EP0046196B1 - Procédé pour le fonctionnement d'une installation de chauffage à absorption monovalente et alternative - Google Patents

Procédé pour le fonctionnement d'une installation de chauffage à absorption monovalente et alternative Download PDF

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Publication number
EP0046196B1
EP0046196B1 EP81105453A EP81105453A EP0046196B1 EP 0046196 B1 EP0046196 B1 EP 0046196B1 EP 81105453 A EP81105453 A EP 81105453A EP 81105453 A EP81105453 A EP 81105453A EP 0046196 B1 EP0046196 B1 EP 0046196B1
Authority
EP
European Patent Office
Prior art keywords
heat
fluid
heating
solvent
absorber
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.)
Expired
Application number
EP81105453A
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German (de)
English (en)
Other versions
EP0046196A2 (fr
EP0046196A3 (en
Inventor
Paul Dipl.-Ing. Heimbach
Peter Goebel
Franz Gruber
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.)
Buderus AG
Original Assignee
Buderus AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Buderus AG filed Critical Buderus AG
Priority to AT81105453T priority Critical patent/ATE9400T1/de
Publication of EP0046196A2 publication Critical patent/EP0046196A2/fr
Publication of EP0046196A3 publication Critical patent/EP0046196A3/de
Application granted granted Critical
Publication of EP0046196B1 publication Critical patent/EP0046196B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • F25B30/00—Heat pumps
    • F25B30/04—Heat pumps of the sorption type

Definitions

  • the invention relates to a method for operating a monovalent alternative absorption heating system, which operates above a predetermined ambient temperature in heat pump mode and at lower temperatures in direct heating mode, with a refrigerant circuit in which a refrigerant is expelled from a refrigerant-rich solvent, liquefied, evaporated from the environment by supplying heat, and is absorbed by low-refrigerant solvents, as well as with a heating medium circuit in which a heating medium is heated by heat exchange with condensing refrigerant and by absorption heat.
  • a method of this type is used, for example, for space and / or process water heating in single and multi-family houses.
  • the term “monovalent alternative” means that the absorption heating system works as a heat pump with only one type of primary energy up to a preselectable lowest outside air temperature, and is operated below this temperature by direct heat transfer from the same primary energy source to the heating medium.
  • the heating of the heating circuit via a flue gas heat exchanger can only partially utilize the combustion gases, because the heat generator is primarily designed and constructed for heating the solvent.
  • the flue gas heat exchanger can only serve to make better use of the flue gases, but cannot optimally take into account the overall function of the heat generator in direct heating mode.
  • DE-A-28 387 15 describes a heat exchanger in the line of the low-refrigerant solvent for the heating medium circuit, but this remains in the overall system in both heat pump and direct heating operation. This means that optimal operation is not possible during the two operating modes.
  • the present invention is therefore based on the object of developing a method which is distinguished by low heat losses and better heating output in both heat pump and direct heating mode.
  • this object is achieved in that the heating medium in direct heating operation bypassing the refrigerant liquefier and absorber is conducted via a heat exchanger which is separate from the refrigerant liquefier and which can be connected in series to the line of the low-refrigerant solvent via a multi-way valve to the absorber between the heat generator and the absorber.
  • heating of the heating medium in direct heating mode is carried out in a heat exchanger provided exclusively for this purpose.
  • the object of the invention achieves the advantage that the heat transfer to the heating medium is carried out under optimal conditions.
  • heating of the absorber and the refrigerant condenser can also be avoided in this way. The heat losses in the system are thus reduced.
  • the low-refrigerant solvent is brought into heat exchange with a refrigerant-rich solvent in a temperature changer. With this procedure you can prevent the above-mentioned excessive cooling of the low-refrigerant solvent.
  • the heating medium is additionally heated by heat exchange with steam flowing out of a rectifier in a return condenser and / or with flue gas withdrawing from the heat generator.
  • devices for supplying heat from the environment to the refrigerant evaporator and absorber are switched off in direct heating mode.
  • Such devices are, for example, fans for supplying ambient air and valves for preventing the supply of refrigerant from the evaporator to the absorber.
  • a further refinement of the subject matter of the invention has proven to be expedient, according to which the switching and control processes required when switching from heat pump to direct heating mode and vice versa are controlled by a central control unit.
  • the absorption heating system has a heat generator 1 which is equipped with a heat generator 2, for example an atmospheric gas burner 2.
  • the absorption heating system contains a solvent circuit, which in the direction of flow of the solvent contains a solvent pump 3, a temperature changer 4, a rectifier 5, an expeller 6 arranged in the heat generator 1, a separator 7 and an absorber 8.
  • a refrigerant circuit is also provided, which begins in the vapor space of the separator 7 and leads via the head of the rectifier 5, a condenser 10, a cold exchanger 22 and an evaporator 11 designed as an air cooler to the absorber 8 and passes there into the solvent circuit.
  • a mixture of ammonia and water is used as the refrigerant-solvent mixture.
  • This mixture is removed from the sump of the absorber 8, brought into heat exchange with low-refrigerant solvent in the temperature changer 4 and then fed to the rectifier 5.
  • this gas mixture is concentrated in refrigerant, while a refrigerant-rich solvent accumulates in the sump of the rectifier 5.
  • the refrigerant-rich solvent is fed to the expeller 6, heated there by supplying heat of combustion and brought to high pressure, and separated in the following separator 7 into a refrigerant-rich gas fraction and a liquid fraction containing low-refrigerant solvent.
  • the liquid fraction is passed through a multi-way solenoid valve 20, which releases the temperature changer 4 during heat pump operation. There, the low-refrigerant solvent is brought into heat exchange with refrigerant-rich solvent and then via a device which regulates the flow rate as a function of the liquid level in the sump of the rectifier 5, e.g. a floating regulator, abandoned at the head of the absorber 8.
  • the absorption heating system contains a heating medium circuit in which a heating medium is circulated by a circulation pump 12.
  • the heating medium is guided in heat pump operation via a multi-way solenoid valve 19 via heating coils 14 and 15 in the condenser 10 and in the absorber 8, where it absorbs heat.
  • the heating medium is further heated in a return cooler 9 arranged in the head of the rectifier 5 and in a flue gas cooler 16 arranged in the flue gas outlet of the heat generator 1.
  • the heating medium reaches the circulation pump 12, from where it is fed to a consumer group 13, in which it emits heat.
  • the multi-way solenoid valve 20 when the heating is switched to direct heating operation, the multi-way solenoid valve 20 is switched over, so that the low-refrigerant hot solvent is passed into the heat exchanger 18 and is brought into heat exchange with the heating medium there.
  • the separate heat exchanger 18 is dimensioned according to the heat exchange conditions that occur and therefore enables an optimization of the heating capacity of the system. After flowing through the separate heat exchanger 18, the low-refrigerant solvent is passed into the temperature changer 4 as in heat pump operation.
  • the multi-way solenoid valve 19 is switched over and the heating medium is bypassed the condenser 10 and the absorber 8 via a bypass line 24. In this way, excessive heating of these antagen parts with all the disadvantages associated with direct heating operation is avoided.
  • All switching operations are controlled by a central control unit 23 in accordance with a preprogrammed function sequence for direct heating or heat pump operation.
  • encoder data e.g. Signals from a temperature sensor supplied (arrow 25), which are then converted into corresponding switching signals (arrow 26).
  • the energy supply to the control unit 23 is symbolized by an arrow 27 ′.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Claims (5)

1. Procédé pour opérer une installation de chauffage à absorption du type monovalént-alternatif marchant au dessus d'une température pré- définie en fonctionnement thermopompe et aux températures plus basses en fonctionnement de chauffage direct, avec un cyclage de fluide frigorigène, dans lequel un fluide frigorigène est fait sortir d'un solvant riche en fluide frigorigène, est liquéfié, évaporé par amenée de chaleur de l'environnement et est absorbé par un solvant pauvre en fluide frigorigène, et avec un cyclage de fluide chauffant, dans lequel un fluide chauffant est chauffé par transfert de chaleur d'un fluide frigorigène condensent et par réception de chaleur d'absorption, en quoi le fluide chauffant est conduit, en fonctionnement de chauffage direct, en dérivation du condenseur de fluide frigorigène (10) et absorbeur (8) sur un échangeur de chaleur séparé du condenseur de fluide frigorigène et est chauffé là par amenée direct de chaleur de combustion du générateur de chaleur, caractérisé en ce que l'échangeur de chaleur (18) prévu en fonctionnement de chauffage direct pour le fluide chauffant est raccordable à la conduite du solvant pauvre en un fluide frigorigène sur une vanne à plusieurs voies (20) en série avec l'absorbeur (8) entre le générateur de chaleur (1 ) et l'absorbeur (8).
2. Procédé selon la revendication 1, caractérisé en ce que le solvant pauvre en fluide frigorigène est, après son transfert de chaleur du fluide chauffant, amené à un transfert de chaleur avec le solvant riche en fluide frigorigène dans un variateur de température (4).
3. Procédé selon les revendications 1 ou 2, caractérisé en ce que le fluide chauffant est chauffé, additionnellement, par transfert de chaleur du vapeur écoulant d'un rectificateur (5) dans un condenseur à reflux (9) et/ou gaz de la combustion écoulant du générateur de chaleur (1 ).
4. Procédé selon une des revendications 1 à 3, caractérisé en ce que des installations pour l'amenée de la chaleur de l'environnement au vaporisateur de fluide frigorigène (11 ) et à l'absorbeur (8) sont déconnectées en fonctionnement de chauffage direct.
5. Procédé selon une des revendications 1 à 4, caractérisé en ce que les processus de commutation et réglage requis au changement du fonctionnement du thermopompe au fonctionnement de chauffage direct et vice versa sont commandés par un équipement central de réglage (23).
EP81105453A 1980-08-16 1981-07-13 Procédé pour le fonctionnement d'une installation de chauffage à absorption monovalente et alternative Expired EP0046196B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81105453T ATE9400T1 (de) 1980-08-16 1981-07-13 Verfahren zum betreiben einer monovalent alternativen absorptionsheizanlage.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803031033 DE3031033A1 (de) 1980-08-16 1980-08-16 Verfahren und vorrichtung zum betreiben einer monovalent alternativen adsorptionsheizanlage
DE3031033 1980-08-16

Publications (3)

Publication Number Publication Date
EP0046196A2 EP0046196A2 (fr) 1982-02-24
EP0046196A3 EP0046196A3 (en) 1982-04-14
EP0046196B1 true EP0046196B1 (fr) 1984-09-12

Family

ID=6109775

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81105453A Expired EP0046196B1 (fr) 1980-08-16 1981-07-13 Procédé pour le fonctionnement d'une installation de chauffage à absorption monovalente et alternative

Country Status (5)

Country Link
US (1) US4410134A (fr)
EP (1) EP0046196B1 (fr)
JP (1) JPS57127761A (fr)
AT (1) ATE9400T1 (fr)
DE (2) DE3031033A1 (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3432888C2 (de) * 1984-09-07 1987-03-12 Borsig Gmbh, 1000 Berlin Absorptionskälteanlage mit räumlich getrenntem Hochdruck- und Niederdruckteil
GB8503287D0 (en) * 1985-02-08 1985-03-13 Ic Gas Int Ltd Heat pump systems
US5367884B1 (en) * 1991-03-12 1996-12-31 Phillips Eng Co Generator-absorber-heat exchange heat transfer apparatus and method and use thereof in a heat pump
US5271235A (en) * 1991-03-12 1993-12-21 Phillips Engineering Company High efficiency absorption cycle of the gax type
US5570584A (en) * 1991-11-18 1996-11-05 Phillips Engineering Co. Generator-Absorber heat exchange transfer apparatus and method using an intermediate liquor
US5255528A (en) * 1992-06-03 1993-10-26 Kim Dao Method and apparatus for recuperating waste heat in absorption systems
US5579652A (en) * 1993-06-15 1996-12-03 Phillips Engineering Co. Generator-absorber-heat exchange heat transfer apparatus and method and use thereof in a heat pump
US5490393A (en) * 1994-03-31 1996-02-13 Robur Corporation Generator absorber heat exchanger for an ammonia/water absorption refrigeration system
US5782097A (en) * 1994-11-23 1998-07-21 Phillips Engineering Co. Generator-absorber-heat exchange heat transfer apparatus and method and use thereof in a heat pump
JPH10160283A (ja) * 1996-11-29 1998-06-19 Sanyo Electric Co Ltd 吸収式ヒートポンプ装置
AT408805B (de) * 1999-05-25 2002-03-25 Vaillant Gmbh Sorptionsmaschine
JP2003075017A (ja) * 2001-09-04 2003-03-12 Sanyo Electric Co Ltd 排熱利用冷凍システム
JP2007120810A (ja) * 2005-10-26 2007-05-17 Tokyo Gas Co Ltd 吸収ヒートポンプ
JP2007120811A (ja) * 2005-10-26 2007-05-17 Tokyo Gas Co Ltd 吸収ヒートポンプ
US20100229594A1 (en) * 2008-12-04 2010-09-16 Donald Charles Erickson Chilling economizer
US9341400B2 (en) * 2010-08-06 2016-05-17 Braun Intertec Geothermal, Llc Mobile hydro geothermal testing systems and methods
CN102840719B (zh) * 2012-09-26 2014-06-11 山东威特人工环境有限公司 一种太阳能空气源吸收式热泵装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2659641A1 (de) * 1976-12-30 1978-07-13 Christian Dipl Ing Schneider Gas- oder oelbetriebene heizanlage zur waermeerzeugung
DE2838715A1 (de) * 1978-09-02 1980-03-13 Vaillant Joh Gmbh & Co Sorptionswaermepumpe
EP0036981A2 (fr) * 1980-03-28 1981-10-07 Buderus Aktiengesellschaft Procédé pour le fonctionnement d'une installation de chauffage à absorption

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE2803118B2 (de) * 1978-01-25 1980-07-31 Stiebel Eltron Gmbh & Co Kg, 3450 Holzminden Verfahren zur Beheizung mit einer Absorptionswärmepumpenanlage und Vorrichtung zur Durchführung des Verfahrens
DE2854055A1 (de) * 1978-12-14 1980-07-03 Linde Ag Verfahren zum erhitzen eines waermetraegers mit einer absorptionswaermepumpe
DE2856767A1 (de) * 1978-12-29 1980-07-17 Alefeld Georg Absorptions-waermepumpe veraenderbarer ausgangs-waermeleistung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2659641A1 (de) * 1976-12-30 1978-07-13 Christian Dipl Ing Schneider Gas- oder oelbetriebene heizanlage zur waermeerzeugung
DE2838715A1 (de) * 1978-09-02 1980-03-13 Vaillant Joh Gmbh & Co Sorptionswaermepumpe
EP0036981A2 (fr) * 1980-03-28 1981-10-07 Buderus Aktiengesellschaft Procédé pour le fonctionnement d'une installation de chauffage à absorption

Also Published As

Publication number Publication date
ATE9400T1 (de) 1984-09-15
DE3031033A1 (de) 1982-05-06
EP0046196A2 (fr) 1982-02-24
JPS57127761A (en) 1982-08-09
US4410134A (en) 1983-10-18
DE3166025D1 (en) 1984-10-18
EP0046196A3 (en) 1982-04-14

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