WO2016135209A1 - Système de stockage d'énergie thermique en spirale - Google Patents

Système de stockage d'énergie thermique en spirale Download PDF

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Publication number
WO2016135209A1
WO2016135209A1 PCT/EP2016/053891 EP2016053891W WO2016135209A1 WO 2016135209 A1 WO2016135209 A1 WO 2016135209A1 EP 2016053891 W EP2016053891 W EP 2016053891W WO 2016135209 A1 WO2016135209 A1 WO 2016135209A1
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Prior art keywords
flow path
fluid
energy storage
thermal energy
storage system
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Ceased
Application number
PCT/EP2016/053891
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English (en)
Inventor
Michael MCKEEVER
Marek REBOW
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Technological University Dublin
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Technological University Dublin
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Filing date
Publication date
Application filed by Technological University Dublin filed Critical Technological University Dublin
Publication of WO2016135209A1 publication Critical patent/WO2016135209A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0472—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled
    • 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
    • F28D20/021—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 and the heat-exchanging means being enclosed in one container
    • 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
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/08—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
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/10—Heat storage materials, e.g. phase change materials or static water enclosed in a space
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/22—Safety or protection arrangements; Arrangements for preventing malfunction for draining
    • 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 present application relates to energy storage systems and in particular to energy storage systems employing a phase change material.
  • TES thermal energy storage
  • PCM phase change material
  • PCM materials offer improvements over conventional sensible storage, an identified problem is that the thermal conductivity of the PCM is lower when in the solid phase and as a result it is difficult to get heat to flow through the solid PCM material to cause the PCM material to melt.
  • the present application is directed at this problem.
  • GB2484539 discloses an arrangement of a heat exchanger employing PCM material.
  • the present application provides a number of improvements upon
  • the present application provides a thermal energy storage system as detailed in claim 1.
  • Advantageous embodiments are provided in the dependent claims.
  • the present application provides a thermal energy storage system comprising a cylindrical tank having a base.
  • a layered arrangement is provided within the tank, with the layers arranged along the cylindrical axis of the tank.
  • at least one of the layers comprises:
  • a first fluid inlet for receiving a first fluid flow
  • a first fluid outlet in fluid communication by a first flow path to the first fluid inlet, wherein the first flow path is arranged in a spiral about the cylindrical axis from the first fluid inlet to the first fluid outlet.
  • a first manifold provides a fluid connection from the outlet of the layer to the inlet of a first flow path in an adjacent layer along the cylindrical axis and PCM material is provided within the tank about the layered arrangement.
  • the first fluid flow path may be formed from a single continuous section of pipe.
  • the first fluid flow path is formed without using a heat exchange plate to join concentric sections of the spiral of the first fluid flow path.
  • the first manifold is arranged generally in a direction parallel to the cylindrical axis.
  • the layers are suitable arranged to substantially parallel to one and other along the cylindrical axis.
  • the interlayer separation distance is suitably the same between all adjacent layers of the arrangement.
  • the spiral may be substantially arranged as an Archimedean spiral.
  • the at least one layer further comprises a second fluid inlet for receiving a second fluid flow; a second fluid outlet in fluid communication by a second flow path to the second fluid inlet; wherein the first and second fluid flow paths are arranged concentrically in a spiral.
  • a second manifold is provided to form a fluid connection from the second fluid outlet to the inlet of second fluid flow path in an adjacent layer along the cylindrical axis.
  • connecting pipes are provided to each of the first and second fluid inlet and each of the first and second fluid outlet, and wherein the connecting pipes are arranged parallel to one in a direction transverse to the cylindrical axis.
  • an opening may be defined in the cylindrical wall to allow the connecting pipes to pass therethrough.
  • a seal may be provided to seal the space between the connecting pipes and the opening to prevent leakage of phase change material.
  • the second fluid flow path may be formed from a single continuous section of pipe.
  • the second fluid flow path may be formed without a heat exchange plate joining concentric sections of the spiral of the second fluid flow path or adjacent sections of the first flow path.
  • the second manifold may be arranged generally in a direction parallel to the cylindrical axis.
  • the interlayer separation distance may be substantially the same as the inter spiral distances between the first fluid flow path and a second fluid flow path within a layer.
  • the phase change material has a melting point in the range -120C to 220C and preferably the phase change material has a melting point in the range of 50 * C to 903 ⁇ 4.
  • the phase change material may be selected from the group consisting of waxes and salt hydrates.
  • An outlet may be provided toward the bottom of the cylindrical wall or in the base of the tank to allow for draining of PCM material from the tank.
  • Figure 1 is a top view of a first coil assembly for use in a first aspect of the present application
  • Figure 2 is a top view of a second coil assembly for use in combination with the first aspect of Figure 1 ;
  • Figure 3 is a view of an inner unit assembly comprising a layered arrangement of the coils of Figure 1 and Figure 2 with connections and support frame;
  • Figure 4 is a view of the assembly of Figure 3 within an exterior tank housing and piping outlets for the first and second coils and base feet;
  • Figure 5 is a front side view of the inner unit assembly of Figure 3;
  • Figure 6 is a rear side view of the inner unit assembly of Figure 3;
  • Figure 7 is a top view of Figure 4.
  • Figure 8 illustrates exemplary temperature profiles obtained from a system
  • Figure 9 illustrates the nature of the shape of the first and second coils shown in Figures 1 and 2.
  • PCM storage there are many advantages to using PCM storage, including, for example smaller size comparable to conventional storage.
  • Research by the present inventor has also identified a limitation of PCM storage systems, namely that latent heat storage depends on the thermal conductivity of the PCM, which is lower when in its solid phase. This means that it may be difficult to get the heat to flow through the solid PCM in order to melt it. Thick PCM storage blocks may only partially melt when exposed to thermal energy and overall latent heat storage capacity is reduced as a consequence.
  • webs heat transfer plates
  • the inclusion of webs in a design makes it difficult filling such heat storage device with PCM material and also adds cost and construction complexity.
  • conventional configurations lack flexibility in the manner of their construction to accommodate different uses.
  • the present application addresses both aspects by providing a layered arrangement in which each layer has two separate fluid flow paths each arranged in a spiral in a tank with the PCM.
  • the thermal energy storage comprises a tank for holding a PCM material.
  • the tank is most suitably substantially cylindrical in shape.
  • the tank 40 comprises a base to which is joined a cylindrical wall 42 which extends upwards therefrom.
  • the shape of the base may be planar or it may be concave or convex shaped.
  • the base may be supported by a plurality of legs 46 to allow for insertion of the forks of a forklift or other means to lift/move the tank. Similarly, the legs may have castors to allow for movement of the tank.
  • An outlet 44 may be provided in the base or in the region of the cylindrical wall adjoining the base to facilitate removal of PCM material from the tank.
  • the outlet suitably comprises a valve (not shown).
  • the valve may be manually operable to facilitate emptying of the tank of PCM material as required, for example during inspection or maintenance.
  • the top of the cylindrical wall is suitably shaped for engagement with a lid (not shown).
  • a flange 48 positioned at the top of the cylindrical wall may provide an abutment surface extending about and transverse to the cylindrical wall.
  • the abutment surface may have a plurality of bolt holes 72 provided therein for alignment with corresponding features on the lid to facilitate securing of the lid to the tank.
  • a layered arrangement 30 of pipework is provided within the tank.
  • the individual layers 80 are concentrically arranged along the cylindrical axis of the tank.
  • Each of the layers 80 has a first coil or flow path 12 starting at one opening at a manifold 15 and ending at an opening provided at a manifold 14 at the opposite end of the first flow path.
  • the first flow path allows for liquid to flow from the first opening 15 to the second opening 14 or vice versa depending on the configuration as will be explained below.
  • the first flow path is arranged in a spiral about the cylindrical axis.
  • the first flow path is suitably constructed of a single piece of pipework which has been formed in a spiral shape.
  • each spiral flow path from a single piece of pipework minimises the risk of failure in use and makes for a simpler and less expensive construction.
  • the position of the inlet and outlet of the first flow path are reversed in each layer.
  • the inlet may be taken to be at the outside end of the spiral where the pipework joins at manifold 15 to an external connection 17 for connection to a source of heating fluid (e.g. water) and the outlet may be taken to be at the centre of the spiral where the pipework joins manifold 14.
  • a source of heating fluid e.g. water
  • the inlet for the first flow path will be at manifold 14 and the outlet will be at manifold 15.
  • outlets 16 is connected to the manifold 15 by a vertical pipe connection 82 which extends from and connects to the outlet 16 at the top and to a connection 84 at the bottom of the manifold.
  • each of the layers 80 further comprises a second flow path 22 having an opening to connect to a manifold 25 at one end and ending at an opening at the opposite end to connect to a further manifold 24.
  • the second flow path in each layer allows for liquid to flow from the manifold 25 to the further manifold 24 or vice versa depending on the configuration as will be explained below.
  • the second flow path is suitably the same shape and dimensions of spiral as the first flow path.
  • the spirals in each layer are rotationally offset at an angle of about 180° about the cylindrical axis with respect to one and other. In practise, the preferred angle is either above or below 180° so that the outlets of the first and second flow paths can be arranged to exit the tank together in parallel at the same point.
  • each of the first and second flow paths is separately fabricated before being assembled together. This means that making connections between the manifolds and spiral pipework is significantly easier.
  • the second flow path of each layer is suitably constructed of a single piece of pipework which has been formed in a spiral shape. It will be appreciated that forming each spiral flow path from a single piece of pipework minimises the risk of failure in use and makes for a simpler and less expensive construction. The position of the inlet and outlet of the second flow path are reversed in each layer.
  • the inlet may be taken to be at the outside end of the spiral where the pipework joins at manifold 25 to an external connection 26 for connection to a source of heating fluid (e.g. water) and the outlet may be taken to be at the centre of the spiral where the pipework joins manifold 24.
  • a source of heating fluid e.g. water
  • the outlet may be taken to be at the centre of the spiral where the pipework joins manifold 24.
  • the inlet for the first flow path will be at manifold 24 and the outlet will be at manifold 25.
  • the outlet connection from the second flow path of the top layer is connected to the inlet of the next (second layer) layer.
  • the connection at manifold 25 of the first layer will connect to the next (third layer) layer.
  • Outlet 26 is connected to the manifold 25 by a vertical pipe connection 86 which extends from and connects to the outlet 27 at the top and to a connection 88 at the bottom of the manifold 25.
  • Each of the outlet/inlet pipes 26, 27 from the second fluid flow path are extend across the top so as to exit from the tank beside the outlet ⁇ inlets of the first flow path.
  • an opening is suitably provided in the abutment surface and a corresponding section of the upper part of the cylindrical wall to accommodate fluid outlet and inlet pipes.
  • a sealing section may be provided which is shaped to allow the outlet and inlet pipes to be inserted and pass through and at the same time shaped to match with the opening in the abutment surface and top of the cylindrical wall so as to form a seal.
  • This sealing section may be shaped or configured to provide a seal.
  • first and second fluid flow paths may be connected in parallel, i.e. where there is just a single supply of fluid.
  • the respective inlets and outlets may be reversed. In this way, the fluid may enter one flow path at the top of the tank and the other flow path at the bottom.
  • the tank may be configured as a heat exchanger with one of the fluid flows receiving a hot fluid and the other flow containing a fluid to be heated by the hot flow (i.e. having a lower temperature relative to the hot fluid).
  • the tank may be configured as a heat exchanger with one of the fluid flows receiving a hot fluid and the other flow containing a fluid to be heated by the hot flow (i.e. having a lower temperature relative to the hot fluid).
  • the tank may be configured as a heat exchanger with one of the fluid flows receiving a hot fluid and the other flow containing a fluid to be heated by the hot flow (i.e. having a lower temperature relative to the hot fluid).
  • the layered assembly 30 of first and second flow paths may be constrained by a frame or support 32 to allow for ease of lifting and installation into the tank 40.
  • the arrangement generally allows for the thermal storage unit to be constructed for a lower cost than alternative structures such as disclosed in GB2484539. It also may reliably be used at relatively high fluid pressures (10 bar) as the design allows for its construction with a minimum number of joints in fluid flow paths. Similarly, the arrangement allows access during manufacture for joints in the pipework to be readily formed by welding, which helps reduce costs.
  • the structure may be formed one layer at a time and separately for the first flow path and second flow paths, with the two combined afterwards, that the construction process is relatively simple. At the same time, since the length of each spiral path is the same that the process for forming them is consistent with no customisation required.
  • the length of the spiral path may be chosen to ensure that an industry standard length of pipe may be used.
  • the pipe material is suitably selected to provide for good heat transfer characteristics. Accordingly, metal may be preferred over plastics. At the same time, the material may need to be resistant to corrosion from the PCM materials present. Thus, the metal selected may be stainless steel.
  • the assembly of the present application does not employ webs (heat transfer plates) which simplifies the nature of construction and allows for example for the second coil assembly 10 simply to be lifted into place within the first coil assembly 20.
  • a further advantage of the present application is that the device is not limited to use as a heat exchanger. Instead, the two coils may be used by the same fluid to give faster charging and discharging rates of the PCM. Accordingly, in the present case, it is not necessary to have two coils in each layer. However having two coils allows a range of connections and configurations. For example, both coils may be used to charge the store and both coils may be used to discharge the store supplied by a single heat source/sink fluid circuit. In another configuration, one coil charges and discharges into a separate heat source/sink fluid circuit while the other coil charges and discharges into a different heat source/sink fluid circuit. In another configuration, both coils are connected in parallel for single charging/discharging to give a particular ⁇ and transient time constant. In another configuration, both coils are connected in parallel for single charging/discharging particular ⁇ and transient time constant.
  • the primary and secondary coils are uniform in their curvature (no tight radii bends).
  • the coils are suitably shaped as Archimedean spirals as illustrated in Figure 9.
  • the spiral may not end at or close to the centre as shown in Figure 9, but at a distance out from the centre.
  • the internal ends of the spirals are at manifolds 14 and 24.
  • Using an Archimedean spiral means that the distance is relatively constant between turns of the spirals and thus between the turns of the first and second coils in any layer.
  • the distance between the layers is selected to match that between turns so that the same PCM thickness is between all pipes in the vertical direction and in the horizontal direction. This makes the PCM easier to melt.
  • each of the primary and secondary coils is selected to be the same length, it allows for low cost manufacturing due to uniformity in construction.
  • Using a cylindrical housing reduces heat losses. It also reduces manufacturing costs and minimises materials used.
  • the PCM material used may be supplied to the tank as a powder, granular form, solid lumps or liquid. As the assembly is relatively open without the presence of webs, it readily facilitates adding the material in solid form, e.g. in powder or granular form or as lumps without having to melt it first.
  • the completed system consists of a reservoir in the form of a cylindrical tank having a removable lid.
  • the cylindrical tank in turn is employed to house a number of coils (spiral fluid flow paths in the form of layers of pipes with with each pipe arranged in a spiral).
  • the tank is also employed to house PCM material.
  • PCM phase change materials
  • phase change materials PCM
  • An example of a paraffin based phase change material is that of RT58 sold under the RUBITHERM ® trade mark available from Rubitherm Technologies GmbH of Berlin, Germany.
  • An alternative material is a salt hydrate such as for example Barium Hydroxide Octahydrate [Ba(OH)2.8H20].
  • phase change material may be employed depending on the intended application of the system.
  • any phase change material with a melting point in the range -120C to 220C may be employed application dependent.
  • the melting point of the phase change material is preferably within the range of eO'C to 90 * C.
  • the tank operates at atmospheric pressure, i.e. the PCM materials housed within the tank are not intended to be pressurised.
  • the tank operates at atmospheric pressure and may have a corrosion resistant liner, e.g. an internal Polypropylene liner for use with corrosive especially when salt hydrates are used.
  • PCM can be filled into the tank in powder, granular beads, solid chunks or liquid.
  • the coils can now be lifted in and out for inspection in the field as they are bolted to the side wall of the tank to form a seal.
  • the tank may be generally constructed using a metal such as steel.
  • an internal plastics liner e.g. polypropylene
  • barrier coating may be employed to protect the metal from corrosion, for example when salt hydrates are used as the PCM material.
  • the coils are arranged in a series of layers which are arranged along the cylindrical axis of the tank from the base to the lid.
  • Each of the coils is a spiral which extends from a region close to the wall of the tank to a region close to the centre defined by the cylindrical axis of the tank.
  • Each layer may comprise a single spiral coil.
  • each layer may comprise two coils arranged in a concentric spiral configuration.
  • the internal thermal energy storage tank system consists of two coils optimally designed to reduce construction and manufacturing costs and having a uniformity of PCM material in the inter-space between the two coils as depicted in figure 1 to figure 8.
  • the first coil 10 shown in figure 1 carries a fluid which may be referred to as the first fluid from inlet to outlet.
  • the second coil 20 shown in figure 2 carries a second fluid.
  • the system has been designed to operate in a range of modes where the first fluid and second fluid may both be used to charge the PCM material in a series or parallel flow path or separately depending on the heat sources used to melt the PCM. In a similar fashion, the discharging of the energy in the PCM may be through both coils or a single coil depending on the application.
  • the coils are provided with a number of supports to maintain their structure when being lifted in and out of the tank.
  • Vertically arranged manifolds are provided at each end of each coil to provide a fluid connection to each end of the coils.
  • This optimal design based on a spiral coil makes the PCM material the only other internal part of the storage system, i.e. if the coils are lifted out all that remains within the liner is the PCM material. This removes the necessity for internal plates which are subject to corrosion over the life of the product.
  • the inter-space between the coils in the vertical has been optimally designed to ensure minimum thermal stratification due to the ratio of the pipe surface area to the height of the tank.
  • the high ratio of pipe surface area to tank volume has been optimised to make the vertical spacing of PCM of uniform thickness.
  • the inter-space between the coils in the horizontal has been designed to be uniform between the coils.
  • the choice between the first fluid and second fluid are liquid/liquid, gas/liquid, liquid/gas or gas/gas with this type of unit. This allows a range of heat sources to be used with this storage unit.
  • the external connections of both coils are placed outside the external wall of the tank. The coils may readily take up to 10Bar pressure.
  • each of the spiral coils are formed from a single piece of pipe which is bent into a spiral.
  • the tank does not employ heat exchanger plates so there is no direct heat exchange between the first coil and second coil. Instead, heat is transferred to the PCM and from the PCM.
  • the PCM spiral thermal storage unit described herein is a low cost thermal storage solution.
  • the simple geometry of the internal heat exchanger chambers doesn't require intricate pipe work associated with other types of heat exchangers.
  • the materials used in the storage unit are standard manufacturing piping materials, and no specialised alloys and associated welding is required.
  • the number of welded joints along the pipe work has been minimised and the construction of the rectangular manifold distribution pipes between the 12 vertical pipes of each coil unit is also minimised.
  • the PCM compact thermal storage unit according to the invention combines the advantages of a typical spiral heating coils without the need for internal heat transfer plates.
  • the spiral thermal energy storage unit described herein which comprises a spiral heat coils enables higher thermal energy storage density, that is, it can store significantly more energy for the same weight and space as conventional storage units.
  • Phase Change Material thermal storage uses the latent heat required to turn the PCM from solid to liquid and results in a higher energy density to weight ratio.
  • a further advantage of the spiral thermal energy storage unit is low storage energy losses.
  • the compact spiral geometry of the heat exchanger concentrates the high density energy at the centre of the unit. Exterior temperatures of the unit are lower than at the centre of the spiral, resulting in lower storage losses through the exterior of the unit. Any energy losses within the interior windings of the spiral are captured by the next outer winding of the spiral.
  • the thermal performance of an exemplary tank is illustrated in figure 8 which demonstrates the ability of the PCM material to capture heat over a period of several hours. It will be appreciated that the PCM material need not reach the same temperature as the fluid being passed through the coils.
  • the design allows routine inspection and maintenance of the unit by removing the simple flat plate lid.
  • the tank walls and lid form a hermetically sealed system when bolted together.
  • the spirals are made from steel tubing turning rolled into a spiral and pass through a seal on the vertical wall of the tank.
  • the PCM fills the inter-space between the coils both horizontally and vertically.
  • the PCM is placed into the storage unit in solid form, typically as a powder, in bead form or in a fluid state.
  • any reference signs placed between parentheses shall not be construed as limiting the claim.
  • the word 'comprising' does not exclude the presence of other elements or steps than those listed in a claim.
  • the terms "a” or "an,” as used herein, are defined as one or more than one.

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

Abstract

La présente invention concerne des systèmes de stockage d'énergie et en particulier des systèmes de stockage d'énergie utilisant un matériau à changement de phase afin d'aider à la gestion de l'énergie par stockage d'énergie thermique lorsque celle-ci est disponible en quantité puis par utilisation de celle-ci lorsque nécessaire. Le système comporte des sections de tuyauterie disposées en une couche, chaque couche ayant une première voie de passage et une seconde voie de passage définies par des sections respectives de tuyau, les première et seconde voies de passage étant disposées en spirales.
PCT/EP2016/053891 2015-02-24 2016-02-24 Système de stockage d'énergie thermique en spirale Ceased WO2016135209A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1503088.5 2015-02-24
GB201503088A GB201503088D0 (en) 2015-02-24 2015-02-24 A spiral thermal energy storage system

Publications (1)

Publication Number Publication Date
WO2016135209A1 true WO2016135209A1 (fr) 2016-09-01

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CN109413785A (zh) * 2018-10-11 2019-03-01 水利部交通运输部国家能源局南京水利科学研究院 水下熔化相变材料的电磁式加热装置及制作方法
FR3077125A1 (fr) * 2018-01-25 2019-07-26 Realisation Chauffage Sanitaire Dispositif de recuperation de chaleur
CN118009783A (zh) * 2024-04-08 2024-05-10 杭州皓华压力容器有限公司 一种可自适应调节的蒸汽储能罐
FR3151388A1 (fr) * 2023-07-20 2025-01-24 Mobius Échangeur thermique
EP4459036A4 (fr) * 2022-03-29 2025-05-07 LG Electronics Inc. Unité de distillation
EP4656997A1 (fr) * 2024-05-27 2025-12-03 Max Boegl Wind AG Échangeur de chaleur à eau et accumulateur d'énergie

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US5423378A (en) * 1994-03-07 1995-06-13 Dunham-Bush Heat exchanger element and heat exchanger using same
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GB2484539A (en) * 2010-10-15 2012-04-18 Green Structures Ltd Thermal energy store for use with a heating or cooling system

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US5423378A (en) * 1994-03-07 1995-06-13 Dunham-Bush Heat exchanger element and heat exchanger using same
DE202006012871U1 (de) * 2006-08-22 2007-12-27 Consolar Solare Energiesysteme Gmbh Wasser-/Eisspeicher
GB2484539A (en) * 2010-10-15 2012-04-18 Green Structures Ltd Thermal energy store for use with a heating or cooling system

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3077125A1 (fr) * 2018-01-25 2019-07-26 Realisation Chauffage Sanitaire Dispositif de recuperation de chaleur
EP3517871A1 (fr) * 2018-01-25 2019-07-31 Realisation Chauffage Sanitaire Dispositif de récupération de chaleur
CN109413785A (zh) * 2018-10-11 2019-03-01 水利部交通运输部国家能源局南京水利科学研究院 水下熔化相变材料的电磁式加热装置及制作方法
CN109413785B (zh) * 2018-10-11 2019-12-17 水利部交通运输部国家能源局南京水利科学研究院 水下熔化相变材料的电磁式加热装置及制作方法
EP4459036A4 (fr) * 2022-03-29 2025-05-07 LG Electronics Inc. Unité de distillation
FR3151388A1 (fr) * 2023-07-20 2025-01-24 Mobius Échangeur thermique
CN118009783A (zh) * 2024-04-08 2024-05-10 杭州皓华压力容器有限公司 一种可自适应调节的蒸汽储能罐
CN118009783B (zh) * 2024-04-08 2024-06-04 杭州皓华压力容器有限公司 一种可自适应调节的蒸汽储能罐
EP4656997A1 (fr) * 2024-05-27 2025-12-03 Max Boegl Wind AG Échangeur de chaleur à eau et accumulateur d'énergie

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