US20160370017A1 - Thermal Connection Of A Geothermal Source To A District Heating Network - Google Patents

Thermal Connection Of A Geothermal Source To A District Heating Network Download PDF

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US20160370017A1
US20160370017A1 US14/901,826 US201414901826A US2016370017A1 US 20160370017 A1 US20160370017 A1 US 20160370017A1 US 201414901826 A US201414901826 A US 201414901826A US 2016370017 A1 US2016370017 A1 US 2016370017A1
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heat
temperature
heat pump
condenser
district heating
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Uwe Lenk
Florian Reißner
Jochem Schaefer
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Siemens AG
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Siemens AG
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Publication of US20160370017A1 publication Critical patent/US20160370017A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • F24D11/0207—Central heating systems using heat accumulated in storage masses using heat pumps district heating system
    • 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
    • F24D10/00—District heating systems
    • 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
    • F24D2200/11—Geothermal energy
    • 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
    • F24D2200/12—Heat pump
    • 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
    • F24D2200/12—Heat pump
    • F24D2200/123—Compression type heat pumps
    • 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
    • F24D2200/13—Heat from a district heating network
    • 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
    • Y02B10/40—Geothermal heat-pumps
    • 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]
    • Y02B30/17—District heating
    • 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]
    • 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
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
    • Y02P80/14—District level solutions, i.e. local energy networks

Definitions

  • the present invention relates to a method for providing heat for a district heating supply and to the arrangement of a district heating network with a geothermal source.
  • district heating supplies have predominantly been based on the burning of fossil energy sources.
  • Most of the existing district heating networks use the waste heat of fossil-fueled plants for electrical power generation. With combined heat and power (cogeneration), the energy content of the fuel is used largely completely.
  • district heating networks are for example connected to refuse incineration combined heat and power plants.
  • district heating networks Since many district heating networks exist at present, they must also continue to be supplied with heat. However, this heat is also to originate as far as possible exclusively from renewable sources of energy.
  • Existing urban district heating networks sometimes have over 800 km of district heating lines and an annual heating output of 4 TWh. They are used for supplying district heat to consumers such as private households, commercial and industrial facilities and various public users. In the year 2012, around 90% of district heat was still being generated by means of heating power plants that burn fossil energy sources.
  • a further alternative heat source for district heating networks is that of geothermal sources.
  • geothermal sources Depending on geographical and geological conditions, however, no thermal water sources of a temperature that would be sufficient for supplying a district heating network are reached even by deep drilling operations.
  • FIG. 1 for example, there is shown a section through a region such as may be found for example in the German Alpine uplands.
  • the limestone bed carrying thermal water in this case lies up to 4000 m below the surface of the Earth.
  • the temperature level would have to be higher.
  • the additional necessary thermal energy has been provided by means of what is known as additional firing. For example, heat from burning natural gas is used, which however is to be avoided in the future.
  • One embodiment provides a method for providing heat for a district heating supply, comprising the following method steps: extracting thermal water for providing heat at a first temperature level from a geothermal source, providing and operating a high-temperature heat pump, thermally connecting the geothermal source to the high-temperature heat pump, conducting the thermal water through the evaporator of the high-temperature heat pump, thermally transmitting heat of the first temperature level from the thermal water to the evaporator of the high-temperature heat pump and providing heat at a second, higher temperature level through the condenser of the high-temperature heat pump.
  • a high-temperature compression heat pump is used as the high-temperature heat pump.
  • the second, higher temperature level is at least 100° C., e.g., at least 110° C.
  • a working medium from the family of fluoroketones is used in the high-temperature heat pump.
  • a non-toxic working medium is used in the high-temperature heat pump.
  • a working medium of which the critical temperature lies above 160° C. is used in the high-temperature heat pump.
  • At least one thermal store for taking up and storing the heat of the first temperature level from the thermal water or the heat of the second, higher temperature level from the condenser of the high-temperature heat pump is used.
  • At least two high-temperature heat pumps are coupled in a series connection.
  • Another embodiment provides an arrangement for providing heat for a district heating network at a temperature level of at least 100° C. comprising at least one thermal water extraction device and a high-temperature heat pump.
  • the high-temperature heat pump is a high-temperature compression heat pump.
  • the high-temperature heat pump contains a working medium that is from the family of fluoroketones.
  • the high-temperature heat pump contains a working medium of which the critical temperature lies above 160° C.
  • the arrangement includes at least one thermal store, which is designed for taking up and storing heat of a first temperature level from the thermal water or heat of a second, higher temperature level from the condenser of the high-temperature heat pump.
  • the arrangement includes at least two high-temperature heat pumps in a series connection.
  • FIG. 1 shows a North-South section through a region given as an example
  • FIG. 2 shows a method diagram of a geothermal heating plant with an absorption heat pump
  • FIG. 3 shows a method diagram of an absorption heat pump
  • FIG. 4 shows a method diagram for raising the temperature with a compression heat pump
  • FIG. 5 shows a method diagram for raising the temperature with a compression heat pump and thermal buffer stores
  • FIG. 6 shows a COP temperature diagram of the high-temperature heat pump (Coefficient of Performance, rate of performance),
  • FIG. 7 shows a COP temperature diagram for estimating the potential in the megawatt power range
  • FIG. 8 shows a temperature entropy diagram of a transcritical heat pump process
  • FIG. 9 shows a temperature entropy diagram of a subcritical heat pump process.
  • Some embodiments of the invention provide a method for providing heat for a district heating supply, which includes the following steps: first, extracting thermal water for providing heat from a geothermal source, the temperature of which is at a first temperature level. Then, providing and operating a high-temperature heat pump, and also thermally connecting the geothermal source to the high-temperature heat pump. This is followed by conducting the thermal water through the evaporator of the high-temperature heat pump and thermally transmitting heat of the first temperature level from the thermal water to the evaporator of the high-temperature heat pump. Finally, there is also providing heat at a second, higher temperature level through the condenser of the high-temperature heat pump.
  • This method of combining a district heating supply with a geothermal source and suitably connecting them by way of a high-temperature heat pump has the advantage of ensuring a decarbonized heat supply.
  • the geothermal source is therefore used as a heat source for the evaporator of the heat pump.
  • Heat can then be provided in the condenser of the heat pump at a higher temperature level for supplying heat consumers in a district heating network.
  • Heat consumers may be for example towns or urban districts, which along with public users may predominantly comprise residential buildings and private consumers, as well as industrial users.
  • the method may provide an enhancement of the heat of a geothermal source.
  • a high-temperature compression heat pump may be used as a high-temperature heat pump. Apart from the heat source for the evaporator, this only requires an electrical energy source for operating the compressor. This may take place via electrical power from regenerative sources of energy, for example by means of electrical power from a photovoltaic or wind turbine installation.
  • geothermal sources are often not at sufficiently high temperatures for a district heating supply. Especially in the vicinity of towns or directly in the urban area, where most of the consumers are located, it is not possible to switch to any sources, no matter how far away they are, or to any bores, no matter how deep they are, on the basis of the geological site.
  • the heat of geothermal sources that are available often lies at a temperature level between 60° C. and 95° C., which could perhaps be sufficient for a district heating supply in the summer months, but especially in the winter season is not sufficient at the temperate latitudes. Then, district heating flow temperatures of at least 100° C., e.g., about 130° C., are necessary.
  • the second, higher temperature level lies at at least 100° C., in particular at at least 110° C.
  • the second, higher temperature level may be at least 120° C. or in some embodiments at least 130° C.
  • working media from the family of fluoroketones are used in the high-temperature heat pump.
  • Exclusively non-toxic working media may be used, e.g., environmentally friendly, safe working media.
  • a working medium of which the critical temperature lies above 140° C., e.g., above 150° C. and in some embodiments above 160° C., may be used in the high-temperature heat pump.
  • environmentally friendly, non-toxic and safe working media are often distinguished by very specific thermodynamic properties, such as for example a high critical temperature.
  • the high critical temperature of the working medium used has the advantage that a subcritical heat pump process can be operated and an almost isothermal heat output can take place.
  • the thermal water is first conducted through a first heat exchanger and the cooled thermal water is returned to the rock bed by way of a reinjection line.
  • the first heat exchanger is adjoined by a heat transporting circuit, in which a heat transporting medium, e.g., water, transports the heat. From this heat exchanger, heat at a temperature level that lies only a little below the temperature of the geothermal source is passed on the one hand to the evaporator and on the other hand to the condenser of the high-temperature heat pump by way of two lines.
  • the heat transporting medium is brought to the required flow temperature for the district heating network.
  • the district heating return and the return from the evaporator of the heat pump may be brought together again and mixed before the heat transporting medium reaches the first heat exchanger again.
  • the return temperatures of heat transporting media to district heating networks usually lie at 45° C. or below.
  • the return temperature downstream of the evaporator is much higher, depending on the temperature of the geothermal source, and, given the mixing with the district heating return, can consequently already provide an increased mixing temperature before the heat transporting medium takes up heat again from the geothermal source by way of the first heat exchanger.
  • At least one thermal store for taking up and storing the heat of the first temperature level from the thermal water or the heat of the second, higher temperature level from the condenser of the high-temperature heat pump.
  • at least one thermal store is arranged with the first heat exchanger at the geothermal source or downstream of the condenser of the heat pump, so that in each case the heat pump can access the thermal store of the geothermal source temperature level or the district heating network can access the thermal store of the heat pump outlet temperature level.
  • the coupling of two heat pumps may be performed for example to enhance the geothermal heat source.
  • the heat pumps may be combined in a series connection, in order in this way to generate sufficiently high temperatures.
  • Some embodiments provide an arrangement for providing heat for a district heating network at a temperature level of at least 100° C., which arrangement comprises at least one thermal water extraction device and a high-temperature heat pump.
  • heat is provided at a temperature level of at least 100° C., for example of at least 120° C. and in some embodiments at least 130° C.
  • This arrangement of a high-temperature heat pump with a geothermal source and a district heating network has the advantage of ensuring a decarbonized heat supply, reducing CO 2 emissions and reducing the dependence on imported fossil energy sources.
  • the high-temperature heat pump is a high-temperature compression heat pump.
  • the high-temperature heat pump may contain a working medium that is from the family of fluoroketones.
  • the working medium in the high-temperature heat pump is at a critical temperature above 140° C., e.g., above 150° C. and in some embodiments above 160° C.
  • Environmentally friendly, non-toxic and safe working media may be contained by the high-temperature heat pump.
  • the compressor of the high-temperature heat pump is typically operated with electrical energy from regenerative energy sources, for example a photovoltaic installation or a wind turbine installation.
  • the arrangement for providing heat for a district heating network comprises a thermal store, which is designed for taking up and storing heat of a first temperature level from the thermal water or heat of a second, higher temperature level from the condenser of the high-temperature heat pump.
  • the arrangement may include a first thermal store for taking up and storing heat of the first temperature level from the thermal water and a second thermal store for taking up and storing heat of a second, higher temperature level from the condenser of the high-temperature heat pump.
  • the first thermal store may be arranged between the geothermal source and the heat pump, so that the evaporator of the heat pump can access this first thermal store.
  • the second thermal store is typically arranged between the condenser of the high-temperature heat pump and the district heating network or the district heating consumers, so that it can be charged with heat from the condenser of the high-temperature heat pump and the district heating network can be fed from it.
  • the arrangement comprises at least two high-temperature heat pumps in a series connection, i.e. that they are coupled one downstream of the other in such a way that heat from thermal water sources of very low temperature can also be enhanced to the extent that a temperature level that is suitable for supplying district heat is achieved.
  • FIG. 1 there is shown, as already mentioned at the beginning, a North-South section through a region of ground such as occurs for example in the German Alpine uplands.
  • the limestone bed M carrying thermal water descends from the North to the South, so that in the South it can only be reached by bores that become increasingly deeper.
  • the thermal water temperature T 1 in the Northern region is around 35° C.
  • the temperature T 4 in the South, and accordingly with the limestone bed M lying very much deeper, is around 140° C.
  • thermal water temperatures T 2/3 of around 65° C. to 100° C. are encountered.
  • this cross section illustrates the problem that a temperature that is usable for the district heating is not achieved without additionally raising the temperature level.
  • the temperature T 7 of a district heating flow 27 lies between 70° C. and 110° C., but depending on the time of year even much higher. In winter, the temperature T 7 of the district heating flow 27 may be between 90° C. and 180° C. Generally, a temperature T 7 of the district heating flow 27 of around 130° C. is sufficient.
  • FIG. 2 there is shown a method diagram known from the prior art for using ground heat in a district heating network 40 .
  • the thermal water is extracted from a rock depth of for example 2300 m via a thermal water line 20 and is at a temperature T 2 of around 65° C.
  • the thermal water is then for example passed to a heat exchanger 22 , which directly sends part of the thermal water at a temperature T 2 of around 65° C. further in the direction of the district heating flow 27 and provides a cooled part of the thermal water at a temperature level T 5 of around 40° C. to 45° C. to a thermal bath 25 .
  • This is a known, very popular material use of the thermal source.
  • Heat exchangers 22 used in such a way lie in a power range of for example around 2 MW.
  • the heat exchanger 22 also has fluidic connections to a heat pump 23 , only the use of absorption heat pumps 23 being known up until now in the prior art. These operate for example in a power range of around 7 MW.
  • An absorption heat pump 23 in this case represents a reheating solution. Alternatively, the burning of biomass or natural gas or electrical reheating is used for example for the additional firing.
  • the heat pump 23 has an outflow to the district heating flow 27 , and also an outflow with very greatly cooled water to a consumer 26 .
  • the cooled water is at a temperature T 6 of for example around 20° C. and is passed on for material use, thus for use as a drinking water supply, for example for households.
  • This outgoing line to the consumer 26 may for example have a fluidic connection to the line to the thermal bath 25 .
  • the heat pump 23 has an inflow for cold water, which is for example partly supplied from the district heating return 28 .
  • a combustion vessel 24 for natural gas which operates for example in the range of 10 MW and can balance out peak loads, and consequently represents a further necessary component for increasing the temperature of the district heating flow 27 .
  • the temperature T 7 of the district heating flow 27 realized in this way is in this case between 70° C. and 110° C.
  • Shown downstream of the heat user 29 are supply lines to heat consumers 40 , such as for example a town S with residential buildings and various public users, as well as alternatively to industrial users I.
  • the district heating return 28 is at a temperature level T g of generally between 40° C. and 45° C.
  • FIG. 3 there is additionally also shown in detail the method diagram of an absorption heat pump 23 , used for example in FIG. 2 .
  • the heat input Q in takes place to an evaporator 31 and the heat output Q out takes place at the liquefier of the absorption heat pump 23 .
  • the refrigerant circuit is identified by arrows.
  • the refrigerant K 1 is liquid and, downstream of the evaporator 31 , the refrigerant K g is vaporous. This is the form in which it reaches the thermal compressor 37 . In the latter, the vaporous refrigerant K g first runs through the absorber 32 and is then transported further by way of a pump 33 to the generator 34 .
  • the return connection between the generator 34 and the absorber 32 has a pressure reducing valve 36 .
  • the generator 34 is heated by means of burning natural gas, so that the refrigerant K g leaves the generator 34 again in a vaporous form. Downstream of the thermal compressor 37 , the refrigerant K g reaches the liquefier 38 , at which the heat output Q out takes place.
  • the return connection between the liquefier 38 and the evaporator 31 has in turn a pressure reducing valve 39 .
  • Heat pump installations 23 of this type known up until now and also compression heat pumps known up until now from the prior art are not currently capable of reliably achieving temperatures above 90° C. Individual prototypes achieve up to 100° C., but are not commercially available and are based on transcritical processes. The majority of the heat pumps used deliver temperatures in the low temperature range of around 55° C. to 60° C. and in the high temperature range of around 70° C. to 75° C.
  • FIGS. 4 and 5 there is shown the concept for raising the temperature of a geothermal source 41 by means of a compression heat pump 43 .
  • the heat pump 43 in this case respectively acts as a link between the geothermal source 41 and the district heating network 40 .
  • the heat pump 43 is thermally coupled to both: the extracted thermal water from the geothermal source 41 is for example at a temperature T 41 of 93° C.
  • the extracted thermal water is passed by way of a thermal water transporting line 411 to a heat exchanger 42 .
  • the outflow of the heat exchanger 42 is configured as a reinjection line 412 and brings the cooled water back into the deep rock beds G.
  • a further circuit is supplied with heat of the thermal water.
  • a transporting medium in particular water, can be conducted through a first supply line 421 to the evaporator 431 of the high-temperature heat pump 43 and by way of a second supply line 422 to the condenser 433 of the high-temperature heat pump 43 .
  • the outflow from the evaporator 431 then carries water at an already reduced temperature T 431 of for example about 80° C.
  • the temperature T 42 of the flow to the evaporator 431 is for example around 90° C.
  • the return from the evaporator 431 is in particular brought together with the return 48 of the district heating network 40 .
  • the return temperature T 40 of the district heating network 40 is in this case a maximum of around 45° C.
  • the brought-together return then again reaches the heat exchanger 42 .
  • the heat Q in which is made available by the geothermal source 41 , is passed on to the heat pump 43 .
  • this comprises a compressor 432 and also an expansion valve 434 .
  • the use of particularly suitable working media in the high-temperature heat pump 43 makes it possible to give off at the condenser 433 heat Q out at a temperature level T 43 of around 130° C., which can be made available to various consumers by way of a district heating network circuit 40 .
  • the compressor 432 of the high-temperature heat pump 43 is operated with electrical power, which according to the invention has been obtained from regenerative energy sources. Consequently, the overall arrangement comprising the geothermal source 41 or thermal water extraction 411 , high-temperature heat pump 43 and district heating network 40 is as it were decarbonized and ensures a reliable supply of heat for a district heating network 40 by means of ground heat.
  • thermal stores 51 , 52 have been added to the concept as it is represented in FIG. 4 .
  • the first thermal store 51 serves as a buffer between the geothermal source 41 and the arrangement of the district heating network 40 with the heat pump 43 .
  • heat at a temperature level T 41 of around 90° C. is stored and can be given off as and when required to the high-temperature heat pump 43 .
  • a second thermal store 52 is arranged between the high-temperature heat pump 43 and the district heating network 40 and is designed in such a way that heat at a temperature level T 43 of around 130° C. can be buffer-stored and given off as and when required to the district heating flow 47 .
  • These possibilities for storing heat make it possible to sever the link between the times at which power and heat are demanded by the customer and the times at which it is possible to supply the heat. If, therefore, there is a reduced demand for heat from the district heating network 40 , this heat can first be buffer-stored in the second store 52 without being lost.
  • this offers an option of providing negative control power (Power to Heat): in this way, a contribution can be made to balancing out fluctuating power production.
  • the power surplus can thus be compensated quickly, reliably and inexpensively and is available to the district heating network 40 at any desired later point in time in the form of heat from the energy store 52 .
  • COP-T diagrams are shown.
  • COP stands here for Coefficient of Performance and is the rate of performance of the heat pump 43 , which represents the heat output per electrical drive input:
  • the temperature T FW plotted in the diagram is the temperature of the heat output of the heat pump 43 to the district heating network 40 .
  • Measured values of a high-temperature compression heat pump 43 which is operated with a working medium such as for example Novec 649 (dodecafluoro-2-methylpentan-3-one), are plotted.
  • the temperature T Q of the source, or the evaporation temperature was varied between 40° C. and 90° C.
  • different temperature swings TH of between 30 K and 60 K were realized. With an increasing temperature swing TH, the rate of performance COP of the heat pump 43 falls.
  • FIG. 7 there is shown an estimate of the potential for high-temperature heat pump installations 43 in the megawatt range: the given measured values 73 with Novec 649 relate to a demonstrator with a thermal capacity of only 10 kW. Alternatively, Novec 524 (decafluoro-3-methylbutan-2-one) may also be used as the working medium. Also depicted in the diagram of FIG. 7 is the thermodynamic limit 70 on the basis of the Carnot efficiency. The expectation values 71 for plants in the megawatt power range lie at 55% to 65% of the Carnot efficiency 70 . The estimates 71 are based on extrapolations such as are to be expected according to experience as a result of higher efficiencies in the case of large plants with a greater volume and lower heat losses, and also greater compressors. The efficiency, that is to say the rate of performance COP, falls with increasing temperature T FW of the heat output, or the condensation temperature of the pump. The values shown in FIG. 7 apply for a heat source temperature of 80° C.
  • FIGS. 8 and 9 two temperature entropy diagrams are shown. These are intended to illustrate the difference between a transcritical heat pump process 80 , as often occurs in the prior art, as indeed especially in the case of a known heat pump that only achieves a heat output of up to 90° C., and a subcritical heat pump process 90 .
  • the transcritical process 80 does not allow the output of heat Q out to be maintained constantly at the achieved temperature level T 7 . Depicted in the diagrams is a portion of the phase limit of the respective working medium with its critical point KP, and also the heat pump process 80 , 90 .
  • the achievable temperature T 7 that can be delivered to the district heating flow 27 lies far above the critical point KP.
  • the flow temperature T 43 that is to say the maximum achievable hot water temperature T H2O for the district heating supply 40 , lies well below the critical point KP of the working medium, since preferably working media with very high critical temperatures are used. Accordingly, the heat pump process 90 is in the subcritical range, whereby an approximately isothermal heat output at this high temperature level T 43 of for example around 130° C. is ensured.

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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-Pump Type And Storage Water Heaters (AREA)
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US14/901,826 2013-07-30 2014-07-21 Thermal Connection Of A Geothermal Source To A District Heating Network Abandoned US20160370017A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102013214891.7 2013-07-30
DE102013214891.7A DE102013214891A1 (de) 2013-07-30 2013-07-30 Wärmetechnische Verschaltung einer Geothermiequelle mit einem Fernwärmenetz
PCT/EP2014/065598 WO2015014648A1 (fr) 2013-07-30 2014-07-21 Connexion thermotechnique d'une source géothermique à un réseau de chauffage à distance

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108518717A (zh) * 2018-04-28 2018-09-11 北京华誉能源技术股份有限公司 一种市政供热系统、供热方法及计费方法
WO2018206334A1 (fr) * 2017-05-12 2018-11-15 Siemens Aktiengesellschaft Dispositif et procédé pour accroître le rendement thermique d'une source de chaleur
US11300334B2 (en) * 2017-05-12 2022-04-12 Siemens Energy Global GmbH & Co. KG Device and method for increasing the thermal output of a heat source
EP4249813A1 (fr) * 2022-03-21 2023-09-27 Wolfgang Jaske und Dr. Peter Wolf GbR Procédé de gestion d'énergie d'un réseau thermique

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3273169A1 (fr) * 2016-07-19 2018-01-24 E.ON Sverige AB Système de transfert thermique
CN109564438B (zh) * 2016-07-20 2022-02-22 威拓股份有限公司 区域制热中的返回温度的降低以及区域制冷中的返回温度的增加
EP3399247A1 (fr) 2017-05-02 2018-11-07 E.ON Sverige AB Systèmes de distribution d'énergie urbain
DE102019000430B4 (de) 2019-01-22 2022-03-17 Franz Schneider Verfahren zur Erreichung sehr niedriger Rücklauftemperaturen mittels einer Wärmepumpe, Heizanordnung zur Durchführung des Verfahrens, sowie System für Wärme- und Kälteverteilnetze
AT521703B1 (de) * 2019-03-20 2020-04-15 Ortner Ges M B H Warmwasserbereitungsanlage
CN114353154A (zh) * 2021-12-10 2022-04-15 中国华能集团清洁能源技术研究院有限公司 地热和火电厂耦合的多级供热系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2298768A1 (fr) * 1975-01-27 1976-08-20 Parica Circuit pour la recuperation optimale de la chaleur d'une eau a temperature moyenne
US5326456A (en) * 1993-04-02 1994-07-05 Exxon Research And Engineering Company Upgrading of bitumen asphaltenes by hot water treatment containing carbonate (C-2726)
US20120272948A1 (en) * 2009-08-25 2012-11-01 Danfoss A/S Heat storage system
US20140245763A1 (en) * 2011-09-30 2014-09-04 Siemens Aktiengesellschaft High-temperature heat pump and method of using working medium in a high-temperature heat pump
DE102013211087A1 (de) * 2013-06-14 2015-01-15 Siemens Aktiengesellschaft Verfahren zum Betrieb einer Wärmepumpenanordnung und Wärmepumpenanordnung

Family Cites Families (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2287582A2 (fr) * 1974-10-08 1976-05-07 Technip Cie Procedes pour la production, le stockage et la distribution d'energies
US3996749A (en) * 1974-05-07 1976-12-14 Compagnie Francaise D'etudes Et De Construction "Technip" Method and plants for producing, storing, modulating and distributing energy
FR2424490A1 (fr) * 1978-04-26 1979-11-23 Lenoir Jacques Procede et installation de production et de distribution d'energie thermique avec transports compenses en nappe geothermique
FI791079A (fi) * 1979-04-02 1980-10-03 Valmet Oy Pao utnyttjande av en vaermepump sig grundande foerfarande vid tillvaratagande av vaerme
DE2952541A1 (de) * 1979-12-28 1981-07-09 Chemowerk Erhard Mödinger, Fabrik f. Kunststofferzeugnisse, 7056 Weinstadt Vorrichtung, insbesondere heizvorrichtung, zur ausnutzung von erdwaerme mit einer waermepumpe
JPH0610596B2 (ja) * 1984-12-06 1994-02-09 株式会社東芝 ヒ−トポンプ装置用熱交換器
DD265216A1 (de) * 1987-09-09 1989-02-22 Inst Energieversorgung Verfahren zur nutzung niedrigthermaler energiequellen in kopplung mit fernwaermeversorgungssystemen
FI98857C (fi) * 1994-01-24 1997-08-25 Abb Installaatiot Oy Menetelmä ja järjestelmä lämmitys- ja/tai jäähdytystehon siirtämiseksi
FI98856C (fi) * 1994-01-24 1997-08-25 Abb Installaatiot Oy Termisen energian jakelujärjestelmä
EP0916913A3 (fr) * 1997-11-14 2000-05-31 ELIN EBG Elektrotechnik GmbH Procédé et dispositif de production d'énergie calorifique
DE29912994U1 (de) * 1999-07-26 1999-11-04 Kuehling Michael Ökonomisch-ökologische Heizzentrale für Einfamilienhäuser, Wohn- und Gewerbeanlagen und Steuerung derselben
US6610250B1 (en) * 1999-08-23 2003-08-26 3M Innovative Properties Company Apparatus using halogenated organic fluids for heat transfer in low temperature processes requiring sterilization and methods therefor
JP2001183030A (ja) * 1999-10-12 2001-07-06 Kubota Corp 地熱採熱試験装置
JP2001296073A (ja) * 2000-04-12 2001-10-26 Kubota Corp 熱源評価方法、及び、その方法に用いる特性表示具
JP2002181381A (ja) * 2000-12-12 2002-06-26 Sekisui Chem Co Ltd 給湯システム
DE10226870B4 (de) * 2002-06-12 2004-05-13 MSR-Service für HKS-Anlagen Öl- und Gasbrenner GmbH Hausanschlussstation für Fernwärme
JP4229881B2 (ja) * 2004-06-23 2009-02-25 サンポット株式会社 ヒートポンプシステム
JP4719873B2 (ja) * 2004-09-15 2011-07-06 国立大学法人山口大学 冷温水用腐食抑制性流れ促進剤および冷温水熱媒における腐食抑制流れ促進方法
JP3976773B2 (ja) * 2006-03-01 2007-09-19 シャープ株式会社 ヒートポンプ給湯機
JP4859560B2 (ja) * 2006-07-04 2012-01-25 三菱マテリアルテクノ株式会社 井戸を利用したヒートポンプ装置
JP2009542883A (ja) * 2006-07-12 2009-12-03 ゾルファイ フルーオル ゲゼルシャフト ミット ベシュレンクテル ハフツング フルオロエーテル化合物を用いた加熱・冷却方法、これに適した組成物およびその用途
DE102008046620B4 (de) * 2008-09-10 2011-06-16 Thermea. Energiesysteme Gmbh Hochtemperaturwärmepumpe und Verfahren zu deren Regelung
EA201491807A1 (ru) * 2009-06-16 2015-05-29 Дек Дизайн Микэникл Кэнсалтентс Лтд. Система энергоснабжения
CN101581517B (zh) * 2009-06-16 2011-01-26 天津大学 单回路地热井下换热器热泵系统
DE202009016576U1 (de) * 2009-12-08 2011-01-13 Gebhardt, Peter Vorrichtung zur Wärmegewinnung umfassend zwei Wärmepumpen
JP2012057836A (ja) * 2010-09-07 2012-03-22 Daikin Industries Ltd 地中熱交換器、及びそれを利用したヒートポンプ
KR101107089B1 (ko) 2011-10-04 2012-01-30 주식회사 에스이티 히트 펌프를 이용한 지역 냉난방 시스템
CN202403323U (zh) * 2012-01-05 2012-08-29 寿光泰达空调设备有限公司 污水源热泵蓄热供热系统
DE202012103891U1 (de) * 2012-10-11 2012-12-10 Bürger-Energie Fischerbach eG i. Gr. Versorgungsnetz
CN102980234B (zh) * 2012-12-10 2014-12-31 安徽日源环保能源科技有限公司 一种高温地热水串联供暖方法

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2298768A1 (fr) * 1975-01-27 1976-08-20 Parica Circuit pour la recuperation optimale de la chaleur d'une eau a temperature moyenne
US5326456A (en) * 1993-04-02 1994-07-05 Exxon Research And Engineering Company Upgrading of bitumen asphaltenes by hot water treatment containing carbonate (C-2726)
US20120272948A1 (en) * 2009-08-25 2012-11-01 Danfoss A/S Heat storage system
US20140245763A1 (en) * 2011-09-30 2014-09-04 Siemens Aktiengesellschaft High-temperature heat pump and method of using working medium in a high-temperature heat pump
DE102013211087A1 (de) * 2013-06-14 2015-01-15 Siemens Aktiengesellschaft Verfahren zum Betrieb einer Wärmepumpenanordnung und Wärmepumpenanordnung

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018206334A1 (fr) * 2017-05-12 2018-11-15 Siemens Aktiengesellschaft Dispositif et procédé pour accroître le rendement thermique d'une source de chaleur
US11300334B2 (en) * 2017-05-12 2022-04-12 Siemens Energy Global GmbH & Co. KG Device and method for increasing the thermal output of a heat source
CN108518717A (zh) * 2018-04-28 2018-09-11 北京华誉能源技术股份有限公司 一种市政供热系统、供热方法及计费方法
EP4249813A1 (fr) * 2022-03-21 2023-09-27 Wolfgang Jaske und Dr. Peter Wolf GbR Procédé de gestion d'énergie d'un réseau thermique

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DE102013214891A1 (de) 2015-02-05
CN105431686B (zh) 2019-03-15
CN105431686A (zh) 2016-03-23
KR20160036618A (ko) 2016-04-04
KR101775568B1 (ko) 2017-09-07
EP2994699A1 (fr) 2016-03-16
JP2016525669A (ja) 2016-08-25
CA2919753A1 (fr) 2015-02-05

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