EP3080540A1 - Procédé et dispositif pour charger un accumulateur en couches thermique - Google Patents

Procédé et dispositif pour charger un accumulateur en couches thermique

Info

Publication number
EP3080540A1
EP3080540A1 EP15702408.4A EP15702408A EP3080540A1 EP 3080540 A1 EP3080540 A1 EP 3080540A1 EP 15702408 A EP15702408 A EP 15702408A EP 3080540 A1 EP3080540 A1 EP 3080540A1
Authority
EP
European Patent Office
Prior art keywords
working fluid
heat
thermal
pressure
heat transfer
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP15702408.4A
Other languages
German (de)
English (en)
Inventor
Uwe Lenk
Florian REISSNER
Jochen SCHÄFER
Alexander Tremel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP3080540A1 publication Critical patent/EP3080540A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F28D20/025—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat the latent heat storage material being in direct contact with a heat-exchange medium or with another heat storage material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • F24H4/04—Storage heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H7/00—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release
    • F24H7/02—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
    • F28D20/0039—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material with stratification of the heat storage material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
    • 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
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the invention relates to a method and a device for loading a thermal stratified storage.
  • Thermal stratified storages allow the generation of energy from their use to decouple in time. Especially with fluctuating energy sources such as renewable energy, provides such a temporal Entkopp ⁇ development, access to energy, particularly electricity, sure.
  • Thermal stratified storage tanks can be coupled with heat pumps that pump thermal energy (heat) from a cold to a hot reservoir, the stratified thermal storage, while absorbing electrical energy.
  • thermal energy heat
  • By using a coupled with a heat pump thermal layer memory thus the generation of thermal energy and whose delivery can be decoupled in time to a heat consumer, whereby, for example Lastspit ⁇ zen can be compensated for in the energy requirements, so that overall improved security of supply.
  • a thermal stratified storage is charged with heat by means of a heat pump.
  • the heat is transferred via walls of a heat exchanger to the thermal stratified storage.
  • certain temperature differences are required as a driving force for heat transfer.
  • the temperature level of the removable storage layer heat ie their value in use.
  • space must be made available for the heat transfer surfaces of a heat exchanger, which can not be used for the storage of thermal energy.
  • a thermal stratified storage with a heat exchanger having heat transfer surfaces is charged by means of the heat pump by a working fluid of the heat pump on the primary side absorbs heat at a low temperature level and within the heat exchanger on the secondary ⁇ the heat of the working fluid at a higher tempera ⁇ turn level transferred to a heat transfer of the thermal Schichtspei ⁇ chers (secondary side).
  • Layer memory is located.
  • the heat from the heat pump to the thermal stratified storage tank is always transferred through a condenser in which condensation of the working fluid of the heat pump takes place, the condenser being outside in the former case and within the second stratified charge accumulator and always in thermal contact with the heat carrier of the thermal stratified storage tank.
  • the capacitors according to the prior art large-scale heat transfer surfaces require a large space requirement and on the other hand reduce the cost of the thermal stratified ⁇ on the basis of high investment costs.
  • the invention is therefore based on the object to improve the loading of a thermal stratified storage with thermal energy.
  • the object is achieved by a method having the features of independent claim 1 and by a device having the features of independent claim 15.
  • advantageous refinements and developments of the invention are given.
  • the pressure in the thermal stratified storage at the point of introduction is greater than or equal to the condensation pressure of the working fluid.
  • the working fluid of the heat pump is introduced directly in the gas ⁇ shaped state of aggregation in the liquid heat carrier of the thermal stratified storage, whereby a direct material contact between the heat carrier and the working fluid takes place.
  • the direct material ⁇ Liche contact with a condensation of the gaseous working fluid leads. This is the case, therefore, since the pressure in thermi ⁇ rule layer memory at the point of introduction of the gaseous working fluid, or in a portion of the thermal layer memory in which the gaseous working fluid is ⁇ tet Weglei is greater than or equal to the condensation pressure of the working fluid.
  • the condensation pressure of the working fluid here depends on the temperature at the point of introduction and must be set according to the temperature mentioned.
  • the pressure is referred to, in which the gaseous working fluid of the heat pump from the gaseous to the liquid state passes namely in the Tem ⁇ temperature, which is present at the point of discharge of the working fluid in the layer memory.
  • the condensate is sationsdazzling of the gaseous working fluid at the Einlei ⁇ processing point or in a portion of the thermal
  • the inventive apparatus for loading a thermal layer memory comprises a thermal Schichtspei ⁇ cher with a liquid heat transfer medium and a heat pump with a working fluid, wherein the thermal layer storage and the heat pump are configured and coupled such that the working fluid (in the gaseous state than ⁇ superheated steam or as saturated steam) introduced into the heat transfer medium at an introduction point and brought into direct material contact with the heat transfer medium, wherein the pressure of the thermal stratified storage at the point of introduction is greater than or equal to the condensation pressure of the working fluid.
  • the device according to the invention allows a direct material contact of the gaseous and consequently also of the condensed (liquid) working fluid with the liquid heat carrier. This results in the already explained inventions to the invention method similar and equivalent ADVANTAGES ⁇ le.
  • the working fluid condensed in the thermal stratified storage tank is returned to the heat pump.
  • a working fluid is used, the density after the Kondensa ⁇ tion in the thermal stratified storage is greater than or equal to the density of the heat carrier, with a genuinely always greater density is preferred.
  • Layer memory can be introduced or introduced.
  • the denser By the action of gravity, which prevails at the location of the thermal layer memory, the denser compared to Wär ⁇ melie working fluid to and / or during its Condensation from the point of introduction to a lower end of the thermal stratified storage sink.
  • the relative terms upper and lower as is known, based on the prevailing before ⁇ direction of gravity.
  • the heat transfer medium in the thermal stratified storage tank will have the highest temperature at its upper end.
  • the advantage of the greater density of the condensed working fluid and the resulting sinking of the working fluid is that the working fluid is subcooled to the temperature of the thermal stratified storage at the lower end, whereby the heat transfer medium and, as a consequence, the thermal stratified storage are charged with additional heat becomes.
  • Another advantage is that the condensed working fluid condenses by the decrease and the associated continuous material contact with the heat transfer medium, almost completely. After the condensation of the condensed working fluid and its accumulation at the lower end of the thermal stratified storage, for example at the bottom, it can be returned from there to the heat pump.
  • one and the same fluid is used for the working fluid in the liquid state and the liquid heat transfer medium.
  • additional separators which separate the working fluid from the heat carrier, for example be ⁇ before it is returned to the heat pump or passed to a heat consumer, omitted.
  • a working fluid which has a condensation pressure of less than 1 MPa at a temperature of 100 ° C. (373.15 K).
  • Low pressure fluids Working fluids that have a condensation pressure of less than 1 MPa at a temperature of 100 ° C, here referred to as low pressure fluids.
  • An advantage of such low-pressure fluids is that they allow use of the method according to the invention in combination with known thermal stratified storage devices. This is the case, therefore, since according to the prior art typical thermal Schichtspei ⁇ cher, in particular water storage layer, have a pressure that is less than 1 MPa and more preferably in the range from Be ⁇ 0.3 MPa to 1 MPa.
  • Heat pumps used in typical working fluids such as the fluids R134a, R400c or R410a, have a condensation ⁇ pressure which ranges from 2 MPa to 4 MPa at 100 ° C. The condensation pressure of the said working fluids is therefore significantly greater than the pressure which is typically in thermal
  • Layer accumulation is present, so that no condensation ⁇ tion of the working fluid takes place at an initiation of the working fluid at a temperature of 100 ° C.
  • low-pressure fluids have a condensation pressure which is in the range of the pressures prevailing in stratified reservoirs, so that they condense in contact with the liquid heat carrier of the thermal stratified reservoir.
  • working fluids containing at least one of the substances 1, 1, 1, 2, 2, 4, 5, 5, 5-nonafluoro-4- (trifluoromethyl) -3-pentanones (trade name Novec TM 649), perfluoromethylbutanone, l Chloro-3,3,3-trifluoro-1-propene,
  • the substances mentioned can be used according to the present invention in combination with known in the prior art thermal stratified storage.
  • Novec TM 649 has a condensation pressure of 0.45 MPa
  • perfluoromethylbutanone a condensation pressure of 0.89 MPa
  • cyclopentane has a condensation pressure of 0.42 MPa.
  • the condensation pressure of said fluids is thus at 100 ° C significantly below the condensation pressure of, for example R134a, which has a Kondensa ⁇ tion pressure of about 3.97 MPa.
  • Another advantage of the substances mentioned is their technical handling.
  • the substances Novec TM 649 and perfluoromethyl butanone belong to the substance group of fluoroketones, while cyclopentane belongs to the substance group of cycloalkanes.
  • water is used as the working fluid.
  • additional separators which are able to separate the working fluid from the heat carrier, can advantageously be dispensed with.
  • hydrostatic thermal stratified storage which build up the pressure in the thermal stratified storage solely by the hydrostatic pressure of the water column, the height of the point of introduction of the working fluid in the heat transfer medium is therefore not important.
  • the water layer accumulator can be loaded at its upper end by the introduced gaseous and then condensed working fluid, whereby advantageously only a small time delay between the loading of the stratified water storage and the achievement of the desired temperature at the upper end.
  • a working fluid is used which is immiscible in the liquid (condensed) state of aggregation with the liquid heat carrier.
  • the condensed working fluid and the liquid heat carrier form a two-phase liquid, wherein one phase is formed by the condensed working fluid and the other phase by the liquid heat carrier.
  • Perfluoromethylbutanone and cyclopentane in water which is particularly suitable as a heat transfer medium, poorly soluble and therefore miscible only in small amounts with water. For example, only 20 ppm of water dissolve in Novec TM 649.
  • the gaseous working fluid is introduced by means of a distribution device in the heat carrier, wherein the distributor homogeneously distributes the working fluid in a layer of constant temperature of the heat carrier.
  • Thermal stratified storage for example Wasser Schweizerspei ⁇ cher, have a layered structure with respect to the temperature of its heat carrier, each layer having a specific temperature and density. With regard to the efficiency of the heat transfer from the working fluid of the heat pump to the
  • Heat transfer it is therefore advantageous to distribute the gaseous working fluid in ⁇ a layer of the heat carrier uniformly or ho ⁇ Mogen.
  • uniform and homogeneous, ⁇ such as temperature or density of a layer are always app- roximativ to understand.
  • Typical stratified storages are vertical - relative to the am
  • Stratified memory predominant gravity - aligned, so that the individual layers of the stratified memory extend horizontally. Due to the uniform distribution of the gaseous working fluid in a layer of the liquid heat carrier, the surface of the material contact (contact surface) between the heat carrier and the working fluid increases, whereby the efficiency of the heat transfer from the working fluid to the heat transfer medium is improved.
  • distributing devices are, for example horizontal distribution pipe systems as they come in layered tanks for appli ⁇ -making in question.
  • the distribution devices known there lead to a reduction in the rate of entry of the working fluid into the heat transfer medium (see Göppert et al., Chemie Ingenieurtechnik, 2008, 80 No. 3).
  • the entrance velocity of the gaseous working fluid can be regulated by changing the cross-sectional area of entrance holes of the distributor.
  • a further advantage of the regulation of the cross-sectional areas of the inlet holes that a primary bubble size of gasför ⁇ -shaped working fluid can be adjusted.
  • a regulated pressure accumulator In one embodiment of the method is used as a thermal stratified storage a regulated pressure accumulator.
  • the pressure within the thermal stratified accumulator can be regulated into a specific pressure range.
  • the pressure within the thermal stratified accumulator can be regulated into a specific pressure range.
  • Accumulator be adapted to the condensation pressure of the working fluid, so that it is independent of the prevailing at the entry point temperature to a condensation of the working fluid. For example, this allows the gaseous working fluid to be introduced at the highest possible entry point of the stratified storage tank.
  • the temperature of a layer of the stratified storage or accumulator is correlated with the height of the layer, so that the highest possible point of introduction corresponds to the highest possible temperature.
  • heat is supplied to the working fluid from the thermal stratified storage tank before it is introduced into a compressor of the heat pump.
  • Layer memory is returned. Due to the direct material contact of the working fluid with the heat transfer medium of the thermal stratified storage tank, introduction of the heat transfer medium into the working fluid and thus into a circulation of the working fluid within the heat pump can not be prevented in principle. In particular, in the evaporator of the heat pump thus accumulates not (with) vaporized, liquid heat transfer medium. This accumulating in the evaporator heat carrier is advantageously removed from the evaporator by means of a droplet and returned to the thermal stratified storage.
  • a line of the heat carrier to use its heat to ei ⁇ nem heat consumer wherein the heat transfer medium is passed through a separator before use in the heat consumer.
  • a line of the heat carrier through a separator is provided in particular in the direct removal of the heat carrier from the thermal stratified storage.
  • direct would take the heat carrier is carried by the material contact according to the invention between the working fluid and the heat transfer medium, a part of the working fluid with the heat carrier ⁇ .
  • the discharge of the working fluid droplets (emulsion) or as dissolved in the heat transfer component (solution) take place.
  • the separator ensures that the discharged portions of the working fluid do not reach the heat consumer and can optionally be returned to the thermal stratified storage and / or to the heat pump.
  • active droplet separators and / or coalescing separators are suitable for the separation.
  • Another way to verhin the discharge of working fluid ⁇ countries is to decrease the solubility of the working fluid in the heat transfer due to the reduced temperature of the heat consumer. This is the case, having a hö ⁇ here solubility at higher temperature for mixtures. The reduced temperature of the heat consumer, the Ar ⁇ beitsfluid precipitates and can thus be separated materially from the heat transfer medium.
  • a separator lying on the side of the heat exchanger, which separates the working fluid from the heat carrier, can be dispensed with.
  • a phase change material (narrow phase change material, PCM) is used in the thermal stratified storage for storing thermal energy.
  • the stratified storage thus comprises two heat carriers, wherein the further heat carrier is designed as a phase change material.
  • Phase change materials or phase change memory are preferred because they can store thermal energy loss with many repeat cycles and over a long period of time.
  • a phase change material is preferred whose melting temperature (phase change temperature) is smaller than the condensation temperature of the working fluid (at the condensation pressure).
  • the condensation ⁇ temperature of the working fluid can be 130 ° C, so that a melting temperature of 125 ° C of the phase change material be ⁇ is vorzugt.
  • a melting temperature which is at most 5% lower than the condensation temperature is preferred.
  • the stratified storage may comprise further heat carriers present in the solid state of matter.
  • the porosity of the solid heat transfer medium can be adapted to the purpose.
  • the porosity can be selected such that a decrease in the condensed working fluid, which has a greater density than the liquid heat carrier, is made possible.
  • Figure 1 is coupled to a heat pump pressure accumulator, wherein a working fluid of the heat pump is introduced directly into the heat carrier of the pressure accumulator;
  • FIG. 2 shows a coupled to the heat pump hydrostatic pressure accumulator, wherein the working fluid of the heat pump is in turn introduced directly into the heat carrier of the pressure accumulator.
  • Figure 1 shows a schematic representation of a regulated pressure accumulator 2, which is coupled to a heat pump 6 such that the working fluid 4 of the heat pump 6 via a Ver ⁇ dividing device 12 in a height 8 of the pressure accumulator 2 in the heat transfer medium 10, which is in direct material contact with the working fluid 12, is distributed.
  • the heat pump 6 comprises a compressor 14, a vaporization fer 16, an expansion valve 20, a separator 18, a mist eliminator 15 and a check valve 22.
  • the working fluid 4 is circulated in the heat pump 6 against the Time ⁇ gersinn 36.
  • an expansion vessel 24, a pump 28, a further expansion valve 30 and a reservoir 26 for the heat carrier 10 can be seen.
  • the aforementioned components 24, 26, 28, 30 serve to regulate the pressure accumulator 2 and / or the heat carrier 10.
  • water is used as the heat carrier 10.
  • the gaseous working fluid 4 is introduced after the compressor 14 in the height 8 of the pressure accumulator 2 via the distributor 12 in the heat carrier 10 and thus brought into direct material contact with the heat carrier 10.
  • the temperature of the pressure accumulator 2 in the Einlei ⁇ processing height 8 for example, 130 ° C. Is used as the working fluid at ⁇ play as Novec TM 649, the pressure must be in
  • Pressure accumulator 2 be at least 0.9 MPa, so that an immediate condensation of the gaseous working fluid 4 he follows ⁇ .
  • the working fluid 4 Novec TM 649 which has a density of about 1300 kg / m 3 , can be used.
  • the heat carrier 10 10 water is used, which has a density of 1000 kg / m 3 , so that the working fluid 4 has a greater density than the varnishträ ⁇ ger 10.
  • the working fluid 4 is lowered by the influence of gravity 100 on the floor 9 of the accumulator 2 by the lowering of the working fluid 4 on the bottom 9 of the accumulator 2, the working fluid 4 from ⁇ Partially subcooled until reaching the present on the bottom 9 temperature of the pressure accumulator 2, so that the Ar ⁇ beitsfluid 4 additional heat is removed. From the clotting ⁇ gen miscibility of Novec TM 649 and water one at the bottom 9-settling phase of the working fluid 4 to the pressure accumulator 2 can then be removed at the bottom 9 and returned to the working circuit 36 of the heat pump 6 via the Ab ⁇ separator 18 resulted becomes.
  • (liquid) separator 18 ensures that no heat carrier 10 is introduced from the pressure accumulator 2 in the working circuit 36 of the heat pump 6.
  • a working fluid 4 which has a lower density than water 10, for example cyclopentane (C 5 H 10 ) with a density of 650 kg / m 3 , then the working fluid 4 rises after the condensation and must therefore at an upper En - De the pressure accumulator 2 are removed.
  • cyclopentane C 5 H 10
  • the check valve 22 prevents heat carrier 10 is discharged into the compressor 14 and thus in the working circuit 36 of the heat pump 6.
  • Figure 2 shows an alternative embodiment of the method according to the invention, wherein instead of a regulated
  • Accumulator 2 use a hydrostatic accumulator 3 it becomes.
  • the heat pump 6 comprises shown and already in Fi gur 1 ⁇ elements discussed.
  • the pressure in the pressure accumulator 3 is generated solely via the liquid column of the water 10.
  • Novec TM 649 as beitsfluid Ar 4 in the hydrostatic pressure storage at a temperature of 110 ° C initiated, then a pressure of Wenig ⁇ least 0.6 MPa for the condensation of the working fluid 4 ⁇ not agile.
  • the entry point or the entry height 8 of the working fluid 4 must be selected in the pressure accumulator 3 so that at least 50 m of water 10 are above the inlet height 8 of the working fluid 4.
  • a cold water layer 32 is placed at the upper end of the pressure accumulator 3.
  • the cold water layer 32 is separated by a separator 34 from the water 10 of the hydrostatic pressure accumulator 3.
  • the working fluid 4 sinks due to its greater density in comparison to the heat carrier 10 due to the influence of gravity 100 on the bottom 9 of the hydrostatic pressure accumulator 3.
  • separator 18 the working circuit 36 of the heat pump 6 is ⁇ leads. If the heat carrier 10 is denser than the working fluid 4, removal of the working fluid 4 is provided at an upper end of the hydrostatic pressure accumulator 3.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

L'invention concerne un procédé et un dispositif pour charger un accumulateur en couches thermique (2, 3). Un fluide de travail (4) d'une pompe à chaleur (6) est introduit à l'état gazeux au niveau d'au moins un point d'introduction (8) dans un caloporteur liquide (10) de l'accumulateur en couches thermique (2, 3) et amené en contact physique direct avec le caloporteur (10). Dans l'accumulateur en couches thermique (2, 3), la pression au niveau du point d'introduction (8) est supérieure ou égale à la pression de condensation du fluide de travail (4).
EP15702408.4A 2014-02-17 2015-01-21 Procédé et dispositif pour charger un accumulateur en couches thermique Withdrawn EP3080540A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014202849.3A DE102014202849A1 (de) 2014-02-17 2014-02-17 Verfahren und Vorrichtung zum Beladen eines thermischen Schichtspeichers
PCT/EP2015/051130 WO2015121039A1 (fr) 2014-02-17 2015-01-21 Procédé et dispositif pour charger un accumulateur en couches thermique

Publications (1)

Publication Number Publication Date
EP3080540A1 true EP3080540A1 (fr) 2016-10-19

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EP15702408.4A Withdrawn EP3080540A1 (fr) 2014-02-17 2015-01-21 Procédé et dispositif pour charger un accumulateur en couches thermique

Country Status (8)

Country Link
US (1) US20170010052A1 (fr)
EP (1) EP3080540A1 (fr)
JP (1) JP2017506322A (fr)
KR (1) KR20160121570A (fr)
CN (1) CN105917187A (fr)
CA (1) CA2939736C (fr)
DE (1) DE102014202849A1 (fr)
WO (1) WO2015121039A1 (fr)

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DE202016102914U1 (de) * 2016-06-01 2017-06-02 Thomas Piller Pufferspeicher
CN110546442B (zh) * 2017-04-19 2020-09-15 三菱电机株式会社 热泵装置
DE202018100856U1 (de) 2018-02-15 2018-03-01 Thomas Piller Pufferspeicher
DE202019105940U1 (de) 2019-10-25 2020-10-27 Thomas Piller Wärmespeichereinheit
KR102450312B1 (ko) * 2020-09-23 2022-10-04 주식회사 유라코퍼레이션 정션블록
DE102022106951A1 (de) 2022-03-24 2023-09-28 Thomas Piller Wärmespeichereinheit

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US20170010052A1 (en) 2017-01-12
CN105917187A (zh) 2016-08-31
CA2939736A1 (fr) 2015-08-20
JP2017506322A (ja) 2017-03-02
CA2939736C (fr) 2018-03-27
DE102014202849A1 (de) 2015-08-20
WO2015121039A1 (fr) 2015-08-20

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