EP3414493A1 - Procédé et dispositif de transfert d'énergie thermique à un consommateur d'énergie thermique d'une installation de chauffage - Google Patents

Procédé et dispositif de transfert d'énergie thermique à un consommateur d'énergie thermique d'une installation de chauffage

Info

Publication number
EP3414493A1
EP3414493A1 EP17703922.9A EP17703922A EP3414493A1 EP 3414493 A1 EP3414493 A1 EP 3414493A1 EP 17703922 A EP17703922 A EP 17703922A EP 3414493 A1 EP3414493 A1 EP 3414493A1
Authority
EP
European Patent Office
Prior art keywords
heat
flow path
section
hollow body
heat transfer
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.)
Pending
Application number
EP17703922.9A
Other languages
German (de)
English (en)
Inventor
Andreas LANGGARTNER
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.)
QUIMAX GMBH
Original Assignee
Kamax GmbH
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
Priority claimed from DE102016001373.7A external-priority patent/DE102016001373A1/de
Priority claimed from DE102016001374.5A external-priority patent/DE102016001374A1/de
Application filed by Kamax GmbH filed Critical Kamax GmbH
Publication of EP3414493A1 publication Critical patent/EP3414493A1/fr
Pending legal-status Critical Current

Links

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
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/0027—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters using fluid fuel
    • 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
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/40—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes
    • F24H1/43—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes helically or spirally coiled
    • 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
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/44—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with combinations of two or more of the types covered by groups F24H1/24 - F24H1/40 , e.g. boilers having a combination of features covered by F24H1/24 - F24H1/40
    • F24H1/445—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with combinations of two or more of the types covered by groups F24H1/24 - F24H1/40 , e.g. boilers having a combination of features covered by F24H1/24 - F24H1/40 with integrated flue gas condenser
    • 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
    • F24H8/00—Fluid heaters characterised by means for extracting latent heat from flue gases by means of condensation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]

Definitions

  • the invention relates to a method for transferring heat energy to a heat consumer of a heating system from a heat energy source having a temperature above an operating temperature range of the heat consumer and to a device suitable for carrying out this method.
  • Such methods and devices find application, for example, in heating systems in which the heating energy source is a burner for gaseous, liquid or solid fuel, is heated by the heating water in a boiler and passed through the primary side through a heat exchanger in an external circuit. Heat is transferred to a secondary heating circuit or hot water circuit in this heat exchanger.
  • the energy efficiency of such a process depends on various factors, including in particular the operating temperatures of the circuits involved.
  • the invention has for its object to provide a method of the type mentioned above, which has a high energy efficiency, and to provide a device suitable for carrying out the method.
  • this object is achieved with respect to the method in that the heat transfer takes place in a refrigerant circuit in which a liquid phase of a refrigerant is transferred with a lying below the operating temperature range of the heat consumer low temperature by absorbing heat from the heating energy source in a vapor phase, the vapor phase is compressed under temperature increase to a lying above the operating temperature range of the heat consumer high temperature, the compressed vapor phase is transferred by heat to the heat consumer in the liquid phase and the liquid phase is depressurized while lowering the temperature to the low temperature.
  • the refrigerant circuit of the method according to the invention thus extends over four sections.
  • a liquid phase of the refrigerant flows at a temperature lower than the operating temperature range of the heat consumer low temperature, for example, in a flow channel formed, for example, in a heated by the heating energy source combustion chamber, where it is absorbed by heat from the heating energy source in a vapor phase transferred.
  • This compressed vapor phase flows into the subsequent third section, which is located, for example, in the primary circuit of a heat exchanger, where it is transferred to the liquid phase by dissipation of heat to the heat consumer lying, for example, in the secondary circuit of the heat exchanger.
  • the latter flows into the subsequent fourth section where it is substantially adiabatically depressurized to the low temperature, for example by means of a throttle valve, and flows back into the adjoining first section of the refrigerant circuit, from where the refrigerant passes through the entire cycle again.
  • the temperature difference between the temperature of the heating energy source and the low temperature of the liquid phase of the refrigerant heated by it is greater than the temperature difference between the temperature of the heating energy source and the operating temperature range of the heat consumer. Due to this larger temperature difference, the heat transfer takes place with higher efficiency than in a direct heat exchange between the heat energy source and a thermally coupled to the heat consumer heat transfer medium. Likewise, the heat dissipation to the heat consumer due to the high temperature achieved by the compression takes place with a relatively high temperature difference, whereby the efficiency of the heat output is increased.
  • the maximum flow temperature for example, 60 ° C, 50 ° C, 40 ° C or 35 ° C. , so that thereby the operating temperature range is limited upwards accordingly.
  • the temperature of the liquid phase of the refrigerant supplied for absorbing heat is below 0 ° C., in particular below -10 ° C. or -20 ° C. or -30 ° G or -40 ° C.
  • the low temperature of the liquid phase supplied for heat absorption is below 0 ° C., in particular in the range from -10 ° C. to -25 ° C.
  • the process control can continue to be such that the temperature of the vapor phase generated by the heat absorption in the range of 45 ° C to 80 ° C.
  • caused by the compression high temperature of the compressed vapor phase is above 100 ° C. In particular, it is 110 ° C or more, preferably 120 ° C or more.
  • the temperature of the heating energy source above 1000 ° C, especially at
  • 1400 ° C lies. In these temperature ranges are, for example, the operating temperatures of burners for gaseous, liquid or solid fuels.
  • Suitable refrigerants for carrying out the process are in particular propane or butane or suitable mixed gases, such as R134a, R407c or the like.
  • the transfer of the refrigerant into the vapor phase takes place in a section of the refrigerant circuit which is arranged in the region of a chamber wall surrounding the heat energy source.
  • the chamber wall surrounds the flame of a solid, liquid or gaseous fuel burner forming the heating energy source, whereby the thermal energy released from the burner is effectively transferred to the refrigerant circulating in the refrigerant circuit.
  • a further expedient embodiment of the method according to the invention is characterized in that the transfer of the compressed vapor phase into the liquid phase takes place in a section of the refrigerant circuit comprising a heat exchanger with a first circuit section located in the refrigerant circuit and in thermal contact with it Having heat transfer medium flowed through the second cycle section.
  • the vaporous phase lying at the high temperature flows through the first cycle section and releases heat energy to the second cycle section through which the heat transfer medium flows, the temperature of the heat transfer medium being within the operating temperature range of the heat consumer.
  • the heat transfer medium is water and then corresponds in function to the heating water of conventional boiler.
  • the object underlying the invention is achieved by a device for transmitting heat energy to a heat consumer of a heating system from a lying over an operating temperature range of the heat consumer temperature having heating energy source, which is characterized by a refrigerant circuit having a first portion in which a Under the operating temperature range of the heat consumer low temperature lying liquid phase of a refrigerant can be converted by heat absorption from the heating energy source in a vapor phase, a second section following the first section, in which the vapor phase with temperature increase to a lying above the operating temperature range of the heat consumer high Temperature is compressible, following the second section following third section in which the compressed vapor phase by Malawia Transfer to the heat consumer in the liquid phase can be transferred, and on the third section following and leading to the first section fourth section, in which the liquid phase is depressurable while lowering the temperature to the low temperature.
  • this design can be realized by means of a device for transferring heat energy from a combustion chamber formed in a hollow body to a heat transfer medium of a heating system with a heated by the combustion chamber in the energy released flow path for the heat transfer medium and a flow path for the withdrawal of exhaust gas from the combustion chamber be formed in the integrally with a combustion chamber transverse to a longitudinal axis of the hollow body bounding the first wall portion of the hollow body, a first portion of the flow path for the heat transfer medium radially inwardly and in a radially outward distance thereto, a first portion of the flow path for the exhaust gas is formed.
  • the first wall section of the hollow body forms a jacket enclosing the combustion chamber with respect to its longitudinal axis in an azimuthal manner. This is heated from the inside by the energy released in the combustion chamber.
  • the heating energy is transferred to the latter efficiently.
  • the one-piece design of the first portion of the flow path with the first wall portion of the hollow body may be designed such that the first portion of the flow path in the form of a corresponding surface structure on the inside of the first wall portion of the hollow body can be seen.
  • the first section of the flow path for the heat transfer medium can also be embedded near the surface completely in the wall section of the hollow body so that it is imperceptible when looking at the inside of the wall section.
  • the integrally formed with the first wall portion of the hollow body first portion of the flow path for the exhaust gas is disposed radially outside of the first portion of the flow path for the heat transfer medium, wherein it surrounds the latter in particular jacket-shaped.
  • this first portion of the flow path for the exhaust gas promotes the thermal separation of the inner first portion of the flow path for the heat transfer medium from the outside of the hollow body.
  • the first wall portion of the hollow body has an inner shell-shaped region in which the first portion of the flow path for the heat transfer medium is formed, and a radially spaced outer shell-shaped region in which the first portion of the flow path for the exhaust gas is formed.
  • the production of the thus structured hollow body can be advantageously carried out by generative manufacturing.
  • this process includes the so-called “3D printing”, preferably 3D printing with powder (3DP), selective laser sintering (SLS) and electron beam melting (EBM / EBAM).
  • the device according to the invention is connected to an external Schuziernik für assuesue to operate the first portion of the flow path for the heat transfer medium in a refrigerant circuit.
  • an external Schuziernik für assue over the return of which is cooled by the release of useful heat heating water is supplied to the first portion of the flow path for the heat transfer medium and its flow in the first section of the flow path for the heat transfer medium heated up Heating water is discharged.
  • a more advantageous mode of operation is to operate the first portion of the flow path for the heat transfer medium in a refrigerant circuit.
  • the heat transfer takes place in that a liquid phase of a refrigerant with a below the operating temperature range in which the useful heat of the heating system is discharged, low temperature by heat absorption during passage through the formed in the first wall portion of the hollow body first portion of the flow path in a vapor phase is transferred, the vaporous phase is compressed with increasing temperature to a high temperature lying above this temperature range, the compressed vapor phase is transferred by Nutztudeabgabe into the liquid phase and the liquid phase depressurized to the low temperature and relaxed in the Hollow body formed first portion of the flow path is returned.
  • the heat transfer takes place with particularly high efficiency.
  • the low temperature of the intended for the heat absorption liquid phase of the refrigerant may be below 0 ° C, in particular in the range of -10 ° C to -25 ° C.
  • the high temperature of the intended for the Nutztudeabgabe vapor phase may be above 40 ° C, in particular in the range of 45 ° C to 80 ° C, lie.
  • this operation can be realized by means of the method according to the invention.
  • the further embodiment of the device according to the invention may suitably be effected in that an external section of a refrigerant circuit is connected to the first section of the flow path for the heat transfer medium.
  • This second wall section thus forms an end-side cover, which closes the hollow body to the outside and bounded on its inside the second portion of the flow path for the exhaust gas, in which section both the combustion chamber and formed in the first wall portion first portion of the flow path for the Exhaust flows.
  • the exhaust gas produced in the combustion chamber enters this second section of the flow path and flows there in a substantially radially outward direction into the essentially axially extending first section of the flow path for the exhaust gas.
  • the second wall section of the hollow body is arranged vertically below.
  • the hollow body has an integrally formed with the first wall portion second wall portion which extends from a first axial end portion of the first wall portion of transverse to the longitudinal axis and the one with both the combustion chamber and The first portion of the flow path for the exhaust gas related second portion of the flow path for the exhaust limited.
  • This third wall portion thus forms a hollow body at its end opposite the second wall portion end frontal lid, which is arranged vertically above in the preferred mounting position of the device.
  • the areas at which the first and the second portion and the second and the third portion of the flow path for the exhaust gas communicate with each other designed flow-obstacle-free.
  • the flow of the exhaust gas along its flow path opposes no additional flow resistance.
  • the device is expediently further designed such that the flow path for the heat transfer medium has a continuation section adjoining the first section thereof, which leads out of the hollow body through the second or third wall section of the hollow body.
  • both the fluidically input side end of the first portion of the flow path for the heat transfer medium and the fluidic output side end each have such a continuation section.
  • one of these ends of the first section of the flow path for the heat transfer medium is arranged near the second or third wall section of the hollow body, wherein in particular the fluidically input side end near the second wall portion and the fluidic output side end is disposed near the third wall portion of the hollow body.
  • Each of the continuation portions integrally formed with the hollow body is led out through the second or third wall portion of the hollow body to the outside and thereby allows a connection to an external circuit.
  • connection opening for serving for firing the combustion chamber Burner is formed in the third wall portion of the hollow body.
  • this connection opening has a central axis which is congruent with the longitudinal axis of the hollow body. Since the third wall section delimits the combustion chamber at one of its axial ends, in particular its vertically upper axial end, the flame of the burner serving for firing the combustion chamber then extends within the combustion chamber in the direction of the longitudinal axis of the hollow body.
  • a further advantageous embodiment is that in the second wall portion of the hollow body, an opening for discharging a liquid condensate of the exhaust gas is formed.
  • the liquid condensate which is obtained when the exhaust gas is cooled below the dew point and water and other condensable substances of the exhaust gas, to remove from the device.
  • the second wall portion of the hollow body forms the lower end, there is the accumulation of the condensate instead.
  • one end of an external siphon is connected to the opening, at the other end a suitable operating pressure is set.
  • a further flow path is formed for a further heat transfer medium.
  • This further flow path is preferably in the form of a meander of straight sections which extend parallel to the longitudinal axis, and the rectilinear sections at their respective axial ends connecting portions which extend transversely to the longitudinal axis formed.
  • this heat exchange with the exhaust gas can be made particularly efficient by the fact that an external section of a further refrigerant circuit is connected to the further flow path for a further heat transfer medium.
  • the function of this further refrigerant circuit corresponds to the function of the refrigerant circuit described above, in which the refrigerant flows through the radially inner portion of the flow path for the heat transfer medium. This means that a liquid phase of the refrigerant evaporates when passing through the further flow path, then compressed along the external portion of the further refrigerant circuit with temperature increase, liquefied under Nutztudeabgabe, relaxed under temperature lowering and returned to the other flow path.
  • the temperature of the exhaust gas can thereby be lowered as it passes through its flow path, for example, to a range of -15 ° C to 15 ° C.
  • the first wall section of the hollow body has a cylinder-shaped basic shape whose cylinder axis corresponds to the longitudinal axis of the hollow body.
  • the rotational symmetry of this basic shape takes into account in particular the shape of the flame of the burner which heats the combustion chamber in the direction of the longitudinal axis.
  • a sufficiently large heat exchanger surface can be achieved in that the first portion of the flow path for the heat transfer medium is formed in the form of a coil. It is particularly favorable for the heat transfer that the shape of a coil having the first portion of the flow path for a heat transfer medium is formed on the combustion chamber facing free inner surface of the first wall portion.
  • the tube coil is designed in the form of a helical coil whose screw axis corresponds to the longitudinal axis of the hollow body.
  • the first portion of the flow path for the exhaust gas has a heat-conducting structure projecting in its cross section.
  • this structure may be ribs projecting into the cross-section, which ribs may be inclined in particular with respect to the flow direction of the exhaust gas.
  • the direction in which the ribs extend encloses an acute angle with the flow direction of the exhaust gas.
  • an end-face lattice structure is formed, which preferably has the shape of a dome towards the combustion chamber dome.
  • the burner flame can not pass. It also promotes the dissipation of heat to the hollow body and causes a cooling of the burner flame. As a result, the amount of nitrogen oxides (NOx) produced during combustion is reduced.
  • Fig. 1 is a schematic diagram of the sequence of a method for transferring heat energy from a heating energy source to a heat consumer of a heating system
  • Fig. 2 shows an embodiment of a device suitable for carrying out the method.
  • a refrigerant for example propane or butane, circulates in a refrigerant circuit 100 which has four sections connected in series.
  • a refrigerant circuit 100 which has four sections connected in series.
  • the first section 101 flows a heat flow Q 0 from a heating energy source, not shown, for example, a heating burner to a provided in the first section 101 evaporator 102, at its inlet side 103, a liquid phase of the refrigerant flows and in the evaporator 102 by absorbing heat from the heat flow Q 0 is converted into a vapor phase, which may also be overheated.
  • This vaporous phase flows from the exit side 104 of the evaporator 102 into the second section 105 following the first section 101, in which a compressor 106 is provided, through which the vaporous phase is compressed substantially adiabatically with an increase in temperature.
  • the compressed vapor phase flows from the outlet side 107 of the compressor 106 into the third section 108, in which a condenser 109 is provided. From the condenser 109 flows a heat flow Q to a heat consumer, not shown, a heating system. By the heat transfer to the heat consumer, the condensed vapor phase of the refrigerant entering the condenser 109 is transferred into its liquid phase. This liquid phase flows from the outlet side 110 of the condenser 109 into the fourth section 111, in which an expansion valve 112 is provided, with which the liquid phase is substantially adiabatically depressurized and returned to the inlet side 103 of the evaporator 102.
  • the temperature of the heating energy source is much higher than the low temperature of the liquid phase of the refrigerant entering the evaporator 102. Therefore, there is a large, the heat flow Q 0 driving temperature gradient.
  • the high temperature of the condensed vapor phase of the refrigerant entering the condenser 109 is, in particular, considerably higher than the temperature of the heat consumer in heat exchange with the condenser 109, see above that the heat flow Q, which causes the heat to the heat consumer, is driven by a relatively high temperature gradient.
  • the heating energy source is a gaseous, liquid or solid fuel heating burner
  • its temperature is above 000 ° C and more particularly in the region of 1400 ° C.
  • the method may be performed such that the low temperature of the liquid phase of the refrigerant supplied to the evaporator 102 is below 0 ° C, especially in the range of -10 ° C to -25 ° C.
  • the temperature of the effluent from the evaporator 102 vapor phase may be in the range of 45 ° C to 80 ° C.
  • FIG. 2 An example of a device design of the evaporator 102 having the first portion of the refrigerant circuit 100 is shown in Fig. 2.
  • the device shown has a longitudinal axis 1 having a hollow body 2, which is shown in Fig. 2 in a longitudinal axis 1 through the longitudinal section.
  • a combustion chamber 3 is bounded transversely to the longitudinal axis 1 by a first wall section 4 of the hollow body 2, wherein in the illustrated embodiment, the first wall section 4 has the basic shape of a cylinder jacket whose cylinder axis coincides with the longitudinal axis 1 of the hollow body 2.
  • first axial end portion 5 of the first wall portion 4 of a second wall portion 6 of the hollow body 2 extends transversely to its longitudinal axis 1 and thereby forms a decker-shaped lower end of the hollow body 2.
  • first axial end portion 5 opposite second axial end portion 7 of a third wall portion 8 transverse to the longitudinal axis 1 of the hollow body 2, which forms a hollow body 2 top closing lid.
  • the first, second and third wall sections 4, 5 and 6 are formed integrally with each other.
  • a tube coil is formed integrally with the first wall section 4 radially inside, wherein in the illustrated embodiment, this coil 9 is formed in the form of a helical coil whose screw axis coincides with the longitudinal axis 1 of the hollow body 2.
  • the coil 9 forms a first portion of a flow path for a heat transfer medium, which may be in particular a refrigerant.
  • the second wall section 6 adjacent end 10 of the coil 9 has an integrally formed therewith continuation section 11 which extends in the axial direction through the second wall section 6 and the inlet side 103 of the evaporator 102 in Fig. 1 forms.
  • the third wall section 8 adjacent axial end 12 of the coil 9 is provided with an integrally formed therewith continuation portion 13 which extends in the axial direction through the third wall portion 8 and forms the outlet side of the evaporator 104.
  • a first section 14 of a flow path for the exhaust gas formed in the combustion chamber 3 is formed at a small radial distance from the coil 9, which extends over the entire axial length of the first wall section 4 in the embodiment shown in FIG and is annular in its longitudinal direction to the longitudinal axis 1 orthogonal radial section.
  • This first section 14 flows at its lower in FIG. 2, the first axial end portion 15 into a second section 16 which extends between the inner side 6 'of the second wall portion 6 and the axial end 3' of the combustion chamber 3 and to the combustion chamber. 3 is open.
  • the first portion 14 of the exhaust flow path in its upper axial end portion 17, shown in FIG. 2 merges into a third portion 18 formed in the third wall portion 8.
  • the third section 18 is closed towards the upper axial end 3 "of the combustion chamber 3 and is guided to the outside at an outer terminal 19 formed on the third wall section 8.
  • connection opening 20 for a burner 21.
  • the third wall section 8 opposite the second wall section 6 has a central exhaust port 22 for exhaust gas condensate in the illustrated embodiment, which opens into an outer terminal 23.
  • a dome-shaped lattice structure 27 which is curved towards the combustion chamber 3, rises, which radially overlaps the discharge opening 22.
  • the lattice structure cools the flame by heat dissipation and thereby prevents the formation of nitrogen oxides during combustion.
  • the flame of the burner 21 extends in the combustion chamber 3 along the longitudinal axis 1.
  • the resulting in the combustion chamber exhaust gas passes from the lower axial end 3 'of the combustion chamber 3 in the second section 16 of the flow path for the exhaust gas and continues to flow through the first section 14 in the third section 18, from where it is discharged to the outer terminal 19.
  • the first portion 14 of the flow path for the exhaust gas has a heat-conducting structure projecting in its cross-section. This consists in the illustrated embodiment of ribs 24, which are inclined in the following in Fig. 2 upward flow direction of the exhaust gas following upwards.
  • a further flow path 25 for a further heat transfer medium is formed integrally with the hollow body 2 in the first wall section 4.
  • This further flow path is applied, for example, in the form of a meander of axially extending channels 26, the adjacent axial ends, with the exception of the beginning and end of the meander, in pairs by transverse to the longitudinal axis extending portions which are not shown in the drawing with each other are connected. It represents a section of a closed circuit outside the hollow body 2, in which the heat transfer medium circulating therein removes heat from the exhaust gas within the hollow body 2 and discharges outside the hollow body 2 to the heat consumer, for example to the return of a hot water line.
  • the capacitor 109 of the third section 108 may be formed as a heat-emitting flow path of a heat exchanger whose heat-receiving flow path is flowed through by a heat transfer medium, which causes the heat transfer to the heat consumer of the heating system.
  • this heat transfer medium may be water.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un procédé et un dispositif de transfert d'énergie thermique à un consommateur d'énergie thermique d'une installation de chauffage, caractérisés en ce que selon l'invention le transfert thermique s'effectue dans un circuit de refroidissement (100).
EP17703922.9A 2016-02-08 2017-02-06 Procédé et dispositif de transfert d'énergie thermique à un consommateur d'énergie thermique d'une installation de chauffage Pending EP3414493A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102016001373.7A DE102016001373A1 (de) 2016-02-08 2016-02-08 Verfahren und Vorrichtung zur Übertragung von Wärmeenergie an einen Wärmeverbraucher einer Heizungsanlage
DE102016001374.5A DE102016001374A1 (de) 2016-02-08 2016-02-08 Vorrichtung zur Übertragung von Wärmeenergie an ein Wärmeträgermedium einer Heizungsanlage
PCT/EP2017/000165 WO2017137159A1 (fr) 2016-02-08 2017-02-06 Procédé et dispositif de transfert d'énergie thermique à un consommateur d'énergie thermique d'une installation de chauffage

Publications (1)

Publication Number Publication Date
EP3414493A1 true EP3414493A1 (fr) 2018-12-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP17703922.9A Pending EP3414493A1 (fr) 2016-02-08 2017-02-06 Procédé et dispositif de transfert d'énergie thermique à un consommateur d'énergie thermique d'une installation de chauffage

Country Status (2)

Country Link
EP (1) EP3414493A1 (fr)
WO (1) WO2017137159A1 (fr)

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DE102014213624A1 (de) * 2014-07-14 2016-01-14 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Verfahren zur herstellung eines strömungskanals

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