser and in both absorbers. In this way, it is possible to share both the advantages of pure heat pump operation and the advantages of pure boiler operation, the proportion of pure heat pump operation relative to the proportion of pure boiler operation being continuously adjustable according to the ratio of the splitting of the two flows into partial flows .
  • the gas flow cross section of the evaporator is preferably reduced compared to pure heat pump operation. Due to the smaller active area of the evaporator, it is possible to keep it free of ice and effectively for longer, so that heat pump operation can be maintained down to lower temperatures.
  • the poor solution and the refrigerant are combined in the low-pressure absorber in pure heat pump operation and the resulting rich solution is then passed through the high-pressure absorber.
  • both absorbers are used for heat exchange even in pure heat pump operation.
  • this can be formed as a volume flow variable expansion valves.
  • the throttles comprise at least two Parallelleitun g s with throttle valves, the parallel lines can be opened alternately or together by on-off valves.
  • the high-pressure absorber can be switched on in the pure heat pump mode between the low-pressure absorber and the first return line.
  • the heat pump shown in the drawing comprises, in the manner customary for heat pumps, a cooker or expeller 1 in which a refrigerant-solvent mixture is heated by means of a heating source not shown in the drawing.
  • the refrigerant evaporating is fed via a refrigerant line 2 through a reflux condenser 3 to a condenser 4 and passes from there in the liquid State through a heat exchanger 5 via a refrigerant throttle 6 to an evaporator 7.
  • the re-evaporated refrigerant which is now under low pressure, is supplied in countercurrent through the heat exchanger 5 to a first absorber 8, which is referred to below as a low-pressure absorber.
  • a solvent line 9 leads from the cooker 1 through a temperature changer 10 and via a solvent throttle 11 to the first absorber 8, in which the refrigerant supplied via the refrigerant line 2 and the solvent supplied via the solvent line 9 are combined.
  • a second absorber 18 is provided, which is referred to below as a high-pressure absorber.
  • a by-pass line 19 leads into this high-pressure absorber, which feeds the solution from the cooker 1 directly to the high-pressure absorber 18, bypassing the temperature changer 10 and the solvent throttle 11.
  • a branch 20 is provided in the refrigerant line 2 downstream of the condenser; here, a bypass line 21 branches off from the refrigerant line 2, which either opens directly into the cooker or preferably according to the broken line in the high-pressure absorber 18.
  • a bypass line 21 branches off from the refrigerant line 2, which either opens directly into the cooker or preferably according to the broken line in the high-pressure absorber 18.
  • a second return line 23 is switched on. The second return line 23 opens directly into the cooker 1.
  • a completely closable metering valve 25 is located in the solvent line 9, and a completely closable metering valve 26 is likewise arranged in the by-pass line 19.
  • Another fully closable metering valve 27 is switched into the bypass line 21.
  • a further fully closable metering valve 28 is located in the refrigerant line downstream of the branch 20.
  • Closing valves 29 and 30 are arranged in the return lines 13 and 23, respectively, and the outlet 22 of the absorber 18 is connected downstream of the closing valve 29 by means of a connecting line 31, in which a closing valve 32 is located.
  • a branch line provided with a closing valve 33 branches off from the by-pass line 19 to the first absorber 8; A further closing valve 35 is arranged in the by-pass line downstream of this branch.
  • Another connecting line 36 in which a closing valve 37 is arranged, connects the outlet 12 of the first absorber 8 to the inlet of the second absorber 18.
  • the two throttles 6 and 11 are adjustable in their throttling action, this is indicated in the drawing by a motorized actuator. These throttles can also be designed as expansion valves variable in volume flow.
  • FIG. 2 Another possible configuration of the chokes results from the exemplary embodiment in FIG. 2, which differs from the exemplary embodiment in FIG. 1 only in the configuration of the chokes. Corresponding parts therefore have the same reference numerals.
  • the refrigerant throttle 6 comprises two parallel lines 38 and 39. In each of these lines, a closing valve 40 or 41 is connected in series with a throttle valve 42 or 43 with a fixed throttle effect.
  • the solvent throttle 11 comprises two parallel lines 44 and 45, in each of which a closing valve 46 or 47 and a throttle valve 48 or 49 with a fixed throttle effect are switched on.
  • the heat pump shown in the drawing can be operated in three different ways, which are explained below.
  • valves 26, 27, 30, 32, 33, 35 and 37 are closed, while only the valves 25, 28 and 29 are open.
  • the refrigerant evaporated by the cooker is supplied to the low-pressure absorber 8 through the refrigerant line 2 via the condenser, the refrigerant throttle and the evaporator.
  • the poor solution passes from the cooker through the solvent line 9 through the temperature changer, the solvent throttle 11 also into the low pressure absorber. After the two components have been combined, the rich solution is fed back to the cooker via the first return line 13 and the two lines 16 and 17.
  • the rich solution only penetrates the low-pressure absorber 8; the high-pressure absorber 18 is not switched into the circuit in this operating mode.
  • valve 29 In an alternative mode of operation of pure heat pump operation, the valve 29 is closed while the valves 32 and 37 are opened.
  • the rich solution then flows through the high-pressure absorber 18 before entering the first return line 13, so that heat can also be exchanged with the heating system in this high-pressure absorber.
  • valves 25, 28, 29, 32, 33 and 37 are closed, while valves 26, 27, 30 and 35 are open.
  • the refrigerant leaving the stove passes through the bypass line 21 neither directly into the cooker or into the high-pressure absorber 18.
  • the refrigerant throttle and the evaporator are bypassed because of the closed valve 28.
  • the solvent passes via the by-pass line 19 directly into the high-pressure absorber 18, the temperature changer 10 and the solvent throttle 11 being bridged.
  • the heat is exchanged with the heating system, and the cooled solvent, to which the coolant, which is also cooled, is added, then reaches the cooker via the second return line 23. Since both the refrigerant choke and the solvent choke are bridged, the pressure in the entire circuit is the same as in the stove, i.e. a relatively high pressure.
  • the pump 24 is therefore designed as a pure circulation pump, while the pump 14 is designed in the manner customary in absorption heat pumps as a pressure pump which has to work against the pressure in the stove.
  • valves 32, 33 and 37 are closed, but the other valves 25, 26, 27, 28, 29, 30 and 35 are open. This divides both the refrigerant flow and the solvent flow. Part of the refrigerant flow reaches the low-pressure absorber via the refrigerant line, the refrigerant throttle 6 and the evaporator 7, the other part of the refrigerant is supplied to either the cooker 1 or the high-pressure absorber 18 via the bypass line 21.
  • Heat is exchanged with the heating system in the condenser and in both absorbers.
  • the heating system in the condenser and in the high-pressure absorber is supplied directly with heat which comes from the heating of the cooker, while the heating in the low-pressure absorber is supplied with heat which is taken from the surroundings via the evaporator.
  • the ratio of the two partial refrigerant flows to one another and the ratio of the two partial solvent flows to one another can be adjusted steplessly from the pure heat pump operation to the pure boiler operation by suitable selection of the opening of the valves 27 and 28 or 25 and 26 assigned to one another.
  • the throttling effect of the refrigerant throttle 6 and the solvent throttle 11 must be changed in accordance with the size of the partial flow flowing through the throttles, so that the relaxation required for the heat pump effect occurs.
  • this throttling is achieved by corresponding opening or closing of the closing valves 40 and 41 or 46 and 47.
  • the entire system can be optimally adapted to the external conditions, in particular it is possible at any time, in mixed operation, depending on the requirements, to have a larger heat pump and egg. to choose a lower proportion of the boiler or vice versa.
  • valve 35 is closed while valves 33 and 37 are opened.
  • the throughput of both the refrigerant expelled from the cooker and the poor solution flowing from the cooker to the absorber is not controlled in a manner known per se by control valves with a variable throttle effect, but by a different pumping capacity of the circulation pump or pumps in the Return lines 13 and 23.
  • these pumps can advantageously be of multi-stage or volumetric flow.
  • the main advantage here is that there is no pressure drop in the line caused by controllable throttle valves, but the pressure level in the entire line system is approximately the same. To circulate the solution, therefore, only low pumping capacities are required, which are altogether significantly lower than those that had to be applied in conventional processes in which the throughput was achieved by different throttling of the flows.
  • control of the circulation pumps can be accomplished in the simplest way and can therefore be optimally adapted to the respective requirements.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)
EP83105566A 1982-06-11 1983-06-07 Procédé pour le fonctionnement d'une pompe à chaleur à absorption bivalente et pompe à chaleur à absorption pour la réalisation de ce procédé Expired EP0096822B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83105566T ATE22612T1 (de) 1982-06-11 1983-06-07 Verfahren zum betrieb einer bivalent betreibbaren absorptionswaermepumpe und absorptionswaermepumpe zur durchfuehrung dieses verfahrens.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3222067 1982-06-11
DE19823222067 DE3222067A1 (de) 1982-06-11 1982-06-11 Verfahren zum betrieb einer bivalent betreibbaren absorptionswaermepumpe und absorptionswaermepumpe zur durchfuehrung dieses verfahrens

Publications (3)

Publication Number Publication Date
EP0096822A2 true EP0096822A2 (fr) 1983-12-28
EP0096822A3 EP0096822A3 (en) 1984-07-25
EP0096822B1 EP0096822B1 (fr) 1986-10-01

Family

ID=6165872

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83105566A Expired EP0096822B1 (fr) 1982-06-11 1983-06-07 Procédé pour le fonctionnement d'une pompe à chaleur à absorption bivalente et pompe à chaleur à absorption pour la réalisation de ce procédé

Country Status (6)

Country Link
US (1) US4464907A (fr)
EP (1) EP0096822B1 (fr)
AT (1) ATE22612T1 (fr)
CA (1) CA1206766A (fr)
DE (2) DE3222067A1 (fr)
DK (1) DK158322C (fr)

Families Citing this family (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4524759A (en) * 1983-10-28 1985-06-25 Butler Robert F Process for the reversible transfer of thermal energy and heat transfer system useful therein
DE3432888C2 (de) * 1984-09-07 1987-03-12 Borsig Gmbh, 1000 Berlin Absorptionskälteanlage mit räumlich getrenntem Hochdruck- und Niederdruckteil
NL8403517A (nl) * 1984-11-19 1986-06-16 Rendamax Ag Absorptie-resorptie warmtepomp.
US4593531A (en) * 1985-01-15 1986-06-10 Ebara Corporation Absorption cooling and heating apparatus and method
NL8501039A (nl) * 1985-04-09 1986-11-03 Tno Werkwijze voor het bedrijven van een absorptiewarmtepomp of koelinrichting, alsmede absorptiewarmtepomp of -koelinrichting.
DE3518276C1 (de) * 1985-05-22 1991-06-27 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5300 Bonn Verfahren zum Betrieb einer Waermepumpenanlage und zur Durchfuehrung dieses Verfahrens geeignete Waermepumpenanlage
DE3619735C1 (de) * 1986-01-24 1987-07-02 Peter Dr-Ing Vinz Verfahren und Einrichtung zur energiesparenden automatischen Einhaltung der Konzentration von verdampfenden Kaeltemittelgemischen
US4748830A (en) * 1986-02-28 1988-06-07 Hitachi, Ltd. Air-cooled absorption heating and cooling system
US5009086A (en) * 1989-03-30 1991-04-23 Gas Research Institute Passive refrigeration fluids condition
US4926659A (en) * 1989-03-30 1990-05-22 Gas Research Institute Double effect air conditioning system
US4972679A (en) * 1990-02-09 1990-11-27 Columbia Gas Service Corporation Absorption refrigeration and heat pump system with defrost
US5024063A (en) * 1990-05-11 1991-06-18 Erickson Donald C Branched gax absorption vapor compressor
JP2897587B2 (ja) * 1993-04-07 1999-05-31 株式会社日立製作所 吸収式冷凍機
KR0132391B1 (ko) * 1994-02-25 1998-04-20 김광호 흡수식 냉방기
US5584193A (en) * 1994-04-26 1996-12-17 York International Corporation Absorption-type refrigeration systems and methods
US5901567A (en) * 1996-12-18 1999-05-11 Honda Giken Kogyo Kabushiki Kaisha Absorption refrigerating/heating apparatus
JP3393780B2 (ja) * 1997-01-10 2003-04-07 本田技研工業株式会社 吸収式冷暖房装置
DE19813157C2 (de) * 1998-03-19 2000-07-27 Hansa Ventilatoren Masch Raumlufttechnische Anlage zur bivalenten Klimatisierung eines Raumes
US6170279B1 (en) * 1999-07-28 2001-01-09 Li Ding-Yu Fisherman refrigerating device using engine exhaust
DE10237851A1 (de) * 2002-08-19 2004-03-04 ZAE Bayern Bayerisches Zentrum für angewandte Energieforschung e.V. Ein- oder mehrstufige Absorptionskältemaschine (AKM) oder Absorptionswärmepumpe (AWP) sowie Verfahren zur Steuerung der Verdampferleistung in einer solchen AKP/AWP
CN101101161B (zh) * 2007-07-30 2010-05-19 李华玉 复合第二类吸收式热泵
CN101694331A (zh) * 2009-08-27 2010-04-14 李华玉 单级基础上的复合第二类吸收式热泵
CN101957093B (zh) * 2010-08-13 2013-05-29 李华玉 吸收-再吸收-发生系统与第一类吸收式热泵
CN103940142B (zh) * 2013-04-03 2016-08-17 李华玉 分路循环第一类吸收式热泵
CN103471281B (zh) * 2013-04-03 2015-11-25 李华玉 分路循环第一类吸收式热泵

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2272871A (en) * 1938-01-10 1942-02-10 Honeywell Regulator Co Absorption heating system
US3638452A (en) * 1969-10-20 1972-02-01 Whirlpool Co Series water-cooling circuit for gas heat pump
US3817050A (en) * 1972-12-26 1974-06-18 Texaco Inc Two-stage ammonia absorption refrigeration system with at least three evaporation stages
DE2743488A1 (de) * 1977-09-28 1979-03-29 Karl Friedrich Prof Dr Knoche Verfahren und vorrichtung zur nutzung von sonnenenergie fuer raumheizung
DE2758773C2 (de) * 1977-12-29 1981-12-17 Ask August Schneider Gmbh & Co Kg, 8650 Kulmbach Bivalente Heizanlage
DE2856767A1 (de) * 1978-12-29 1980-07-17 Alefeld Georg Absorptions-waermepumpe veraenderbarer ausgangs-waermeleistung
DE2908423A1 (de) * 1979-03-03 1980-09-11 Alefeld Georg Absorptions- waermepumpe veraenderbarer ausgangs- waermeleistung

Also Published As

Publication number Publication date
DK158322C (da) 1990-10-01
DK266383A (da) 1983-12-12
EP0096822A3 (en) 1984-07-25
DK266383D0 (da) 1983-06-10
CA1206766A (fr) 1986-07-02
DE3222067A1 (de) 1983-12-15
DE3366562D1 (en) 1986-11-06
ATE22612T1 (de) 1986-10-15
EP0096822B1 (fr) 1986-10-01
US4464907A (en) 1984-08-14
DK158322B (da) 1990-04-30

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