EP0013018A1 - Installation de chauffage comportant un circuit de chauffage, une chaudière et une pompe à chaleur - Google Patents

Installation de chauffage comportant un circuit de chauffage, une chaudière et une pompe à chaleur Download PDF

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Publication number
EP0013018A1
EP0013018A1 EP79105317A EP79105317A EP0013018A1 EP 0013018 A1 EP0013018 A1 EP 0013018A1 EP 79105317 A EP79105317 A EP 79105317A EP 79105317 A EP79105317 A EP 79105317A EP 0013018 A1 EP0013018 A1 EP 0013018A1
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EP
European Patent Office
Prior art keywords
heating
heat
evaporator
heating device
air
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
EP79105317A
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German (de)
English (en)
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EP0013018B1 (fr
Inventor
Hartmut Behrens
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.)
Euroterm Te Bromma Zweden AB
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Euroterm AB
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Filing date
Publication date
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=25777004&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0013018(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority claimed from DE19782855485 external-priority patent/DE2855485A1/de
Priority claimed from DE19792919877 external-priority patent/DE2919877A1/de
Application filed by Euroterm AB filed Critical Euroterm AB
Priority to AT79105317T priority Critical patent/ATE8177T1/de
Publication of EP0013018A1 publication Critical patent/EP0013018A1/fr
Application granted granted Critical
Publication of EP0013018B1 publication Critical patent/EP0013018B1/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
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps

Definitions

  • the invention relates to the construction and operation of heating devices, in particular heating devices for residential buildings, and is particularly concerned with the recovery of the heat contained in the exhaust gases of the heating furnaces of such heating devices.
  • recuperators are known in which the exhaust gas heat heats the combustion air of the furnace through heat exchange. Since the exhaust gas contains a considerable amount of pollutants, in particular sulfur compounds, the cooling of the exhaust gas is problematic because the pollutants can then escape in the chimney and the chimney can be destroyed. For the reasons mentioned above, the situation is particularly unfavorable when the heating circuit requires only relatively small amounts of heat to heat the building.
  • the invention is therefore primarily based on the object to better utilize the combustible fuels by recovering heat from the exhaust gas from the heating furnace, without endangering the existence of the heating device and / or contaminants being released to the outside air to a critical extent.
  • the exhaust gases of the heating furnace act on the evaporator in the exhaust duct of a heat pump circulating a refrigerant, so that the exhaust gas heat is transferred to the refrigerant by heat exchange, the exhaust gases being cooled down to substantially below the dew point of all the pollutants contained therein and can therefore be easily released into the outside air.
  • the heat absorbed by the refrigerant in the evaporator is brought to a higher temperature level with the aid of a compressor in the manner customary in heat pumps and is fed directly into the heating circuit of the heating system by renewed heat exchange.
  • the heat pump used for exhaust gas heat recovery can be used during the period in which the heating circuit requires only a relatively small amount of heat (transition time, cool days, etc.) can be used as the sole heat supplier by directly introducing the surrounding outside air into the exhaust duct and pasting the evaporator.
  • the heat pump operates in the manner of a conventional air heat pump.
  • a combination of those two operating states of the heat pump can be achieved by adding outside air to the exhaust gas coming from the heating furnace according to a development of the invention, before this is fed to the evaporator. In this way, on the one hand, the high throughput that a heat pump operating in pure air operation needs is obtained, and on the other hand, excessive heating of the evaporator is avoided.
  • This mode of operation can be further developed in that, instead of fresh outside air, the cooled exhaust air is recirculated, which occurs behind the fan, which forces the necessary exhaust gas / air flow through the evaporator.
  • This has the additional advantage that the dew point drop that occurs when fresh air is added is avoided and only a temperature drop occurs.
  • a heat pump according to the invention is particularly advantageous because it allows a particularly simple basic control of the heating device. Because the pressure (and in the same way the temperature) is a reliable indicator of the condition of the refrigerant in the heat pump and thus also the temperature at the evaporator on the one hand and the heat transport caused by the heat pump on the other hand, a simple control device is sufficient, which depends on the pressure or the temperature of the refrigerant in the evaporator controls the operation of the heating furnace and the fan in such a way that When the fan is running and heat is exchanged between the outside air and the refrigerant, the heating system is only switched on if the pressure falls below a specified lower limit value or the temperature, but the heating system is switched off if a specified upper limit value of the pressure or temperature is exceeded .
  • This arrangement can be further developed according to the invention into a system with multivalent heat use, first by including further heat energy sources in the heating circuit directly or indirectly in such a way that a "logical regulation" results due to the respective temperature gradient without major control measures and new primary energy (with the help of the heating burner) only if other auxiliary energies are not available.
  • a solar heating device which (if solar thermal energy is generated) heats the return of the heating circuit before it enters the condenser and absorbs the thermal energy of the refrigerant there. Only then does the return flow get into the boiler, which however only comes into action when the return temperature is below the required flow temperature.
  • An advantageous side effect of this arrangement is that the boiler is kept warm and no corrosion damage can result from non-operation.
  • process water has priority over this use of the energy supplied by a solar heating device.
  • the Solar heat transport medium Has the Solar heat transport medium a sufficient temperature, so the process water is first heated and only if the solar circuit return heating is carried out only if either enough solar heat is available or its temperature level is too low.
  • the solar heat is at an even lower temperature level, so that it cannot be used for domestic water heating or return preheating, it is intended to be used by preheating the air, either as fresh air or as recirculated, cooled exhaust gas air Mixture is fed to the evaporator of the heat pump.
  • the heated exhaust air from an air conditioning system air conditioner
  • the cold fresh air by heat exchange with at least part of the cold exhaust air leaving the evaporator of the heat pump (or the cold exhaust gas / air mixture flowing out instead) ) receives.
  • the heat energy contained in the exhaust air from warm or heated rooms, such as swimming pools or the like can be used by this air directly the air flowing into the evaporator of the heat pump (or the exhaust gas / air mixture) is admixed.
  • the utilization of the thermal energy obtained can be improved by the fact that the hot water is heated to a peak in a heat exchanger which is on the primary side of that from the compressor flowing through the heat pump, highly heated refrigerant of the heat pump circuit.
  • the economy of the heat pump improves at the same time, the greater the lower the condensation temperature of the refrigerant.
  • a cross connection between the hot water return and the heating circuit return as well as a cross connection in the heats can be provided in such a way that in summer operation with the heating switched off, the hot water circuit also otherwise heat exchangers are used to preheat the heating circuit return.
  • auxiliary heat energy is wastewater.
  • a branch is therefore provided in the heat pump circuit which, with its own expansion valve, leads to an evaporator which is arranged in a waste water container and is in heat exchange connection with the waste water.
  • any other water (or any other liquid) of the appropriate temperature can be used.
  • thermal energy obtained can be that a heat exchanger is arranged in the return of the refrigerant to the expansion valve and evaporator, with the aid of which the heat contained in the still warm refrigerant condensate is transferred to the ambient air or - using a blower - to heat the air into others Rooms can be delivered.
  • a heat exchanger is arranged in the return of the refrigerant to the expansion valve and evaporator, with the aid of which the heat contained in the still warm refrigerant condensate is transferred to the ambient air or - using a blower - to heat the air into others Rooms can be delivered.
  • Such utilization of the residual heat in the refrigerant of the heat pump circuit is cheaper than a countercurrent heat exchange with the cold refrigerant flowing from the evaporator to the compressor, because this leads to an increase in the compressor temperature.
  • This heat extraction from the heat pump circuit can also be used to remove the heat of condensation in the summer when the heat pump is only running to operate a cooling air conditioning system (because hot water has already been sufficiently heated).
  • the circulation pump is switched off when the pressure or the temperature in the condenser of the heat pump circuit reaches a certain value falls below. If the pressure or temperature rise above this value again, the circulation pump is switched on again.
  • Fig. 1 shows a boiler 1 with the associated heating, not shown in detail.
  • the heated in the boiler 1 heat transfer medium usually water, flows through the heating circuit 2, in which a plurality of radiators 3 are turned on; only a single radiator is shown in the present case.
  • a circulation pump 4 ensures the forced circulation of the heat transfer medium.
  • the flue gases from the heating system are released through the flue gas duct 6. Of the building in which the heating system is arranged, only the roof 7 is indicated.
  • An adjustable flap 8 in the exhaust duct 6 makes it possible to direct the exhaust gas into a branch 9 through the evaporator 12 of a heat pump 13 described below and a further branch 10 back into the exhaust duct 6.
  • a control flap 21 Through the connection 19, in which there is a control flap 21, ambient air can be led into the branch 9 and mixed with the exhaust gas flowing to the evaporator 12.
  • a fan 22 in the branch 10 ensures the required flow of the exhaust gas or the exhaust gas / air mixture.
  • the fan 22 is advantageously speed-controllable, so that in pure air mode it produces a substantially higher, for example 10 times, the throughput than in exhaust gas / air mode.
  • a return line 29 for cold air (or cold air / exhaust gas mixture) branching off behind the blower 22 can be provided in the connection 19; the control flap 21 is designed and arranged such that it opens either the fresh air or the cold air supply.
  • the heat pump 13 also includes a compressor 14, a condenser 15 and an expansion valve 16. With the associated pipelines, these components form a secondary circuit which is filled with a refrigerant which is circulated by the compressor 14.
  • the refrigerant heated in the evaporator 12 flows through the pipeline 17 into the compressor 14.
  • the temperature rises sharply.
  • the condenser 15 which is in heat exchange connection with the heating circuit 2
  • the heat of the refrigerant largely becomes that in the heating circuit 2 circulated heat transfer agent given.
  • the refrigerant in the expansion valve 16 expands, it cools down strongly, so that the refrigerant is ready to absorb heat again in the evaporator 12.
  • the temperatures in the evaporator are usually 0 to + 5 ° C, in the condenser 80 to 90 ° C.
  • a valve arrangement is designated, through which a short-circuit connection 26 of the flow and return of the heating circuit 2 can be effected if the heating of the heating circuit 2 takes place only by such heat that the heat pump 13 draws the ambient air drawn in through the connection 19 from the blower 22 .
  • Fig. 2 shows - albeit schematically - the constructive design of a heating device with the features that can be seen in FIG. 1.
  • the same parts have the same reference numerals and do not require a new explanation here. Deviations and additions are described below.
  • the flow is denoted by 5 'and the return by 5 "; the broken line 30 indicates what belongs to a heating device according to the invention of simple construction and can be set up at the place of use as a compact unit.
  • the burner 38 is indicated on the boiler 1, which is subject to control by the control unit 37: the pressure in the evaporator 12 of the heat pump 13 is measured via a measuring line 36, and when the pressure falls below a predetermined minimum, the control unit 37 switches the burner via the signal line 36 ' 38 a.
  • the pressure of the refrigerant in the evaporator 12 its temperature can also be used to control the burner 38.
  • a base frame 33 standing on the floor 34 supports the boiler 1 and - partly via supports 32 for an upper frame 31 - all other components of the heating device.
  • the evaporator 12 of the heat pump 13 is supported on the upper frame 31.
  • a drip tray 23 which collects condensed water and condensed pollutants.
  • the exhaust duct is reduced to an exhaust nozzle 6 '.
  • the exhaust duct continues in a connecting line 11 which so surrounds the exhaust outlet 6 'with an extended section 11', that ambient air according to the arrows 18 in the Verbindun g s-line 11 occur and there - if the burner 38 in the Operation is - can mix with the exhaust gas.
  • the air (or the exhaust gas / air mixture) accelerated by the blower 22 comes out of the building through the outlet connection 24 in the building wall 25.
  • a chimney is not required, since the escaping gas is cooled and cleaned.
  • FIG. 3 has been expanded compared to that in FIG. 2 by numerous additional devices for the purpose of multivalent heat use. Again, the same parts are identified by the same reference numerals as in the previous figures. This also applies to FIG. 4, which in terms of circuitry illustrates the structural design of the heating device shown in FIG. 3.
  • the blower 22 arranged in the outlet connection 24 sucks either air according to the arrows 18 or air and additionally exhaust gas according to the arrows 18 ′ into the connecting channel 11 and through the evaporator 12 the heat pump.
  • an inlet 56 is provided through which warm external air (for example from a swimming pool) can be supplied.
  • a heat exchanger 48 is provided which is acted upon on the primary side via a line 59 by a heat transfer medium heated by solar energy (in a manner not shown here). The air entering according to arrows 18 can thus be preheated.
  • a connecting line - not shown here - can lead from the outlet port 24 to the inlet port with the heat exchanger 48, so that the cooled exhaust air is returned to the connecting line 11.
  • the exhaust air flowing out of the outlet connection 24 according to the arrows 24 ′ can also be used for the air conditioning (cooling) of rooms; if necessary by exchanging heat with fresh air.
  • the air duct shown on the left in FIG. 4 illustrates this, with the heat exchanger 67 and the air line 68 of an air conditioning system.
  • the heat exchanger 48 is only acted on when only solar heat of a low temperature level is available.
  • the solar heat is fed directly to the domestic water (hot water); this is not shown in Fig. 3, but in Fi g . 4 specified.
  • the heat transport medium in question is fed via line 41 to a heat exchanger 40 which is acted upon on the secondary side by the return 5 ′′ of the heating circuit 2. This then enters the condenser 15 of the heat pump and leaves it at its connection to a likewise in W ärmepumpenniklauf lying heat exchanger 42 which performs the secondary side 43 hot water through the line.
  • the refrigerant circulated by the compressor 14 in the heat pump circuit arrives after leaving the condenser 15 in a collector 28 and from there in a collector 44 which heats the ambient air or - with the help of a pipeline, not shown - the air in another room with the aid of a blower 46 .
  • a branch 51 is provided, which leads via an expansion valve 16 'to an evaporator 12' only shown in FIG. 4.
  • the return line bears the reference number 52.
  • the circulation pump 55 in the heating circuit 2 is subject to control by a pressure switch 57, which measures the pressure (or the temperature) in the condenser 15 and switches off the circulation pump 55 when the pressure falls below a certain minimum pressure in the condenser 15.
  • Fig. 4 complements the representation of Fig. 3 somewhat.
  • a line 41 ' is provided, which extends the line 41 from the solar device 61 to a heat exchanger 62, which is used for basic heating of the process water.
  • the circulation pump 63 is shown for the circulation of the heat transport medium that heats the process water.
  • the circulation pumps 63 and 55 are connected to one another by a line 64.
  • the cross connection of the feed lines consists of a line 69 with a valve 70, which is opened by a thermoplastic controlled priority switch when the process water needs heat.
  • a combustion gas turbine generator for generating electrical energy can be arranged between the burner 38 and the boiler 1 and supplies certain electrical auxiliary units with electricity. This applies primarily to the compressor 14, but possibly also the fans 22 and 46 and other electrically operated devices.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Central Heating Systems (AREA)
  • Processing Of Solid Wastes (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Heating, Cooling, Or Curing Plastics Or The Like In General (AREA)
  • Air Supply (AREA)
EP79105317A 1978-12-22 1979-12-21 Installation de chauffage comportant un circuit de chauffage, une chaudière et une pompe à chaleur Expired EP0013018B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT79105317T ATE8177T1 (de) 1978-12-22 1979-12-21 Heizeinrichtung mit einem heizungskreislauf, einer heizfeuerung und einer waermepumpe.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE2855485 1978-12-22
DE19782855485 DE2855485A1 (de) 1978-12-22 1978-12-22 Heizeinrichtung, insbesondere zur durchfuehrung des verfahrens
DE19792919877 DE2919877A1 (de) 1979-05-17 1979-05-17 Heizeinrichtung
DE2919877 1979-05-17

Publications (2)

Publication Number Publication Date
EP0013018A1 true EP0013018A1 (fr) 1980-07-09
EP0013018B1 EP0013018B1 (fr) 1984-06-27

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ID=25777004

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Application Number Title Priority Date Filing Date
EP79105317A Expired EP0013018B1 (fr) 1978-12-22 1979-12-21 Installation de chauffage comportant un circuit de chauffage, une chaudière et une pompe à chaleur

Country Status (6)

Country Link
EP (1) EP0013018B1 (fr)
CA (1) CA1120465A (fr)
DK (1) DK547979A (fr)
FI (1) FI793650A (fr)
NO (1) NO152268C (fr)
SE (1) SE438547B (fr)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0070560A2 (fr) * 1981-07-21 1983-01-26 Laurentius Pohlmeyer Installation pour réchauffer de l'eau
FR2518229A1 (fr) * 1981-12-14 1983-06-17 Dietrich De Ensemble de production de chaleur bi-energie
WO1983003662A1 (fr) * 1982-04-14 1983-10-27 KASTRÖM, Per-Olof Installation de chauffage
DE3218727A1 (de) * 1982-05-18 1983-11-24 Viessmann Hans Heizungsgeraet
EP0099441A2 (fr) * 1982-07-21 1984-02-01 Paolo Curti Appareil pour la récupération de chaleur de fumées dans une installation de chauffage ou d'air ambiant
GB2142136A (en) * 1983-06-01 1985-01-09 Star Refrigeration Heating apparatus including a heat pump
US4512288A (en) * 1983-07-15 1985-04-23 Roger Michaud Furnace heat exchanger
DE3516072A1 (de) * 1985-05-04 1986-11-06 Morgenschweis, Thomas, 5900 Siegen Heizsystem mit waermepumpe, fuer gemischten gas-aussenluftbetrieb (zentralheizung)
NL1020944C2 (nl) * 2002-06-26 2003-12-30 Gastec Technology B V Verwarmingsinrichting en werkwijze voor ruimteverwarming en/of sanitairwaterverwarming.
US20140137813A1 (en) * 2012-11-19 2014-05-22 General Electric Company Waste heat capture from a dual fuel gas and electric water heater
WO2016066153A1 (fr) * 2014-10-29 2016-05-06 Josef Reiter Installation de chauffage
ITUB20155279A1 (it) * 2015-10-16 2017-04-16 Zocca Lavori Edili S A S Di Zocca Mattia & C Gruppo di scarico dei fumi di combustione di una stufa o simile
WO2018056891A1 (fr) * 2016-09-26 2018-03-29 Flue Gas Recovery Sweden Ab Système et procédé de traitement de gaz de combustion
CN108019940A (zh) * 2017-12-05 2018-05-11 合山锌业科技有限公司 多燃料导热油炉
EP3361178B1 (fr) * 2017-01-26 2021-03-10 Kamax GmbH Procédé et installation de chauffage et/ou de refroidissement d'espaces
DE102019220038A1 (de) * 2019-12-18 2021-06-24 Robert Bosch Gmbh Wärmepumpensystem mit Komponenten einer Wärmepumpe

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE9304144L (sv) * 1993-12-13 1995-06-14 Aaps En Ab Värmeanläggning
AT411099B (de) * 2001-08-16 2003-09-25 Vaillant Gmbh Heizanlage mit einer adsorptionswärmepumpe

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2524085A1 (de) * 1975-05-30 1976-12-09 Erich Gross Auffangbehaelter fuer abwasser
DE2620395A1 (de) * 1976-05-08 1977-11-17 Wilhelm Emmerich Waermerueckgewinnungsanlage
DE2629345A1 (de) * 1976-06-30 1978-01-12 Krupp Gmbh Waermepumpe
DE2647216A1 (de) * 1976-10-15 1978-04-20 Hermann Holland Verfahren zur heizwaermeversorgung mittels waermepumpe und heizkessel
DE2822808A1 (de) * 1977-05-25 1978-11-30 Leif Eriksson Vorrichtung zum kuehlen von kamingasen
DE2728722A1 (de) * 1977-06-25 1979-01-04 Hartmut Behrens Verfahren und vorrichtung zur waermerueckgewinnung
DE2730123A1 (de) * 1977-07-04 1979-01-11 Werner Sahl Maximale spar-energie-anlage fuer den auffang und die verwertung der ungenutzten abwaerme, energie-ersparnis ca. 50 %
DE2747620A1 (de) * 1977-10-24 1979-04-26 Buderus Ag Waermepumpe
DE2748252A1 (de) * 1977-10-27 1979-05-03 Siemens Ag Verfahren zum regeln des verfluessigungsdruckes im kaeltemittelkreislauf einer waermepumpe
DE2758181A1 (de) * 1977-12-27 1979-07-05 Schako Metallwarenfabrik Vorrichtung zur rueckgewinnung der abgaswaerme von heizungsfeuerungen
DE2811586A1 (de) * 1978-03-17 1979-09-27 Motan Gmbh Heizanlage

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2524085A1 (de) * 1975-05-30 1976-12-09 Erich Gross Auffangbehaelter fuer abwasser
DE2620395A1 (de) * 1976-05-08 1977-11-17 Wilhelm Emmerich Waermerueckgewinnungsanlage
DE2629345A1 (de) * 1976-06-30 1978-01-12 Krupp Gmbh Waermepumpe
DE2647216A1 (de) * 1976-10-15 1978-04-20 Hermann Holland Verfahren zur heizwaermeversorgung mittels waermepumpe und heizkessel
DE2822808A1 (de) * 1977-05-25 1978-11-30 Leif Eriksson Vorrichtung zum kuehlen von kamingasen
DE2728722A1 (de) * 1977-06-25 1979-01-04 Hartmut Behrens Verfahren und vorrichtung zur waermerueckgewinnung
DE2730123A1 (de) * 1977-07-04 1979-01-11 Werner Sahl Maximale spar-energie-anlage fuer den auffang und die verwertung der ungenutzten abwaerme, energie-ersparnis ca. 50 %
DE2747620A1 (de) * 1977-10-24 1979-04-26 Buderus Ag Waermepumpe
DE2748252A1 (de) * 1977-10-27 1979-05-03 Siemens Ag Verfahren zum regeln des verfluessigungsdruckes im kaeltemittelkreislauf einer waermepumpe
DE2758181A1 (de) * 1977-12-27 1979-07-05 Schako Metallwarenfabrik Vorrichtung zur rueckgewinnung der abgaswaerme von heizungsfeuerungen
DE2811586A1 (de) * 1978-03-17 1979-09-27 Motan Gmbh Heizanlage

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0070560A2 (fr) * 1981-07-21 1983-01-26 Laurentius Pohlmeyer Installation pour réchauffer de l'eau
EP0070560A3 (fr) * 1981-07-21 1983-08-03 Laurentius Pohlmeyer Installation pour réchauffer de l'eau
FR2518229A1 (fr) * 1981-12-14 1983-06-17 Dietrich De Ensemble de production de chaleur bi-energie
WO1983003662A1 (fr) * 1982-04-14 1983-10-27 KASTRÖM, Per-Olof Installation de chauffage
DE3218727A1 (de) * 1982-05-18 1983-11-24 Viessmann Hans Heizungsgeraet
EP0099441A2 (fr) * 1982-07-21 1984-02-01 Paolo Curti Appareil pour la récupération de chaleur de fumées dans une installation de chauffage ou d'air ambiant
EP0099441A3 (en) * 1982-07-21 1984-09-12 Paolo Curti Apparatus for recovery of heat from fumes in a heating system or from the ambient air
GB2142136A (en) * 1983-06-01 1985-01-09 Star Refrigeration Heating apparatus including a heat pump
US4512288A (en) * 1983-07-15 1985-04-23 Roger Michaud Furnace heat exchanger
DE3516072A1 (de) * 1985-05-04 1986-11-06 Morgenschweis, Thomas, 5900 Siegen Heizsystem mit waermepumpe, fuer gemischten gas-aussenluftbetrieb (zentralheizung)
NL1020944C2 (nl) * 2002-06-26 2003-12-30 Gastec Technology B V Verwarmingsinrichting en werkwijze voor ruimteverwarming en/of sanitairwaterverwarming.
EP1376025A1 (fr) * 2002-06-26 2004-01-02 GASTEC Technology B.V. Apparei de chauffage et méthode pour chauffer un espace et/ou de l'eau sanitaire
US20140137813A1 (en) * 2012-11-19 2014-05-22 General Electric Company Waste heat capture from a dual fuel gas and electric water heater
WO2016066153A1 (fr) * 2014-10-29 2016-05-06 Josef Reiter Installation de chauffage
ITUB20155279A1 (it) * 2015-10-16 2017-04-16 Zocca Lavori Edili S A S Di Zocca Mattia & C Gruppo di scarico dei fumi di combustione di una stufa o simile
WO2018056891A1 (fr) * 2016-09-26 2018-03-29 Flue Gas Recovery Sweden Ab Système et procédé de traitement de gaz de combustion
EP3361178B1 (fr) * 2017-01-26 2021-03-10 Kamax GmbH Procédé et installation de chauffage et/ou de refroidissement d'espaces
CN108019940A (zh) * 2017-12-05 2018-05-11 合山锌业科技有限公司 多燃料导热油炉
CN108019940B (zh) * 2017-12-05 2020-01-21 合山锌业科技有限公司 多燃料导热油炉
DE102019220038A1 (de) * 2019-12-18 2021-06-24 Robert Bosch Gmbh Wärmepumpensystem mit Komponenten einer Wärmepumpe

Also Published As

Publication number Publication date
EP0013018B1 (fr) 1984-06-27
SE7909528L (sv) 1980-06-23
NO152268C (no) 1985-08-28
NO793745L (no) 1980-06-24
FI793650A (fi) 1980-06-23
SE438547B (sv) 1985-04-22
DK547979A (da) 1980-06-23
NO152268B (no) 1985-05-20
CA1120465A (fr) 1982-03-23

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