WO2009100924A2 - Système de chauffage produisant du courant - Google Patents

Système de chauffage produisant du courant Download PDF

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Publication number
WO2009100924A2
WO2009100924A2 PCT/EP2009/001023 EP2009001023W WO2009100924A2 WO 2009100924 A2 WO2009100924 A2 WO 2009100924A2 EP 2009001023 W EP2009001023 W EP 2009001023W WO 2009100924 A2 WO2009100924 A2 WO 2009100924A2
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WO
WIPO (PCT)
Prior art keywords
heat
energy
heating system
thermodynamic
heating
Prior art date
Application number
PCT/EP2009/001023
Other languages
German (de)
English (en)
Other versions
WO2009100924A3 (fr
Inventor
Gerhard Schilling
Original Assignee
Dynatronic 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
Application filed by Dynatronic Gmbh filed Critical Dynatronic Gmbh
Priority to CA2714644A priority Critical patent/CA2714644A1/fr
Priority to EP09710656A priority patent/EP2252835A2/fr
Priority to AU2009214266A priority patent/AU2009214266A1/en
Priority to US12/867,132 priority patent/US20110101119A1/en
Priority to CN2009801122107A priority patent/CN102047044A/zh
Publication of WO2009100924A2 publication Critical patent/WO2009100924A2/fr
Publication of WO2009100924A3 publication Critical patent/WO2009100924A3/fr

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Classifications

    • 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
    • F24D11/002—Central heating systems using heat accumulated in storage masses water heating system
    • F24D11/003—Central heating systems using heat accumulated in storage masses water heating system combined with solar energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • 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
    • F24D18/00—Small-scale combined heat and power [CHP] generation systems specially adapted for domestic heating, space heating or domestic hot-water supply
    • 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
    • F24D2101/00—Electric generators of small-scale CHP systems
    • F24D2101/40—Photovoltaic [PV] modules
    • 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
    • F24D2103/00—Thermal aspects of small-scale CHP systems
    • F24D2103/10—Small-scale CHP systems characterised by their heat recovery units
    • F24D2103/13—Small-scale CHP systems characterised by their heat recovery units characterised by their heat exchangers
    • 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
    • F24D2103/00—Thermal aspects of small-scale CHP systems
    • F24D2103/10—Small-scale CHP systems characterised by their heat recovery units
    • F24D2103/17—Storage tanks
    • 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
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/04—Gas or oil fired boiler
    • 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
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/14—Solar energy
    • 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
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/20—Solar thermal
    • 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
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/70—Hybrid systems, e.g. uninterruptible or back-up power supplies integrating renewable energies
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the invention relates to a heating system for an object, with a controller controlled by a thermal coupling of a thermal heat generator, in particular a conventional heating system, with multiple heat consumers for simultaneous heat and power production, one of the heat consumer on a thermodynamic cycle, in particular a steam or ORC or Kalina process, based conversion system for the conversion of thermodynamic energy into electrical energy and the heat of condensation occurring in the thermodynamic cycle is transferred to other heat consumers,
  • the brochure "Short info: Lion ® Powerblock” (as of October 2007) of OTAGmaschines GmbH & Co. KG, Olsberg (http://www.otag.de/download/071007_Lion_ Kurzinfo_2007_E.pdf), is a heating system for residential properties
  • the essential components of this system are a gas burner, a steam-based thermodynamic cycle consisting of a tube evaporator and a heat exchanger for condensing the water vapor and for transferring the heat of condensation to the heating circuit.
  • the steam supply to the working chamber of the free piston is controlled mechanically via slides, which are firmly connected to the piston rod and depending on the piston position and Piston speed the inlet for a besti Open and close the time that can not be controlled.
  • the heating system should be able to effectively use the heat energy from solar thermal collectors available in excess in summer to generate electricity; - The heating system should be able to automatically adjust the condensation temperature of the thermodynamic cycle to the existing variable low temperature level, such. B. heating return temperatures to adjust to achieve a maximum temperature spread; and
  • the power plant should not belong to any kind of firing system
  • Be bound gas, oil, pellets, etc.
  • a) only one heat generator a conventional heating system, designed to achieve the high temperatures required in the thermodynamic process, as a gas heater;
  • the heating system is combined with a thermally coupled heat accumulator in which the heating heat produced by the heating system can be temporarily stored and forwarded to a heat consumer with a time delay.
  • the balance between the thermal energy production and the thermal energy requirement results from the following formula:
  • E heating (t) + Espou ⁇ (t) Eww (t) + E HW (t) + E TH D Y (t) + E Sp ⁇ N (t)
  • the system has only one operating mode in which electricity is simultaneously produced by means of a conversion system from thermodynamic to electrical energy and that the heat accumulator is filled with the heat of condensation arising in the thermodynamic process;
  • thermodynamic cycle is based on a single-stage steam cycle
  • thermodynamic into electrical energy takes place either by means of a combination of a DC steam engine with a linear generator in a design with two counter-rotating pressure cylinders, as used in conventional free-piston systems, while always a working space is unused and alternately always only one pressure cylinder the power stroke performs.
  • the performance of the conversion system over the repetition frequency of the power strokes is adjustable, but due to a lack of control of the intake volume per stroke, the conversion system can be realized only with a constant ratio of inlet pressure to outlet pressure, which in turn leads to that of the outlet pressure dependent condensation temperature the thermodynamic cycle is not adjustable;
  • thermodynamic efficiency there is currently no working medium known with which a thermodynamic process in this required temperature range is technically feasible and its thermodynamic properties also allow high efficiency in power generation.
  • water In addition to the disadvantageously high boiling point, water also has the property of requiring high superheating of the steam to permit expansion with dry steam, which adversely affects thermodynamic efficiency;
  • the problem to be solved is how the various heat generators, heat storage and heat consumers can be thermally coupled with each other most favorably.
  • the heating system can be operated in at least one of two operating modes, wherein in the first operating mode the heat generated is fed to the thermodynamic cycle process for the production of electricity and the residual heat resulting from the thermodynamic cycle Heating is used, and is produced in the second mode regardless of the heating demand electricity by a heat sink absorbs the heat of condensation of the thermodynamic process.
  • the invention primarily aims at a heating system for residential objects, with which the rooms of the object and / or the hot water of the object (heat consumers) are heated.
  • a system is proposed in which "on a small scale" (ie not in large-scale plant or power plant) a conventional heating system with a thermodynamic cycle, for example, with an ORC cycle (Organic Rankine Cycle) is combined to in this way a
  • ORC cycles Organic Rankine Cycle
  • the invention provides a heating system that overcomes the above-mentioned disadvantages of the prior art by one or more preferred measures and meets the additional requirements.
  • These preferred measures relate both to improvements in the basic system structure, as well as improvements in a need-based efficiency and cost-optimized design of each component, as well as an optimized overall system structure, which results from the additional requirements.
  • a special overall system consisting of a combination of the advantageous measures listed below leads to a preferred technical design of the heating system, which causes maximum energy efficiency in the conversion of thermodynamic into electrical energy due to the thermodynamic system design:
  • thermodynamic process in the low temperature range a thermal coupling to thermal solar collectors for solar power generation by means of a thermodynamic process in the low temperature range and to realize another mode of operation "solar electricity production” in which electricity is produced by means of thermal solar collectors.
  • a thermal coupling to an on-site exhaust heat recovery plant which is utilized to increase the efficiency of electricity production by means of a thermodynamic process in the low temperature range;
  • thermodynamic cycle with a high temperature circuit and a low temperature circuit, preferably both ORC circuits, generating electricity from both circuits;
  • the rotation system has a rotation generator, in particular an RMT generator;
  • the controller controls a power adjustment required due to the additional heat generators in the different operating modes, preventing the heating system from providing an adjustable power required, and the thermal equilibrium in the different operating modes is compensated either by power regulation in the conversion system from thermodynamic to electrical energy or by regulation of a storage flow Ps P i N (t) and thus over the Speicher- level of the heat storage;
  • thermodynamic cycle a maximum temperature spread between the temperature level medium before expansion (T THDY m) and the temperature level of a heat sink located on the object (T Ws ) is achieved.
  • a special high-temperature heating system in particular a biomass incineration plant, such as a wood pellet heating system, which medium outlet temperatures T H ut from above the boiling point of water allows, in particular with outlet temperatures from higher 300 0 C.
  • thermodyficant suitable for this temperature range is present in the ( ⁇ ⁇ Q T culinarym ⁇ oil N oin ⁇ r Uritie »r» Kor »Töm ⁇ roti tr above the outlet temperature of the high-temperature heating system required.
  • the power is recovered by means of the thermodynamic cycle process in that the working medium, preferably a coolant with a low boiling point, is evaporated, whereby the evaporation creates a high pressure. This can be taken in the form of volume change work in the expansion of the gas as mechanical kinetic energy and thereby converted into electrical energy.
  • thermodynamic cycle medium for.
  • ORC medium the shadow in addition to the required good istungseigen- also characterized by the fact that in the medium in the required low condensation temperature no negative pressure relative to the ambient pressure, since in the vacuum technically difficult in the long run avoiding penetrating air which reduces the efficiency thermodynamic cycle.
  • the lowest possible overheating of the vaporized gas should be necessary because the energy added during the overheating does not increase the energy yield of the thermodynamic cycle.
  • the controller directs the energy distribution and balances the thermal energy production with the thermal energy demand according to the formula
  • E H ei. (T) Eww (t) + E HW (t) + ETHDYO) + E remainder (t) due to periodically determined measurement data.
  • a valve-controlled piston engine with which the inlet and outlet times of each power stroke can be set separately and variably. This has the consequence that the expansion under the given conditions in each case takes place under optimum pressure conditions.
  • the inlet time the inlet volume is controlled and thus the outlet pressure of the medium after expansion, which in turn allows the temperature of the medium after the expansion of the thermodynamic cycle can be variably adjusted to the maximum required at the time of conversion temperature of the heat consumer , Ideally, then the condensation takes place of the medium also at this temperature level. It is therefore used from the available heat energy of the largest possible proportion under the given circumstances for power generation.
  • the balance between the thermal energy production and the thermal energy requirement is determined and set periodically by the controller preferably according to the following formula:
  • a further improvement in the energy recovery is achieved by a thermally coupled heat storage in which the heat produced by the heating system can be cached and forwarded to at least one heat consumer.
  • This thermal coupling allows the heating system to be put into operation for heating purposes only for a short time.
  • the heat storage also allows the use of solar energy both for heating purposes, as well as for solar power generation.
  • the heat storage is preferably an additively executed heat storage with different temperature levels (stratified storage), in which takes place both in the flow and in the return heat exchange each on a selectable, available in the heat storage best possible temperature level. In addition to the frequently used buffers other types of storage are conceivable, such. B.
  • thermochemical heat storage space-saving latent heat storage with a storage medium, which performs a phase change, preferably from solid to liquid, in the required storage temperature range, or a thermochemical heat storage.
  • the balance between the thermal energy generation and the thermal energy requirement is determined and adjusted periodically by the controller preferably according to the following formula:
  • E Hei z (t) + Espou ⁇ (t) Eww (t) + E HW (t) + E ⁇ HD ⁇ (t) + E Sp lN (t)
  • the controller independently sets the most favorable operation due to changes in the process control variables (such as the flow rate of the circuits, etc.) on the basis of data from sensors for recording process-influencing parameters. Due to sensor data, each heat exchange between individual components of the heating system is adjusted by regulating the occurring heat flows. that the most effective and complete transfer of heat energy of each warmer medium takes place on the respective colder. Also, the controller may incorporate information from an electricity supplier of the object into the control of the heating system to facilitate power production in particularly desirable periods of time.
  • the process control variables such as the flow rate of the circuits, etc.
  • the balance between the thermal energy production and the thermal energy requirement is determined and set periodically by the controller preferably according to the following formula:
  • E H e, 2 (t) + Espou ⁇ (t) Eww (t) + E HW (t) + E THD ⁇ (t) + E Sp IN (t) + E remainder (t)
  • the controller independently sets one or more of the following characterized operating modes:
  • the generator side of the equation can always be compensated for all operating modes by the use of a heating system that can be regulated in the power P He ⁇ z (t), which generates a constant high output temperature T H o ut , regardless of the required power with constant heat transfer efficiency.
  • the consumer side of the equation can always be balanced by a variable power flow rate of the thermodynamic conversion system P THDY O), which, however, additionally requires regulation of the condensation temperature. Furthermore, there is the possibility to regulate the heat storage capacity PspiN (t).
  • Espou ⁇ (t) Eww (t) + E H w (t)
  • thermodynamic conversion system While this mode of operation is active, the power flow rate P THDY O) of the thermodynamic conversion system is constant:
  • the operating mode is active until the heat storage level has exceeded an upper limit, and becomes active again as soon as a lower limit is reached.
  • thermodynamic conversion system While this mode of operation is active, the power flow rate P ⁇ HD ⁇ (t) of the thermodynamic conversion system is constant:
  • Heating power P He ⁇ z operate, this means:
  • a further possibility to realize a heating system with a constant heating power P H & Z ZU results when the outlet pressure constantly corresponds to the temperature level of the heat sink T Ws .
  • the resulting operating mode a) must therefore be replaced by a mode in which the heating system 2 thermal energy exclusively for use as heating heat and WW Heating produced, of course, the corresponding heat cycles are to be integrated.
  • this requires a conversion system with a variable conversion power P THDY O)
  • an advantage of this application is that the conversion system only has to convert a constant ratio of inlet pressure to outlet pressure and the power can be controlled via the repetition frequency f c y C .
  • An implementation is possible for example with a turbine or a DC steam engine.
  • a preferred option for power generation is a linear conversion system coupled to the thermodynamic cycle for converting thermodynamic energy into electrical energy with one or more pressure cylinders, a linear generator, a filtering and rectifying unit.
  • the linear conversion system provides for a thermodynamic cycle coupled and then specially tuned piston-cylinder unit for converting the thermodynamic energy first in kinetic energy, which then generates by means of a tuned specifically for this application linear generator electrical energy, which by means of a power converter is converted into an AC voltage suitable for feeding in the grid.
  • a suitable pressure cylinder linear generator arrangement is characterized by a high overall conversion efficiency, low production costs, silent operation as well as a long service life, since lateral and rotational forces do not exist.
  • a particular aspect of the conversion system is that by means of a valve-controlled piston engine, the inlet and outlet times of each power stroke can be set separately and variably.
  • inlet time is used to control the inlet volume and thus the outlet pressure of the medium after expansion, which in turn allows the temperature of the medium to decrease the expansion of the thermodynamic cycle can be variably adapted to the maximum temperature required at the time of conversion of the heat consumer.
  • the condensation of the medium also takes place at this temperature level. It is therefore used from the available heat energy of the largest possible proportion under the given circumstances for power generation.
  • thermodynamic pressure cylinder conversion system with variable conversion power P ⁇ HD ⁇ (t)
  • the conversion power is calculated from the product of the number of power strokes (Hub1 and Hub2) and the work performed on a piston stroke W THY and the clock frequency f Cyc :
  • the performed work W THDY is a function of the constant cylinder dimensions and the variable parameters: f (evaporation of vapor VEI ⁇ I.T
  • thermodynamic pressure cylinder conversion system can be changed by changing the clock frequency:
  • One way of making the clock frequency f cyc variable is to vary the rate of expansion and thus the expansion time t ⁇ p of a piston stroke by varying the induction force F
  • the clock frequency f Cyc is dependent on the expansion time t Exp . If after a work cycle immediately (without dead time) the opposite working cycle, then:
  • An electrically adjustable parameter of the linear generator is the coil inductance, which can be changed, for example, via an electrically selectable interconnection of coil pairs.
  • nd to design variable is the load current of the inverter se beispielswei- be regulated by the input resistance of the inverter.
  • This interface designed for example as a semiconductor path, allows a very fast and precise control of the induction force Fi n d during the expansion phase.
  • This in turn has the consequence that the combination of pressure cylinder and linear generator can be optimized in the design of the dimensions, since thus an optimal Operation can be enabled under the limiting factors of maximum acceleration and maximum piston speed.
  • the highest power throughput occurs when the piston is initially accelerated constantly at maximum acceleration during expansion. When the maximum permissible speed of the piston has been reached, it is moved at this maximum speed until it is necessary to decelerate the piston again with a negative and constant maximum acceleration.
  • the temporal synchronization of all valves takes place in that the pressure cylinder in its expansion phase by the mechanical movement of the pressure cylinder or a derived synchronized movement, such as a rotational movement, periodically changes the valve position and thus controls the closing times of each valve directly mechanically.
  • the opening tion times for each valve for example, by the dimensions of a control piston which opens and closes a valve by the linear movement, set.
  • An example of a linear design of a periodic double-acting pressure cylinder conversion system is the well-known James Watt steam engine.
  • a rotary embodiment of this periodic pressure cylinder conversion system has separate rotary valves which are opened and closed in synchronism with the clock frequency f Cyc for predetermined periods of time as shown in FIG.
  • the opening times t E i n i of the separate valves arise from the angular dimensions of the rotating valve segment, in which a flow through the valve is possible.
  • the clock frequency f Cyc is derived in purely mechanical systems of the mechanical movement of the printing cylinder, which is converted into a rotational movement, such as. B. in the known Corliss engine. Another possibility of realization results by externally controlled z. B. wins with an electric motor which rotates synchronously to the piston position.
  • the temporal synchronization of the rotary valves takes place, for example, in that all valves are connected to one another via an axis of rotation which rotates at the clock frequency f C yc.
  • the intake volume per stroke V A is ⁇ adjustable, which t a variable opening time of the intake valves e i n is possible i.
  • the inlet valves are pneumatically operated, that is, a controller adjusts the intake volume V A ⁇ (t) by means of the input let duration T A ⁇ so that the desired fluid pressure is reached after the end of the expansion over the entire piston stroke.
  • the condensation temperature of the medium is adjusted so that it corresponds to the maximum required temperature of the coupled heat consumers.
  • electrically controllable intake valves are used for this purpose.
  • the control of the valve can also be pneumatic or hydraulic.
  • the intake valves are realized with a control piston which opens and closes the intake valves by the linear movement, wherein the linear movement of the control piston is realized. Bens is externally controlled, that is not derived from the movement of the printing cylinder.
  • a controlled linear movement of the control piston can be realized eg with a linear motor.
  • valve-controlled double-acting pressure cylinder shown in FIG. 11, in which the piston of the piston-cylinder unit is moved by the inflow of the working medium into a working chamber of the pressure cylinder. After evaluation of sensor data, the controller automatically determines the duration of the inflow.
  • the inlet volume to be controlled is thus a function of the medium pressure available on the input side, which, however, is to be regarded as constant, and the temperature desired on the output side during the condensation.
  • each adjustable condensation temperature T K ⁇ ⁇ d exists a corresponding intake period t Em i and a constant value for the performed work of a piston stroke W THDY
  • valve-controlled double-acting impression cylinder is that there is no need to immediately start executing the next cycle after a completed stroke.
  • the clock frequency f Cyc is dependent on the expansion time t Exp and the dead time ttot-
  • the controller determines the corresponding clock frequency f Cyc in the different operating modes:
  • the controller waits from the execution of a power stroke to the execution of the counterclockwise power stroke until half the period T Cyc has expired.
  • a power-modulated valve control takes place, as shown in FIG. The dead times are compensated by the filter and straightening unit almost lossless.
  • the exhaust valves are after half the period T Cyc , ie synchronous to the clock frequency f Cyc . alternately opened and closed.
  • Execution of the exhaust valves is thus both externally controlled, such as. B. by electrically controllable valves, as well as by one of the linear movement of the pressure cylinder derived control possible, such. B. by means of a synchronous to the piston position rotary valve control.
  • thermodynamic cycle such as a specially adapted compressed air motor
  • the linear piston movement is first converted into rotational energy by means of a crankshaft, which is also converted into rotational energy by means of a specially designed motor
  • Application tuned generator is then converted into electrical energy.
  • Another preferred option is through the use of a
  • Rotary piston engine in particular a DiPietro engine as such, in which also the intake volume per power stroke can be controlled.
  • the generator of rotations is the RMT generator designed especially for wind turbines. Both components are characterized in the required power range already at low speeds both by a high efficiency in the conversion and by very low start-up and shutdown losses.
  • the electrical voltage generated at the generator in all the systems described can also be used elsewhere.
  • mains voltage can by means of a suitable converter battery charging, z.
  • lithium-ion batteries for electric vehicles or suitable voltages in order to win by electrolysis hydrogen produced.
  • the kinetic energy generated by the conversion system can otherwise, for. B. are used for cooling room air by means of a refrigerator.
  • the exhaust residual heat can be used to cover heating and DHW requirements, where:
  • FIG. 8 shows a possible technical realization of this thermal coupling via the heat accumulator.
  • the disadvantage of this arrangement is that Eww (t) + E H w (t) are variable, whereas the amount of heat recovered is always constant as soon as the heating system is in operation. The thermal compensation can only take place if there is a need for heating.
  • a further improvement according to the invention is therefore the use of the waste gas residual heat for the production of electricity in the thermodynamic cyclic process, that is to say in the operating modes a) and b), where the following applies:
  • E ⁇ HD ⁇ (t) E jerk (t) + E H e, z (t)
  • the heating system according to the invention can furthermore optionally be operated in several operating modes.
  • a first mode of operation the heat generated or stored by the one or more heat generators is used to heat or fill the heat accumulators.
  • the heat generated is fed to the thermodynamic cycle for the production of electricity, the residual heat resulting from the thermodynamic cycle being transferred to the heat sink.
  • a third mode of operation the heat generated is supplied to the thermodynamic cycle for the production of electricity, the residual heat resulting from the thermodynamic cycle being used to heat or fill the heat store.
  • the controller automatically determines, based on predetermined criteria, in which of the operating modes the heating system is operated and can optionally obtain information from an electricity supplier of the object in order to enable power production in particularly worthwhile periods of time.
  • the solar energy can be effectively harnessed with this heating system, both for electricity production and for heating heat recovery by the prevailing in the heat storage or in the solar collector low temperature level, which must be only higher than the temperature of the heat sink (Tws) to the remaining temperature range up to a consumption-dependent setpoint temperature is further heated.
  • Tws temperature of the heat sink
  • the solar collectors are used in one operating mode of the heating system, in particular at night or in winter, as a heat sink, which absorbs the residual heat of the thermodynamic cycle.
  • a multi-stage solar collector construction is advantageous, which consists of a series connection of different collector types, on the one hand from inexpensive collectors lower thermal insulation and on the other hand from higher-value collectors with high thermal insulation.
  • the individual collector types also bridged, ie can not be traversed by the solar medium.
  • the controller determines by means of fixed set criteria, such as B. the outside temperature, whether only one of the collector types or both are flowed through serially by the solar medium.
  • radiators or underfloor heating of the object can be used as a permanent heat sink for the thermodynamic cycle, even if there is no heating demand.
  • a special radiator in the washroom which is always heated with residual heat, if this occurs during the exclusive power production, could be used, for example incidentally also for drying clothes.
  • a solar-assisted heating system has an inverse relationship between the availability of the primary solar energy and the heating demand, ie. H. Although there is a lot of primary energy available in summer, there is little or no need for heating, while the opposite is true in winter.
  • the invention takes advantage of this inverse ratio in that the excess primary energy is converted into electrical power.
  • the solar collectors, the heat storage, the heating system and the radiator only the cost price of the conversion system plus worthwhile expansions, such as additional collector surface and storage volume to install solar power production. It is advantageously achieved a high overall system utilization of the costly collector surface, since there is no oversupply of solar heat in the summer and in winter, the solar supply is made available through the heating system.
  • thermodynamic cycle processes for successive temperature ranges, each sub-process itself being independent.
  • ger thermodynamic process is and each sub-process has its own conversion system for the conversion of pressure into electrical energy and the heat of condensation of the sub-process for the higher temperature range is used by coupling via a heat exchanger as the evaporation energy for the sub-process of the lower temperature range.
  • the balance between the thermal energy production and the thermal energy requirement is determined and set periodically by the controller preferably according to the following formula:
  • a further improvement according to the invention occurs when the required power compensation between the sub-processes takes place in that the controller controls the transition temperature between the condensation of the medium of the first sub-process and the evaporation of the medium of the second sub-process, the power ratio of the two sub-processes and the According to requirements.
  • a cost-effective coupling of individual components of the two conversion systems for the conversion of pressure into electrical energy so that not all individual components are twice required, by means of a mechanical coupling of the conversion systems, which is designed so that the mechanical forces add, so that only a generator and a power grid are required, which each transmit the sum of the energy of the sub-processes.
  • Another possible cost-effective coupling of individual components of the two conversion systems for the conversion of pressure into electrical energy, so that not all individual components are doubly required, is by means of a electrical coupling of the generator outputs feasible, which causes only a power grid is required, which transmits the sum of the energy of the sub-processes.
  • thermodynamic process particularly advantageous here is the coupling of an exhaust heat recovery system and a thermal solar system to the low-temperature circuit of the two-stage thermodynamic process.
  • the energy supply E THDY takes place at different temperature levels in two stages.
  • the recovered heat energy E RUC * is used for heating or partial evaporation of the thermodynamic medium up to the temperature level T jerk , where:
  • E THDY2 (t) Eso l (t) + E jerk (t) + E R68M (t)
  • the amount of energy for conversion into electrical energy E T HDY-Stufe2 and thus E THDY thus increases due to the different temperature levels additively to the value of the recovered exhaust heat E Ruck (t) and the solar energy Esoi (t).
  • the recovered thermal energy E He ⁇ Z is used only for residual evaporation of the thermodynamic medium from the temperature level T RQck to the temperature level T He z , where:
  • the controller independently sets one or more of the operating modes characterized below: a) “Heating, DHW and electricity production” operating mode b) Operating mode “Exclusive electricity production from heating heat”
  • the controller takes into account but u in the operating mode. a. also the primary energy supply, the (predicted) heating energy demand, the time-dependent efficiency of the heat storage and the relationship between the yield for injected electricity and the actual heating costs.
  • the controller ensures energy management for the site-dependent energy distribution, taking into account determined and predicted process-influencing parameters.
  • the operating mode a) "heating, DHW and power production” is alternately active until the heat storage is sufficiently filled and then, after reaching this condition, the operating modes b) "Exclusive power production from heating heat” and e) "Solar heating and DHW by means of heat storage” are activated until the stored amount of heat in the heat storage falls below a lower threshold.
  • PTHDY2 PsP Out + PRück + PR ⁇ SU
  • the condensation temperature of the first stage T Kon d 2 is constant in the operating modes, a conversion system without a regulatable outlet pressure is advantageous for the first stage, such as a DC steam engine or a turbine.
  • the second stage has a conversion system without an adjustable outlet pressure, such as a DC steam engine or a turbine.
  • the heating system is realized with a mode a) in which only the first stage produces electricity.
  • the second stage only heat is produced in this mode by the second-stage conversion system in this mode is not flowed through by the thermodynamic low-temperature circulation medium.
  • the thus modified mode a) is characterized by the following properties:
  • thermodynamic cycle Further general increases in efficiency for all system systems presented on the one hand result from the fact that internal heat exchangers (regenerators) are provided for the thermodynamic cycle.
  • a cost-effective solution here is a sprinkler, which cools solar collectors in addition, among other things by the resulting evaporative cooling.
  • this sprinkler system should only be activated by the controller, if overall cost advantages are expected.
  • FIG. 1 is a schematic representation of the thermal couplings of all the components involved and the associated tasks of the intelligent
  • FIG. 2 is a technical embodiment of the heating system according to the invention.
  • FIG. 3 is a schematic representation of a combined condenser
  • FIG. 5 shows the operating mode "heating, WW and electricity production"
  • FIG. 7 is a technical embodiment of the heating system according to the invention with exhaust heat recovery coupled to the heat storage;
  • FIG. 8 shows a technical embodiment of the heating system according to the invention with exhaust gas heat recovery coupled to the thermodynamic process
  • FIG. 9 shows a schematic representation of a possible linear conversion system for the conversion of thermodynamic into electrical energy
  • FIG. 10 is a schematic representation of a periodic valve control
  • FIG. 11 is a schematic representation of a valve-controlled double-acting pressure cylinder
  • FIG. 12 shows a schematic illustration of a power-modulated valve control
  • FIG. 13 shows a schematic representation of a possible rotational conversion system for converting thermodynamic energy into electrical energy
  • FIG. 14 is a schematic representation of a double-stage thermodynamic cycle
  • FIG. 15 shows a schematic representation of a mechanical coupling of the conversion systems for the conversion of pressure into kinetic energy
  • FIG. 16 shows a schematic representation of an electrical coupling of the generator outputs
  • FIG. 17 shows a technical embodiment of a solar collector circuit
  • FIG. 18 shows a technical embodiment of a double-stage design with solar collectors and exhaust gas heat recovery in the THDY circuit
  • FIG. 19 shows the operating mode "heating, DHW and electricity production"
  • FIG. 20 shows the operating mode “Exclusive power production from heating heat"
  • FIG. 21 shows the operating mode "Exclusive power production from heating heat and stored or direct solar energy"
  • FIG. 1 shows in general the individual components of a heating system according to the invention and the thermal coupling 5 according to the invention: the heat generators 1, comprising a conventional heating system 2 and optional solar collectors 3, an optional heat and / or cold storage 4, a heat sink 6, heat consumer 7, comprising an apparatus for hot water heating 8, a heating circuit 9 and a thermodynamic cycle 10, which is used by means of a conversion system 11 for the conversion of thermodynamic energy into electrical energy for power production.
  • the operation of this heating system and its individual components is controlled by a central controller 12.
  • the control includes process-influencing control parameters which are continuously recorded by suitable sensors 13 and supplied to the controller 12.
  • the controller 12 is also capable of estimating or predicting parameters relevant to the control of the heating system based on the sensed parameters and / or assumptions (others).
  • FIG. 2 shows the schematic structure of a mini CHP according to the invention with a burner circuit 70, which flows through the boiler of a firing system 71, a thermodynamic circuit 74 with which power is obtained, a heating circuit 79, which supplies the radiators
  • the burner circuit 70 flows through the evaporator 73 of the thermodynamic circuit 74 and two separate condenser 75 and 76 depending on the operating mode on the output side either from the heating circuit 79 or from the cooling circuit 77 flows through ,
  • the separate condensers 210 and 211 are combined in a cost-effective manner in a combined heat exchanger with separate inlets and outlets for the thermodynamic cycle 200, the collector circuit 201 and the heating circuit 202.
  • FIG. 4 illustrates the schematic structure of another mini CHP according to the invention, which is cheaper to produce by a dual function of some components.
  • the combustion chamber of the furnace 331 which flows through the medium of the thermodynamic cycle 330, at the same time the evaporator of the thermodynamic cycle 330.
  • the heat storage 332 can be selected as a thermal heat sink of the thermodynamic cycle used by the condenser 333 kos- is inexpensively integrated in the heat storage 332.
  • the heating circuit can be used cost-effectively indirectly as a thermal heat sink of the thermodynamic cycle process by relating to a heat exchanger 332 integrated heat exchanger 334, the required heating heat.
  • FIG. 5 describes the components and temperature levels contained in the overall structure according to FIG. 4, which are required for the operating mode "heating, DHW and power production”.
  • FIG. 6 describes the components and temperature levels contained in the overall structure according to FIG. 4, which are required for the operating mode "Exclusive power production from heating heat".
  • FIG. 7 shows the schematic structure of another possible mini CHP with an exhaust heat recovery 338, which is coupled to a heat accumulator 340 via a heat exchanger 339.
  • FIG. 8 shows the schematic structure of another possible mini CHP with an exhaust heat recovery 350, which is coupled to the thermodynamic circulation medium 352 via a heat exchanger 351.
  • the system shown in FIG. 9 comprises a thermodynamic part 501 with a working medium, one or more pressure cylinders 502, a linear generator 503 having a magnet and a coil, a controller 506 acting on both parts, which is part of the central controller 12 Rectifier and filter unit 504, which converts the voltage pulses generated by the magnetic movement into DC voltage, and an inverter 505, which converts the DC voltage into an AC voltage suitable for feeding in the grid.
  • Rectifier and filter unit 504 which converts the voltage pulses generated by the magnetic movement into DC voltage
  • an inverter 505 which converts the DC voltage into an AC voltage suitable for feeding in the grid.
  • the heat of condensation of the thermodynamic process is supplied to the heat consumers.
  • FIG. 10 shows a schematic representation of a periodic valve control, in which each individual inlet and outlet valve is periodically opened and closed with the clock frequency f Cyc for a period of time defined by the valve control settings, the period t Cyc being the sum of the duration of a work cycle t From ii and an opposite working cycle t AuS i 2 corresponds.
  • a valve-controlled pressure cylinder is shown, in which the two power strokes are completely independent of each other (in particular temporally); So there is no predetermined periodic clock sequence as in known multi-stroke engines.
  • the controller 609 provides by opening or closing the ports 605, 606, 607, 608 for performing a power stroke.
  • the four ports 605, 606, 607, 608, to which the lines 601, 602 are coupled to the work spaces 603, 604, may be selectively opened or closed by the controller 609.
  • the expanding working fluid passes through the first conduit 601 into the first working space 603 of the pressure cylinder 600.
  • the control 609 opens the port 605 and closes the port 606.
  • the control 609 closes the port 608 of the second conduit and opens the port 607
  • a force F stroke is exerted on the piston 608, resulting in a movement of the piston 608 to the right (as shown in the figure) while performing work.
  • This process which ends after a stroke of the piston 608, represents a "normal" power stroke of the printing cylinder.
  • the controller 609 closes the open ports 606, 607 and opens the closed ports 605, 608 to give an oppositely directed piston force -F stroke and a movement of the piston 608 to the left. Which of the two working strokes (normal or opposite) is performed depends on the current position of the piston 26.
  • the volume (intake volume) flowing into the working spaces 603 or 604 is regulated.
  • the start and duration of the inflow are automatically determined, thereby adjusting the pressure and thus the medium temperature after the expansion so that it corresponds to the maximum required temperature of the coupled heat consumers.
  • the inlet volume is thus a function of the input pressure available medium pressure and the output side desired pressure during condensation, which allows a very efficient energy conversion.
  • control / regulation of the individual circulation processes and of the linear generator takes place with the inclusion of process-influencing parameters (thermal energy supply, thermal heating demand, pressure and temperature of the working medium, the heat storage and the environment, etc.), which are provided by a multiplicity of suitable sensors 610 (Pressure, temperature, etc.) are provided.
  • this principle is also applicable to two counter-rotating pressure cylinders, as used in conventional free-piston systems, in which case the working space 304 remains unused and alternately always only one pressure cylinder performs the power stroke, while the other is in the exhaust phase.
  • FIG. 12 shows a diagrammatic representation of a power-modulated valve control in which the execution of the next working cycle is not immediately started after an executed work cycle.
  • the clock frequency f Cyc is dependent on the expansion time t Exp and the dead time t tot :
  • the controller waits from the execution of a power stroke to the execution of the opposite clock cycle until half the period T Cyc has expired.
  • the dead times are compensated by the filter and straightening unit almost lossless.
  • the exhaust valves are thereby alternately opened and closed after half the period T Cyc , ie synchronously with the clock frequency f Cyc .
  • FIG 13 illustrates an alternative rotation conversion system which may be used in place of the previously described linear conversion system.
  • the rotation conversion system is coupled to the thermodynamic cycle 701 where first the available thermal energy (heat energy) is converted to thermodynamic energy (vapor pressure). The vapor pressure is then measured by means of a valve-controlled expansion machine 702, such.
  • a rotary piston engine in particular a di- Pietro- Enyi ⁇ e
  • the controller 705 by means of the intake and exhaust valves, the intake volume of each individual NEN working clock sets so that the pressure and thus the medium temperature after expansion corresponds to the maximum required temperature of the coupled heat consumers.
  • the rotational energy is converted by means of the generator 703 into electrical energy, which is finally converted by a power converter 704 in AC to the grid feed.
  • a power converter 704 in AC to the grid feed.
  • process-influencing control parameters are included, which are continuously detected by suitable sensors 706 and the controller 705 (part of the central controller 12) are supplied.
  • FIG. 14 describes a double-stage thermodynamic process which consists of two sub-processes 400 and 401 for successive temperature ranges.
  • Each subprocess itself is an independent thermody- namic process with a medium suitable for the assigned temperature range.
  • Each subprocess has its own conversion system for converting pressure into electrical energy 402 and 403.
  • the heat of condensation of the higher temperature portion subprocess 400 is used as coupling energy via a heat exchanger 404 as the evaporative energy for the lower temperature portion 401 subprocess.
  • FIG. 15 describes possible cost-effective solutions, one for a linear system (FIG. 15a) and one for a rotation system (FIG. 15b), such as preventing all the individual components of the two conversion systems required in the two-stage thermodynamic process to convert pressure into electrical energy , are duplicated.
  • This is realized by the illustrated mechanical couplings of the pressure-to-kinetic energy conversion systems 451 and 452, which are designed to vectorially add the mechanical forces involved in the conversion of pressure to kinetic energy by , controlled by the controller, act simultaneously in the same direction.
  • a generator 453 and a power converter 454 are required, which each transmit the sum of the energies of the sub-processes.
  • FIG. 16 describes a further cost-effective solution for preventing the duplication of all individual components of the two conversion systems required for a double-stage thermodynamic process to convert pressure into electrical energy.
  • FIG. 17 is a schematic representation of a multi-stage solar collector construction, which comprises a series connection of collectors of lower thermal insulation 50 and higher thermal insulation 51.
  • each of the collector types can also be bridged, i. H. not flowed through by the solar medium.
  • the controller 12 determines based on sensor data such. B. the ambient or collector temperature and the current intended use of the collectors as a heat source or as a heat sink, whether only one of the collector types or both are serially flowed through by the solar medium.
  • FIG. 18 shows a schematic representation of a double-stage embodiment with solar collectors and exhaust gas heat recovery in the THDY circuit, consisting essentially of a burner circuit 100, a thermodynamic high-temperature circuit 101, a thermodynamic low-temperature circuit 102, a heating circuit 117, a solar circuit 103, a WW circuit 104, and a cooling circuit 105.
  • the burner circuit 100 flows through the boiler of a furnace 106 and is coupled via a heat exchanger 107 to a thermodynamic high-temperature circuit 101.
  • the stored in the heat storage 115 solar energy Es o i (t) is thereby used for heating the thermodynamic medium to the temperature level T S po ut by the low-temperature circuit 102 is thermally coupled via a heat exchanger 112 to the heat storage 115, wherein the heat exchanger 1 12 a Dual function: in one mode, it serves to heat the thermodynamic medium to the temperature level T S po ut , and in another mode, it serves as a condenser for transmitting the heat of condensation of the low-temperature circuit 102 to the storage medium.
  • the recovered heat energy E Re is used for heating tion or partial evaporation of the thermodynamic medium from the temperature level T SP o ut to the temperature level T return thereby used by the low-temperature circuit via a heat exchanger 111 to the exhaust heat recovery 110 is thermally coupled.
  • the residual heat of the low-temperature circuit E residual stage 2 (t) is transferred to the cooling circuit 105 by means of a condenser 109.
  • the thermal coupling of a solar collector circuit 103 to the heat storage 115 takes place by means of a heat exchanger 113.
  • the thermal coupling of a heat accumulator 115 to the WW circuit 104 takes place by means of a heat exchanger 114.
  • FIG. 19 describes the components and temperature levels contained in the overall construction according to FIG. 18, which are required for the operating mode "heating, DHW and power production”.
  • FIG. 20 describes the components and temperature levels contained in the overall construction according to FIG. 18, which are required for the operating mode "Exclusive power production from heating heat".
  • FIG. 22 describes the components and temperature levels contained in the overall structure according to FIG. 18, which are required for the operating mode "filling solar storage tank”.
  • FIG. 23 describes the components and temperature levels contained in the overall structure according to FIG. 18, which are required for the operating mode "solar heating and DHW”.
  • Figure 24 is a schematic representation of a modified embodiment of Figure 18, in which the second stage has a conversion system without a regulatable outlet pressure, such as a DC steam engine or a turbine. This is made possible by the heating system tem with a mode a) is realized in which only the first stage produces electricity and the second stage in this mode, only heating heat is produced by the second stage conversion system in this mode is not flowed through by the thermodynamic low-temperature circulation medium.
  • a a
  • FIG. 25 describes the components and temperature levels contained in the overall structure according to FIG. 24, which are required for the modified operating mode "heating, DHW and power production".

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  • Chemical & Material Sciences (AREA)
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  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
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  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

L'invention concerne un système de chauffage destiné à un objet et comprenant un couplage thermique (5), régulé par un dispositif de commande (12), d'un générateur de chaleur thermique (1), en particulier d'une installation de chauffage classique (2), avec plusieurs consommateurs de chaleur (7) pour la production simultanée de chaleur et de courant. L'un des consommateurs de chaleur (7) présente un système de conversion (11) servant à transformer l'énergie thermodynamique en énergie électrique et se basant sur un cycle thermodynamique (10), en particulier un cycle à vapeur, un cycle organique de Rankine ou un cycle de Kalina. La chaleur de condensation apparaissant dans le cycle thermodynamique (10) est transmise à d'autres consommateurs de chaleur (7). On peut faire fonctionner le système de chauffage dans au moins un mode parmi deux modes de fonctionnement. Dans le premier mode de fonctionnement, la chaleur produite est amenée au cycle thermodynamique (10) en vue de la production de courant et la chaleur résiduelle provenant du cycle thermodynamique (10) est utilisée pour le chauffage. Dans le deuxième mode de fonctionnement, du courant est produit indépendamment des besoins en chauffage grâce à un dissipateur thermique (6) qui absorbe la chaleur de condensation du cycle thermodynamique (10).
PCT/EP2009/001023 2008-02-13 2009-02-13 Système de chauffage produisant du courant WO2009100924A2 (fr)

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CA2714644A CA2714644A1 (fr) 2008-02-13 2009-02-13 Systeme de chauffage produisant du courant
EP09710656A EP2252835A2 (fr) 2008-02-13 2009-02-13 Système de chauffage produisant du courant
AU2009214266A AU2009214266A1 (en) 2008-02-13 2009-02-13 Heating system producing current
US12/867,132 US20110101119A1 (en) 2008-02-13 2009-02-13 Heating system producing electricity
CN2009801122107A CN102047044A (zh) 2008-02-13 2009-02-13 产生电流的供热系统

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DE102008008832.3 2008-02-13
DE102008008832A DE102008008832A1 (de) 2008-02-13 2008-02-13 Strom produzierendes Heizsystem

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WO2009100924A3 WO2009100924A3 (fr) 2009-11-19

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AU2009214266A2 (en) 2011-02-03
CA2714644A1 (fr) 2009-08-20
CN102047044A (zh) 2011-05-04
US20110101119A1 (en) 2011-05-05
DE102008008832A1 (de) 2009-08-27
AU2009214266A1 (en) 2009-08-20
EP2252835A2 (fr) 2010-11-24
RU2010137854A (ru) 2012-03-20

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