Fluid flow in thermal storage container

Abstract

A thermal storage container for heat exchange in a thermal system, the thermal storage container exchanging heat via a fluid flowing through a phase change material disposed inside the thermal storage container, the thermal storage container comprising: a thermal storage container shell; a fluid inlet and a fluid outlet; and one or more membrane cells containing the phase change material and defining a plurality of channels configured to guide the flow of the fluid in different portions within the shell; wherein an actual fluid flow length from the fluid inlet to the fluid outlet is greater than the straight-line length of the fluid flowing through the entire section between the fluid inlet and the fluid outlet. The invention also describes related apparatus and methods.

Description

[0001] Related applications

[0002] This application claims priority to U.S. Provisional Patent Application No. 62 / 824,914, filed March 27, 2019; U.S. Provisional Patent Application No. 62 / 824,575, filed March 27, 2019; and U.S. Provisional Patent Application No. 62 / 824,541, filed March 27, 2019, which claims priority to International Patent Application PCT / IB2018 / 001091, filed September 25, 2018, which claims priority to U.S. Provisional Patent Application No. 62 / 685,147, filed June 14, 2018 (titled "Configurable Thermal Storage Array") and U.S. Provisional Patent Application No. 62 / 562,562, filed September 25, 2017 (titled "Configurable Thermal Storage Array").

[0003] The contents of all the above applications are incorporated herein by reference, as if they were fully described herein.

[0004] Technical Field and Background Technology

[0005] In some embodiments of the present invention, the present invention relates to various thermal containers, particularly but not limited to thermal containers that exchange heat through a phase change material in a thermal energy storage container of a thermal energy storage system via fluid flow.

[0006] Numerous studies on energy consumption in developed countries indicate that peak energy (electricity) consumption occurs for less than 300 to 400 hours per year (accounting for 5% of the total time). A significant portion of these peak energy demand can be attributed to structural cooling systems, such as chillers, air conditioners, or space heating systems relying on heat pumps. Therefore, the demand for efficient, low-cost cooling systems to offset grid fluctuations is growing.

[0007] One way to address this demand is to develop thermal energy storage systems, particularly ice storage systems. These systems store cold or hot energy by operating grid-connected coolers or heat pumps during off-peak hours and then releasing the stored energy during peak or other times. Current systems suffer from drawbacks such as incompatibility with commercial buildings, lack of modularity, and large footprints. Providing sufficient thermal energy storage often requires expensive real estate assets; therefore, commercial sectors (office buildings, shopping malls, hotels, hospitals, etc.) almost entirely lack this energy storage method, which is a significant contributing factor to peak demand phenomena.

[0008] The most common type of conventional thermal energy storage system is called an "ice-on-coil" storage system. These systems consist of a storage tank filled with water / ice (as a phase change medium (PCM)) for storing thermal energy, specifically utilizing the phase change from liquid water to ice. These systems also include a coil placed inside the storage tank, which exchanges heat with the water / ice. When storing heat in this type of system, ice forms around the coil, creating a large block. These systems suffer significant efficiency losses because freezing of the water often begins at or on the coil, and frozen water is a fairly good thermal insulator. Therefore, as the storage tank is cooled below 0°C by the coil, the thickness of the ice layer on the coil increases to store shallow thermal energy. This increased insulation makes it increasingly difficult to freeze the entire volume of the storage tank. This is known as the "ice buildup" problem. Consequently, conventional systems must use very low temperatures to cool the coil, which is inefficient. Furthermore, operating at excessively low temperatures impairs the cooler's coefficient of performance (COP).

[0009] In addition, a different type of conventional thermal energy storage system is called an "encapsulated ice" storage system, in which multiple water-filled containers are placed in a storage tank as phase change material (PCM) to store energy. Another medium, such as a water-glycol mixture, is used for heat exchange with the water / ice in the containers and is pumped through the storage tank as needed. However, this type of thermal energy storage system has so far lacked efficiency and reliability.

[0010] One inefficiency in existing systems (especially "encapsulated ice" and "ice coil" systems using water / ice) is slow or inconsistent ice nucleation, which leads to inefficient thermal energy storage and cooling. Inconsistent ice nucleation and formation are often caused by the failure of supercooled water to freeze at the required temperature.

[0011] Another limitation of some existing systems is the limited ratio between the storage fluid (water) volume and the total system volume, and / or the limited contact between the storage fluid (water) and the heat transfer fluid (e.g., ethylene glycol). This is due to the increasing water barrier between the two fluids within the capsule as the discharge cycle progresses, or the low fill factor of the storage fluid container, or poor design of the storage fluid container that results in insufficient surface area exposed to the heat transfer fluid or obstructs its flow, thus significantly reducing the efficiency of thermal storage. Another limitation of some systems is the inefficient cooling process, which prevents the melting of all the ice stored in the system. Furthermore, conventional systems provide insufficient, and particularly declining, cooling rates, which are inadequate to support load demands. In other words, conventional ice storage systems typically suffer from unstable and deteriorating cooling behavior / curves.

[0012] Another problem with some thermal energy storage systems that use water / ice as the energy storage medium is that they suffer from performance degradation over their lifespan, for example, due to material fatigue or changes in system flow characteristics. This is particularly true in current encapsulated ice systems, where the repeated expansion and contraction of water during freezing causes this problem. Another issue with conventional thermal energy storage systems is the power reduction when using water as the PCM in the latter half of the cooling cycle. This phenomenon is caused by meltwater within the membrane chamber, which acts as a barrier to heat exchange / conduction, and this barrier expands as the ice melts.

[0013] The foregoing and the references disclosed in this specification, as well as all references cited in those references, are incorporated herein by reference. Summary of the Invention

[0014] According to some embodiments of the present invention, the present invention provides a heat storage container for heat exchange in a thermal system, the heat storage container performing heat exchange via a fluid flowing through a phase change material disposed inside the heat storage container, the heat storage container comprising: a heat storage container shell; a fluid inlet and a fluid outlet; and one or more membranes containing the phase change material and defining a plurality of channels configured to guide the flow of the fluid in different portions within the shell.

[0015] Selectively, one or more upstream membrane cells are laterally positioned within the housing relative to one or more downstream membrane cells located downstream of the housing.

[0016] Optionally, a longitudinal axis is defined through the thermal storage container, and one or more membrane cells have a direction relative to one or more downstream membrane cells, the direction being at an angle of at least 30° around the longitudinal axis.

[0017] Selectively, one or more membrane cells are horizontal, while one or more membrane cells closer to the downstream end are vertical.

[0018] Selectively, the actual fluid flow length through the membrane from the fluid inlet to the fluid outlet is greater than a length measured between the fluid inlet and the fluid outlet along the general flow direction.

[0019] According to some embodiments of the present invention, the present invention provides a method for heat exchange via a fluid flowing through a thermal storage container, the method comprising:

[0020] The fluid is injected into the heat storage container through a fluid inlet;

[0021] Heat exchange occurs between the fluid and a cryogenic phase change material located inside a section of the heat storage container;

[0022] The flow direction of the fluid is modified by at least 30° to a longitudinal direction of the heat storage container;

[0023] The fluid is repeatedly exchanged and modified at least once in other parts of the thermal storage container; and the fluid is discharged from the thermal storage container via a fluid outlet.

[0024] Selectively, the actual fluid flow length through the section from the fluid inlet to the fluid outlet is greater than the straight-line length of the fluid flow through the entire section, measured between the fluid inlet and the fluid outlet.

[0025] Selectively, it can be exchanged with one or more membrane cells disposed in the section.

[0026] Optionally, the orientation can be modified by changing the orientation of one or more membrane cells disposed in the section.

[0027] According to some embodiments of the present invention, the present invention provides a thermal energy storage array comprising a plurality of ice blocks, wherein each ice block comprises a plurality of membrane cells; wherein the ice blocks are interconnected for fluid communication of a first fluid flowing through the ice blocks; and wherein the plurality of ice blocks are configured in a modular arrangement, the modular arrangement comprising one or more: ice blocks stacked together; ice blocks end-to-end with each other; or ice blocks adjacent to each other.

[0028] Optionally, the array also includes insulating plates on the outer surfaces of the modular arrangement of the ice blocks. On one hand, these insulating plates are provided to surround the outer surfaces of the modules. On the other hand, insulating plates should be avoided on non-external surfaces. Depending on the planned modular ice block arrangement, the insulating plates are designed to be attached to one or more ice blocks. This results in a homogeneous ice block structure that is easy to install and remove. This configuration saves on the need for total insulation, as only the outer surface of the entire array needs insulation, rather than every surface of every single block.

[0029] Optionally, the membrane capsule includes a second fluid, which includes water. Optionally, the array further includes a fluid distribution system. Optionally, the first fluid has a freezing point lower than that of the second fluid. Optionally, the second fluid includes an ice nucleation agent. Optionally, the ice nucleation agent is quartz. Optionally, the ice block includes between 65% and 85% of the second fluid, which is contained within the membrane capsule. Optionally, the array further includes a TES cooler for cooling the first fluid.

[0030] Optionally, the condenser portion of the TES cooler is cooled by a third fluid that also cools the load in the structure used by the array. Optionally, the array includes an air compressor. Optionally, the membrane cartridge includes a filling nozzle located at the upper corner of the cartridge to allow the cartridge to be filled to its maximum capacity using the second fluid. Optionally, the cartridge includes one or more narrow-side spacers and wide-side spacers, wherein the spacers, when packaged together within the ice block, form gaps between the cartridges. Optionally, the cartridge surface includes a plurality of protrusions adapted to increase turbulence of the first fluid surrounding the cartridge. Optionally, the ice block is rectangular. Optionally, the ice block has dimensions of 50 × 50 × 400 cm. Optionally, the ice block has dimensions of 25 × 25 × 400 cm. Optionally, the ice block has a capacity of 750 to 1200 liters. Optionally, the ice block has an energy storage capacity of 15 to 23 TRH. Optionally, the cartridge comprises a cyclohexane shape. Selectively, the cyclohexane-shaped membrane box is placed inside the ice block to allow it to settle freely within the ice block.

[0031] Optionally, the ice block is adapted to be positioned underground. Optionally, the ice block is cylindrical and includes a conduit comprising a spiral metal reinforcement extending along the exterior of the ice block to enable placement underground. Optionally, the membrane cassettes are arranged in fixed positions within the ice block. Optionally, the ice block also includes a plurality of spacers inserted between the membrane cassettes, wherein the spacers ensure the first fluid flows through the ice block and maximize turbulence as the gaps between the membrane cassettes increase due to the melting of the second fluid.

[0032] According to some embodiments of the present invention, the present invention provides a method for discharging a thermal energy storage (TES) system for cooling a load, the method comprising: providing a TES system, wherein the TES system includes a row of ice blocks, a controller, and a fluid distribution system, wherein the row of ice blocks is divided by the fluid distribution system into a plurality of subsets of ice blocks; wherein the controller is a computing device; activating the controller of a first subset of the plurality of subsets such that a first fluid flows through the first subset to cool the load; monitoring the temperature of the first fluid via the controller; when the temperature of the first fluid exceeds a threshold, activating another subset of the plurality of subsets by the controller such that the first fluid flows through the other subset to cool the load, wherein the other subset is a subset not activated during active cooling; and repeating the foregoing two steps.

[0033] Optionally, in addition to the first subset, the method also activates another subset such that the first fluid flows through all activated subsets. Optionally, the method further includes: the controller determining whether all of the plurality of subsets are activated, and the controller terminating the cooling when all of the plurality of subsets are activated. Optionally, the fluid distribution system includes: at least one pump and at least one flow control mechanism, wherein activating a subset includes: activating the at least one pump and the at least one flow control mechanism such that the first fluid flows through the subset. Optionally, each ice block includes a container including a plurality of membrane cartridges and including inlet and outlet pipes for achieving fluid communication of the first fluid within the array. Optionally, the plurality of membrane cartridges include a second fluid, the second fluid being at a lower temperature than the first fluid before cooling, and wherein the plurality of membrane cartridges cool the first fluid as the first fluid flows through the ice block.

[0034] According to some embodiments of the present invention, the present invention provides a thermal energy storage unit, the thermal energy storage unit comprising: a tube having at least one inlet for a first fluid and at least one outlet; a plurality of membrane cells containing a second fluid, wherein the plurality of membrane cells are disposed within the tube; wherein the first fluid is a heat transfer fluid for exchanging heat with the second fluid; the second fluid is a phase change medium; wherein the average length of the actual flow path of the first fluid from the inlet to the outlet is greater than the length of the tube.

[0035] According to some embodiments of the present invention, a thermal energy storage unit is provided, the thermal energy storage unit comprising: a tube having at least one inlet for a first fluid and at least one outlet; a plurality of plate-shaped membrane cells containing a second fluid, wherein the plurality of membrane cells are stacked within the tube or wherein the plurality of membrane cells are arranged inside the tube to form a stack of a plurality of membrane cells; wherein the first fluid is a heat transfer fluid for exchanging heat with the second fluid; the second fluid is a phase change medium; wherein a plurality of defined narrow or shallow flow paths for the first fluid are provided between the membrane cells.

[0036] Optionally, the thermal energy storage unit has a plurality of membrane cells, the plurality of membrane cells being adapted to provide the flow path in a tortuous pattern in at least a portion of the flow path.

[0037] Optionally, the thermal energy storage unit is configured such that the pipe is rectangular; and the ratio of the length to the width of the pipe is in the range of about 4 to 50; and / or the ratio of the width to the height of the pipe is in the range of about 0.5 to 2.

[0038] Optionally, the thermal energy storage unit is configured such that the shape of the pipe is rectangular, and the ratio of the length to the width of the pipe is in the range of about 12 to 20, optionally about 16; and / or the ratio of the width to the height of the pipe is about 1.

[0039] Optionally, the thermal energy storage unit is configured such that the total volume of the second fluid in the plurality of membrane cells is 50% to 90% of the total volume of the pipe, and optionally 65% ​​to 85%. This has been proven to be the optimal or near-optimal ratio of the volume of the second fluid to the total volume of the pipe. On the one hand, the first fluid must have sufficient space to exchange heat with the fluid; on the other hand, it should have as much available capacity as possible to store heat.

[0040] Selectively, the thermal energy storage unit is configured to provide thermal energy storage such that: (a) the inlet and outlet are located at the same end of the tube; and (b) on each membrane capsule, the flow of the first fluid from the inlet to the outlet is substantially bidirectional. For example, a rubber sealing element located approximately in the middle of the membrane capsule can serve as a diverter for the first fluid inside the tube. Thus, two substantially bidirectional flows of the first fluid can pass through membrane capsules with different temperatures. Consequently, the membrane capsules are affected by the two different flows of the first fluid and are heated or cooled at two different temperatures, thereby providing a temperature gradient inside the membrane capsules. This temperature gradient leads to favorable circulation of the second fluid (water) inside the membrane capsules, thereby providing a heat conduction effect inside the membrane capsules and having an additional effect on the formation of an insulating barrier for melted water inside the membrane capsules.

[0041] Selectively, the thermal energy storage unit is configured such that the wide side of its box-shaped or plate-shaped membrane capsule is concave. This capsule has multiple concave walls that provide specific elasticity at the center. Therefore, the walls of the capsule can bend to allow the volume of the second fluid to increase during its phase change without damage. Furthermore, the concave shape of the wide side provides a narrow and defined flow path between the side-by-side stacked capsules. Due to the concave shape of the wide side of the capsule walls, a flow channel for the first fluid is formed between the narrow (or shallow) stacked adjacent capsules. Therefore, compared to a cylindrical channel, the surface-to-volume ratio of the channel is improved, and the surface area of ​​the first fluid in contact with the wide side of the capsule is increased. Thus, by providing a correspondingly (narrow) shaped flow channel (and flow path) for the first fluid and the capsule, heat exchange through the contact surface between the capsule and the first fluid is improved, which is another space-saving solution. In other words, by providing a flat membrane with a corresponding flat flow channel between the membrane and the first fluid, the heat exchange rate between the membrane and the first fluid can be significantly improved.

[0042] Optionally, the thermal energy storage unit is configured such that at least one surface of the membrane capsule includes a plurality of protrusions adapted to generate or increase turbulence of the first fluid through the conduit. This may increase the efficiency of the system.

[0043] Optionally, the thermal energy storage unit is configured such that each of the plurality of membrane cartridges is of the same type, or that each of the plurality of membrane cartridges has the same volume for the second fluid. This may reduce manufacturing costs and facilitate the production of stacked membrane cartridges with defined flow paths.

[0044] Optionally, the thermal energy storage unit also includes rigid spacers placed between multiple membrane cells. Therefore, the rigid (e.g., grid-type) spacers, made of metal or plastic, are placed between the flat walls of the membrane cells, wherein the grid can have various shapes: rectangular, diamond, or square-hole welded or chain-locked grids. The size of the spacers can be selected to have sufficient free space for the expansion of the membrane cell walls; the free space should be greater than 15% of the membrane cell volume but less than 30% of the assumed free flow area between membrane cells without spacers. The metal grid can be made of stainless steel rods with a diameter of approximately 2.8 mm, welded into a square grid with dimensions of 310 × 140 mm, having 8 longitudinal rods and 6 transverse rods.

[0045] Optionally, the thermal energy storage unit also includes resilient spacers placed between the plurality of membrane cells, wherein the resilient spacers include fins. These resilient fins may provide resilient flow control to autonomously adjust according to the cooling state of the membrane cells.

[0046] Optionally, the thermal energy storage unit is configured such that the membrane box is typically box-shaped or plate-shaped; and the size of the spacer is such that the free flow area between the wide sides of the two membrane boxes is in the range of 15% to 30% of the free flow area between membrane boxes without spacers.

[0047] Optionally, the thermal energy storage unit is configured such that at least one membrane cell includes a nucleating agent, such as quartz. Therefore, the cooling temperature of the membrane cell can be higher than that of conventional ice storage systems.

[0048] Optionally, the thermal energy storage unit is configured such that the membrane capsule includes multiple heat transfer strips, which are selectively arranged to transfer heat to the interior of the membrane capsule. A problem with some conventional aqueous membrane capsules is the low heat transfer coefficient of water. Therefore, heat transfer from the interior to the exterior of the capsule is blocked by water / ice near the walls. Using heat transfer strips can potentially solve this problem because they also provide effective heat transfer to the interior of the capsule.

[0049] Optionally, the thermal energy storage unit is configured such that the heat transfer strip is made of aluminum. This material provides good thermal conductivity. Alternatively, the heat transfer strip can be made of other materials with good thermal conductivity, such as stainless steel. Optionally, the thermal energy storage unit is configured such that the heat transfer strip is made of a material having a thermal conductivity k greater than 10 W / (m*k) under standard conditions. Optionally, under standard conditions, the thermal conductivity k of the strip is greater than 75 W / (m*k). This may further improve the ice-making process inside the membrane chamber.

[0050] Optionally, the thermal energy storage unit is configured such that the heat transfer strips have a thickness of 0.4 to 4 mm, a length of 35 to 350 mm, and a width of 5 to 10 mm. These dimensions can provide a good heat transfer rate inside the membrane chamber. Furthermore, these strips can be easily placed inside the membrane chamber through small openings.

[0051] Optionally, the thermal energy storage unit is configured such that the membrane capsule is typically box-shaped or plate-shaped; and the membrane capsule includes a single inlet located at a corner of the capsule. This shape has a high surface area to volume ratio. This may improve the heat exchange rate between the first fluid and the second fluid.

[0052] Optionally, the thermal energy storage unit is configured such that the membrane capsule is typically box-shaped or plate-shaped; and the membrane capsule includes a plurality of ridges, such that the plurality of membrane capsules are spaced apart from each other. The plurality of ridges allows for the creation of free space for a defined flow path of the first fluid between the membrane capsules.

[0053] Because the membrane capsules have wide, flat or uneven sides, a narrow (or shallow) space is formed between two stacked membrane capsules. This establishes a modified and defined flow path for the first fluid, thereby achieving a high heat exchange rate.

[0054] Optionally, the thermal energy storage unit is configured such that the pipe has a prismatic shape, the length of which is four times its maximum diameter.

[0055] Optionally, the thermal energy storage unit is configured such that the membrane capsule has a base and a plurality of protrusions protruding from the base; the base is typically spherical and has a first radius; the plurality of protrusions are typically semi-circular and have a second radius; the second radius is at least 50% smaller than the first radius. This preferred embodiment relates to a cyclohexane-shaped membrane capsule, which will be discussed below.

[0056] Optionally, the thermal energy storage unit is configured such that the plurality of protrusions are evenly distributed on the surface of the base.

[0057] Optionally, the thermal energy storage unit is configured such that the membrane capsule has 12 protrusions and is therefore shaped like cyclohexane.

[0058] According to some embodiments of the present invention, the present invention provides a thermal energy storage system, the system comprising the plurality of thermal energy storage units described above, wherein the thermal energy storage units are part of the structural arrangement of a building; wherein the structural arrangement is a wall, floor or roof, or a combination of a wall, floor or roof.

[0059] According to some embodiments of the present invention, the present invention provides a thermal energy storage system comprising the plurality of thermal energy storage units described above, wherein the system is characterized in that the ratio of the combined length of the plurality of tubes to the flow-cut area is in the range of about 40 to 400 (cm / cm²), selectively about 60 and 150 (cm / cm²), wherein the flow-cut area is defined as the cross-sectional free-flow area of ​​the first fluid in each membrane capsule.

[0060] Optionally, the thermal energy storage system is configured such that the number of tubes is 3 to 5, optionally 4.

[0061] Optionally, the thermal energy storage system is configured such that the combined length of the plurality of tubes is 10 to 30 meters, optionally 16 meters. This indeed creates an optimal or near-optimal heat exchange rate for the system.

[0062] According to some embodiments of the present invention, the present invention provides a membrane cartridge for a thermal energy storage system or thermal energy storage unit as described above, wherein the membrane cartridge contains an ice nucleating agent, the ice nucleating agent selectively comprising quartz.

[0063] According to some embodiments of the present invention, the present invention provides a membrane box for a thermal energy storage system or thermal energy storage unit as described above, wherein the membrane box contains at least one thermally conductive element, optionally a metal strip.

[0064] According to one aspect of some embodiments of the present invention, a heat storage container for heat exchange in a thermal system is provided, the heat storage container performing heat exchange via a fluid flowing through a phase change material disposed inside the heat storage container, the heat storage container comprising: a heat storage container shell; a fluid inlet and a fluid outlet; and one or more membranes containing the phase change material and defining a plurality of channels configured to guide the flow of the fluid in different portions within the shell; wherein an actual fluid flow length from the fluid inlet to the fluid outlet is greater than the straight-line length of the fluid flowing through the entire segment measured between the fluid inlet and the fluid outlet.

[0065] According to some embodiments of the present invention, the actual fluid flow length from the fluid inlet to the fluid outlet is more than twice the straight-line length of the fluid flow through the entire section measured between the fluid inlet and the fluid outlet.

[0066] According to some embodiments of the present invention, the ratio between the average cross-sectional area of ​​the heat storage container along the flow path of the container and the total heat exchange area of ​​all the membrane cells in the container is between 4.5 × 10⁻⁶. -5 Up to 45×10 -5 between.

[0067] According to some embodiments of the present invention, the ratio between the average cross-sectional area of ​​the heat storage container along the flow path of the container and the total heat exchange area of ​​all the membrane cells in the container is between 1 × 10⁻⁶. -5 Up to 100×10 -5 between.

[0068] According to some embodiments of the present invention, the gamma ratio of the heat storage container is greater than 150 cm / cm², wherein the gamma ratio is defined as a ratio between a linear length of the heat transfer fluid flow path and a free-flow cross-sectional area of ​​each membrane, wherein the linear length is in centimeters and the free-flow cross-sectional area is in square centimeters.

[0069] According to some embodiments of the invention, the plurality of channels are configured to allow the fluid to meander within the housing.

[0070] According to some embodiments of the present invention, one or more upstream membrane cells are laterally positioned within the housing relative to one or more downstream membrane cells positioned downstream of the housing.

[0071] According to some embodiments of the invention, a longitudinal axis is defined through the thermal storage container, and one or more membrane cells have a direction relative to one or more downstream membrane cells, the direction being at an angle of at least 30° around the longitudinal axis.

[0072] According to some embodiments of the present invention, one or more membrane cells are horizontal, and one or more membrane cells near the downstream end are vertical.

[0073] According to some embodiments of the present invention, the actual fluid flow length through the membrane from the fluid inlet to the fluid outlet is greater than a length measured along the general flow direction between the fluid inlet and the fluid outlet.

[0074] According to some embodiments of the present invention, the membrane box disposed within the heat storage container has an assembly of concave and convex contours, the assembly defining a plurality of gaps between the outer shapes of the membrane box.

[0075] According to some embodiments of the present invention, the membrane box contains a plurality of metal strips, wherein the length of the plurality of metal strips is greater than the width of the membrane box.

[0076] According to some embodiments of the present invention, the thermal storage container includes one or more turbulence generators.

[0077] According to one aspect of some embodiments of the present invention, the present invention provides a method for heat exchange via a fluid flowing through a thermal storage container, the method comprising:

[0078] The fluid is injected into the thermal storage container through a fluid inlet; heat exchange occurs between the fluid and a cryogenic phase change material located inside a section of the thermal storage container; the flow direction of the fluid is modified by at least 30° to a longitudinal direction of the thermal storage container; the exchange and modification are repeated at least once in other parts of the thermal storage container; and the fluid is discharged from the thermal storage container via a fluid outlet.

[0079] According to some embodiments of the invention, the modification is made by causing the fluid inside the heat storage container to flow in a meandering manner.

[0080] According to some embodiments of the present invention, the actual fluid flow length from the fluid inlet to the fluid outlet through the section is greater than the straight-line length of the fluid flow through the entire section measured between the fluid inlet and the fluid outlet.

[0081] According to some embodiments of the present invention, it is exchanged with one or more membrane cells disposed in the section.

[0082] According to some embodiments of the present invention, the modification is made by changing the orientation of one or more membrane cells disposed in the section.

[0083] According to some embodiments of the present invention, the method further includes generating turbulence on a heat exchange surface of a membrane capsule.

[0084] According to some embodiments of the present invention, the method further includes generating a tortuous flow on a heat exchange surface of a membrane capsule.

[0085] According to some embodiments of the present invention, the modification is achieved by alternating between turbulent and meandering flow in the thermal storage container.

[0086] According to some embodiments of the invention, in at least 35% of the fluid flow path within the heat storage container, the temperature is between 100 and 300 W / (m³). 2 The fluid flow generated within the range of *K) is highly turbulent.

[0087] According to some embodiments of the present invention, in at least 35% of the fluid flow path within the thermal storage container, the fluid flow generates a flow rate greater than 100 W / (m²). 2 The thermal conductivity coefficient of K.

[0088] According to one aspect of some embodiments of the present invention, a thermal energy storage system is provided, the thermal energy storage system comprising: a plurality of thermal storage containers used in a thermal system, the thermal storage containers exchanging heat via a heat transfer fluid flowing through a phase change material disposed inside the thermal storage containers; a heat transfer fluid inlet; a conduit connecting at least some of the thermal storage containers in series; a flow control mechanism; and a heat transfer fluid outlet; wherein the flow control mechanism is configured to allow the heat transfer fluid to bypass a thermal storage container and reach the heat transfer fluid outlet without passing through the thermal storage container.

[0089] According to some embodiments of the present invention, the flow control mechanism is an electrically operated valve, and the thermal energy storage system further includes a controller for controlling the electrically operated valve.

[0090] According to some embodiments of the present invention, the controller is configured to receive control commands via a communication line.

[0091] According to some embodiments of the present invention, the flow control mechanism is a pressure reducing valve.

[0092] According to one aspect of some embodiments of the present invention, the present invention provides a method for heat exchange via a heat transfer fluid flowing through a thermal storage container, the method comprising: providing a thermal energy storage system, including: a plurality of thermal storage containers used in a thermal system, the thermal storage containers exchanging heat via a heat transfer fluid flowing through a phase change material disposed inside the thermal storage containers; a heat transfer fluid inlet; a conduit connecting at least some of the thermal storage containers in series; a flow control mechanism; and a heat transfer fluid outlet; wherein the flow control mechanism is configured to allow the heat transfer fluid to bypass a thermal storage container and reach the heat transfer fluid outlet without passing through the thermal storage container; and providing a control signal to the flow control mechanism to open a flow path for the heat transfer fluid, such that the heat transfer fluid bypasses more downstream thermal storage containers.

[0093] The technical effects of the above embodiments will be described in more detail below. One of the key performance indicators of a thermal energy storage system is the average cooling rate relative to the storage capacity, which can maintain the required temperature range throughout the entire cooling period. A typical system holding a certain capacity should be able to release as much of its stored capacity as possible within, for example, 4 hours, while maintaining the final outlet temperature of the first liquid below or equal to 5°C.

[0094] Based on the above requirements, the effective heat transfer rate of a given membrane capsule should be as high as possible. Specifically, the heat transfer rate of the membrane capsule is determined by the following factors:

[0095] 1. Heat transfer zone, including:

[0096] i. The effective heat transfer area of ​​the ice material (e.g., large blocks of ice) within the membrane chamber 715 (heat transfer begins from the entire inner surface area of ​​the membrane chamber shell and decreases as the ice material begins to melt, and vice versa).

[0097] ii. The internal area of ​​the membrane capsule shell (i.e., the ice / water heat transfer area of ​​the membrane capsule material).

[0098] iii. The outer region of the membrane casing (i.e., the outer heat transfer region to the first fluid)

[0099] 2. Heat transfer coefficient (HTC), including:

[0100] i. Secondary fluid, i.e. ice turning into water (melting) or water turning into ice (freezing).

[0101] ii. Further effects of water inside the membrane capsule (i.e., heat conduction from inside the membrane capsule through the water itself)

[0102] iii. The second fluid of the membrane capsule material (so-called thin-film HTC; i.e., boundary effects, e.g., depending on the circulation of the second fluid within the membrane capsule)

[0103] iv. The membrane material itself, such as polymers (i.e., the thermal conductivity of the membrane material itself).

[0104] v. Membrane material to the first fluid (i.e., boundary effects, e.g., depending on the velocity and turbulence of the first fluid flowing outside the membrane).

[0105] 3. Temperature difference, including:

[0106] i. Total temperature difference between the inside of the membrane capsule and the first fluid

[0107] ii. Individual temperature difference between 2i and 2v in each stage.

[0108] Several variables can be considered approximately constant: 1ii, 1iii, 2i, 2ii, 2iii, 2iv, and 3i. The remaining variables change during the cooling process. Details are as follows:

[0109] 1i: During the cooling process, the surface area of ​​the ice material (block) decreases significantly. The rate of decrease is not necessarily linearly related to the percentage of ice that melts.

[0110] 2v: The heat transfer coefficient from the membrane material to the second fluid 120 is highly dependent on the flow characteristics of the second fluid 120. As the ice melts, the space of the flow path continuously increases (the membrane shrinks to its "water-filled size"), causing the HTF velocity to decrease, and the plasticity HTC of the HTF surface to decrease accordingly (not necessarily linearly proportional to the percentage of melted ice, but depending on the flow Reynolds number).

[0111] The above embodiments consider several of items 1 to 3 above. For example, plate-shaped or box-shaped membrane capsules provide a membrane capsule surface area that is increased relative to its volume. The HTC through the membrane capsule shell is improved by reducing the thickness of the membrane capsule material using a rigid polymer. Providing metal transfer strips within the membrane capsule improves the HTC of ice to water and the HTC of water. Internal circulation of the second fluid within the membrane capsule is caused by exposing each membrane capsule to bidirectional flow of the first fluid at different temperatures, resulting in a favorable exchange of the second fluid volume within the membrane capsule. This favorable exchange improves the internal HTC of the membrane capsule because circulation promotes heat conduction. More efficient heat transfer between the membrane capsule shell and the first fluid is achieved by adding protrusions to the membrane capsule surface to provide a turbulent flow profile for the flow path of the first fluid, as heat conduction is also promoted by the transport of the first fluid itself. Conversely, a purely laminar flow profile negatively impacts the heat transfer rate because the velocity of the first fluid at the membrane capsule boundary tends to zero (due to boundary phenomena), and therefore, in the case of purely laminar flow, the movement of the first fluid itself provides little or no heat transfer. Using metal or other materials as spacers or meshes between membrane cells can create turbulent profiles and well-defined flow paths. Using variable / flexible spacers can maintain a tight flow path between the spacers and membrane cells, while also increasing the heat transfer rate.

[0112] In summary, some embodiments and aspects of the present invention may stabilize the cooling rate through the latter part of the cooling process and potentially position multiple units to be compatible with commercial buildings, thus enabling water to become a safe, clean, efficient, and economical energy storage device.

[0113] Unless otherwise defined, all technical and / or scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. While various methods and materials similar to or equivalent to those described herein may be used to practice or test embodiments of the invention, various exemplary methods and / or materials are also described below. In case of conflict, the patent specification (including definitions) shall prevail. Furthermore, the materials, methods, and examples herein are illustrative and not restrictive.

[0114] The term "ice block" can be understood as a thermal energy storage unit, which is particularly suitable for encapsulating a heat transfer fluid (i.e., the first fluid) and multiple membrane cells containing a PCM (i.e., the second fluid).

[0115] The term "tube" can be understood as an elongated hollow body having a length at least twice (preferably six times) its diameter. The cross-section of the tube can be circular, elliptical, square, rectangular, or polygonal. Optionally, the cross-section of the tube is rectangular and its overall length is substantially constant.

[0116] The term "membrane capsule" can be understood as a closed volume that permanently stores PCM (e.g., water or a mixture of water). Additionally, other components or ingredients can be stored within this closed volume.

[0117] The term "heat" refers to the ability to store and exchange thermal energy.

[0118] The efficiency or effectiveness of a heat exchanger is the ratio of the actual heat transfer rate to the maximum possible heat transfer rate in the heat exchanger.

[0119] The cross-sectional view shows a section of the pipe along its width.

[0120] Practicing the methods and systems of the present invention involves performing or completing certain selected tasks or steps manually, automatically, or in a combination thereof. Furthermore, the actual instruments and apparatus of preferred embodiments of the methods and systems according to the present invention can implement several selected steps via hardware or software on any operating system with any firmware or combination thereof. For example, as hardware, the selected steps of the present invention can be implemented as chips or circuits. The selected steps of the present invention can be implemented as a plurality of software instructions executed by a computer using any suitable operating system. In any case, the selected steps of the methods and systems of the present invention can be described as being executed via a data processor, for example, a computing platform executing multiple instructions.

[0121] Although the present invention is described with respect to a “controller,” “computing device,” “computer,” or “mobile device,” it should be noted that, optionally, any device having a data processor and capable of executing one or more instructions can be described as a computer, including but not limited to: any type of personal computer (PC), PLC (programmable logic controller), server, distributed server, virtual server, cloud computing platform, cellular phone, IP phone, smartphone, or PDA (personal digital assistant). Any two or more such devices communicating with each other may optionally include a “network” or a “computer network.”

[0122] As will be understood by those skilled in the art, some embodiments of the present invention can be implemented as systems, methods, or computer program products. Therefore, some embodiments of the present invention may take the form of entirely hardware embodiments, entirely software embodiments (including firmware, resident software, microcode, etc.), or embodiments combining software and hardware aspects, which are generally referred to herein as “circuit,” “module,” or “system.” Furthermore, some embodiments of the present invention may take the form of computer program products contained on one or more computer-readable media, on which computer-readable program code is contained. Implementation of methods and / or systems according to some embodiments of the present invention may involve performing and / or completing selected tasks manually, automatically, or in a combination thereof. Furthermore, practical instruments and apparatus according to some embodiments of methods and / or systems of the present invention can implement several selected tasks through hardware, software, firmware, and / or combinations thereof, for example, using an operating system.

[0123] For example, according to some embodiments of the invention, the hardware for performing a selected task can be implemented as a chip or circuit. As software, the selected task according to some embodiments of the invention can be implemented as a plurality of software instructions executed by a computer using any suitable operating system. In an exemplary embodiment of the invention, one or more tasks according to some exemplary embodiments of the methods and / or systems described herein are performed by a data processor, such as a computing platform for executing a plurality of instructions. Optionally, the data processor includes volatile and / or non-volatile memory for storing instructions and / or data, such as a magnetic hard disk and / or removable media. Optionally, the invention also provides network connectivity. The invention also optionally provides a display and / or a user input device, such as a keyboard or mouse.

[0124] Any combination of one or more readable media can be used in some embodiments of the present invention. A computer-readable medium can be a computer-readable signal medium or a computer-readable storage medium. For example, a computer-readable storage medium can be, but is not limited to, electronic, magnetic, optical, electromagnetic, infrared, or semiconductor systems, devices, or apparatuses, or any suitable combination thereof. More specific examples of computer-readable storage media (a non-exhaustive list) will include the following: electrical connections having one or more wires, portable computer disks, hard disks, random access memory (RAM), read-only memory (ROM), erasable programmable read-only memory (EPROM or flash memory), optical fiber, portable optical disc read-only memory (CD-ROM), optical storage devices, magnetic storage devices, or any suitable combination thereof. In this document, a computer-readable storage medium can be a tangible medium that may contain or store a program for use with an instruction execution system, device, or apparatus.

[0125] Computer-readable signal media may include propagating data signals, including, for example, computer-readable program code in baseband or as part of a carrier wave. Such propagating signals can take many forms, including but not limited to: electromagnetic, optical, or any suitable combination thereof. A computer-readable signal medium can be a computer-readable medium of any non-computer-readable storage medium, and said computer-readable medium can communicate, propagate, or transmit programs for use by or in connection with an instruction execution system, device, or apparatus.

[0126] Program code embodied on a computer-readable medium and / or data used therefrom may be transmitted using any suitable medium (including, but not limited to, wireless, wired, fiber optic cable, radio frequency, etc.) or any suitable combination thereof.

[0127] The computer program code for performing operations in some embodiments of the present invention can be written in any combination of one or more programming languages, including object-oriented programming languages ​​such as Java, Simaltalk, C++, etc., and conventional programming languages ​​such as the "C" programming language or similar programming languages. The program code can be executed entirely on the user's computer, partially on the user's computer as a standalone software package, partially on the user's computer, partially on a remote computer, or entirely on a remote computer or server. In the latter case, the remote computer can be connected to the user's computer via any type of network, including a local area network (LAN) or a wide area network (WAN), or it can be connected to an external computer (e.g., using a network service provider's network).

[0128] The following description of some embodiments of the invention may be made with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of the invention. It should be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks of the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, or other programmable data processing apparatus to produce a machine, such that the instructions, executable via the processor of the computer or other programmable data processing apparatus, create a method for implementing the functions / actions specified in the flowchart illustrations and / or block diagrams.

[0129] These computer program instructions may also be stored in a computer-readable medium that can instruct a computer, other programmable data processing device or other apparatus to operate in a particular manner, such that the instructions stored in the computer-readable medium produce an article of writing including instructions that implement the functions / actions specified in the flowchart and / or block diagram.

[0130] Computer program instructions may also be loaded onto a computer, other programmable data processing apparatus or other device to cause a series of operational steps to be performed on the computer, other programmable apparatus or other device, thereby producing a computer-implemented process, such that the instructions executing on the computer or other programmable device provide a process for implementing the functions / actions specified in the flowchart and / or block diagram.

[0131] Some of the methods described in this article are typically designed for computer use only, and may be infeasible or impractical for human experts to perform them manually. Human experts who wish to perform similar tasks manually (e.g., controlling thermal energy storage) might use entirely different approaches, such as leveraging expert knowledge and / or the pattern recognition capabilities of the human brain, which would be more efficient than manually executing the steps of the methods described in this article.

[0132] The term "refrigeration ton (TR)," also known as the freezing ton (RT), is a unit of power used in some countries (particularly in North America) to describe the heat absorption capacity of refrigeration and air conditioning equipment. TR refers to the rate of heat transfer that causes 1 short ton, 2000 pounds, or 907 kilograms of pure ice to freeze or melt in 24 hours at 0°C.

[0133] A refrigeration ton is approximately equivalent to 12,000 BTU / h or 3.5 kW. Attached Figure Description

[0134] This document describes some embodiments of the invention by way of example only, with reference to the accompanying drawings. Now, with detailed reference to the drawings, emphasis is placed on the details shown being illustrative and intended to discuss embodiments of the invention in an illustrative manner. In this regard, the accompanying drawings will enable those skilled in the art to clearly understand how to practice embodiments of the invention.

[0135] In the attached diagram:

[0136] Figures 1A to 1E This is a schematic diagram of a thermal energy storage system according to at least some embodiments of the present invention;

[0137] Figures 2A to 2Y These are illustrations of ice blocks, ice film boxes, and heat storage arrays according to at least some embodiments of the present invention;

[0138] Figure 3 An ice film box according to at least some embodiments of the present invention is shown;

[0139] Figure 4 A cylindrical ice block is shown according to at least some embodiments of the present invention;

[0140] Figure 5A This demonstrates a TES system capable of activating a separate subset of ice blocks via a controller;

[0141] Figure 5B A flowchart illustrating the operation of the TES system is shown.

[0142] Figure 5C Experimental data on the operation of a TES system according to at least some embodiments of the present invention are shown;

[0143] Figures 6A to 6G These are multiple spacers for ice blocks according to at least some embodiments of the present invention;

[0144] Figures 7A to 7D A cross-sectional view of the thermal energy storage unit, including tubes and membranes, is shown.

[0145] Figure 8A and Figure 8B A diaphragm containing a metal strip is shown;

[0146] Figure 9A and Figure 9B The spacers between the membrane cells are shown;

[0147] Figures 10A to 10B This is a simplified schematic diagram of the flow of heat exchange fluid inside a heat storage container according to some embodiments of the present invention;

[0148] Figure 11 This is a simplified flowchart of a method for flowing heat exchange fluid inside a heat storage container according to some embodiments of the present invention.

[0149] Figures 12A to 12E This is a simplified schematic diagram of the side view and cross-section of a heat storage container according to some embodiments of the present invention;

[0150] Figure 12FThis is a simplified schematic diagram of a perspective view of a membrane box in a thermal storage container according to some embodiments of the present invention;

[0151] Figure 13 This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention;

[0152] Figure 14 This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention;

[0153] Figure 15A and Figure 15B This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention;

[0154] Figure 16 This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention;

[0155] Figure 17 This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention;

[0156] Figure 18A and Figure 18B This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention;

[0157] Figure 19 This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention;

[0158] Figure 20 This is a simplified schematic diagram of a heat storage container according to some embodiments of the present invention;

[0159] Figure 21 This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention;

[0160] Figure 22 This is an example of a data sheet for a thermal storage container according to some embodiments of the present invention;

[0161] Figure 23A This is a simplified schematic diagram of an ice block and a bypass mechanism according to an embodiment of the present invention;

[0162] Figure 23B This is a simplified schematic diagram of an ice block and two valves according to an embodiment of the present invention;

[0163] Figure 23C This is a simplified schematic diagram of the construction of three ice blocks and a valve according to an embodiment of the present invention;

[0164] Figure 24This is a simplified flowchart of a method for heat exchange via fluid flowing through a heat storage container according to an embodiment of the present invention; and

[0165] Figure 25 It is a collection of graphs illustrating the experimental results performed using an exemplary embodiment of the present invention. Detailed Implementation

[0166] In some embodiments of the invention, the invention relates to a variety of thermal containers, more specifically but not limited to: thermal storage containers in thermal energy storage systems, where heat is exchanged via fluid flow with adjacent phase change materials.

[0167] Overview:

[0168] According to one aspect of some embodiments of the present invention, the present invention relates to a heat storage container for a thermal system, wherein heat exchange is performed by a heat exchange fluid having a long flow path adjacent to a heat exchange surface within the heat storage container.

[0169] According to some embodiments, a long path is defined as the flow length, where the time it takes for the fluid to approach the heat exchange surface at a known speed is longer than the time required for the fluid to flow through the length of the container at a known speed (if the fluid flows directly from the fluid inlet to the fluid outlet).

[0170] According to some embodiments, the heat exchange fluid flows from the inlet to the outlet along one or more paths in a channel defined along the heat exchange surface. In some embodiments, the length of the flow path is defined as the average length in which 80% of the fluid flows, ignoring turbulence with a radius less than 1 cm.

[0171] According to some embodiments, the flow length within the thermal storage container is extended by having a meandering flow path between the fluid inlet and outlet.

[0172] According to some embodiments, the flow length inside the container is extracted through numerical simulation.

[0173] According to some embodiments, the flow shape is wide and shallow. In some embodiments, the flow within narrow channels within the container is restricted to a shallower depth, and the flow cut area at these channels is small. In some embodiments, the flow path defines one or more bends, and the flow bends around its narrow side. According to some embodiments, the container defines a high ratio between the length of the fluid flow path and the flow cut area. In some embodiments, the container has a small flow cut area, a small cross-sectional area along its length, and a small ratio between the cross-sectional area and the length. In some embodiments, the ratio between the flow length and the flow cut area should be in the range of 10 to 800 cm / cm². In some embodiments, the ratio between the flow length and the flow cut area should be in the range of 20 to 600 cm / cm². In some embodiments, the ratio between the flow length and the cut area should be in the range of 40 to 400 cm / cm².

[0174] According to some embodiments, the long flow path in the thermal storage container is defined by having two or more fluid-connected chambers, each chamber being supplied with fluid flow in a different overall flow direction.

[0175] One aspect of some embodiments of the present invention relates to a thermal storage container having a membrane chamber for containing a phase change material and performing heat exchange via a heat exchange fluid having a flow path adjacent to a heat exchange surface, the heat exchange surface being the side of the membrane chamber.

[0176] According to some embodiments, the majority of the heat exchange fluid is adjacent to the phase change material. In some embodiments, at least 60% of the volume of the heat exchange fluid is within 5 mm of the phase change material. In some embodiments, at least 75% of the volume of the heat exchange fluid is within 5 mm of the phase change material. In some embodiments, at least 90% of the volume of the heat exchange fluid is within 5 mm of the phase change material.

[0177] According to some embodiments, when the phase change material in the membrane capsule includes ice, most of the heat exchange fluid near the membrane capsule is adjacent to the ice. In some embodiments, the flow path is designed such that most of the ice is close to the coolant. In some embodiments, at least 70% of the ice in the membrane capsule is within 5 mm of the heat exchange fluid. In some embodiments, at least 80% of the ice in the membrane capsule is within 5 mm of the heat exchange fluid. In some embodiments, at least 90% of the ice in the membrane capsule is within 5 mm of the heat exchange fluid. In some embodiments, most of the ice is within 5 mm of the heat exchange surface. In some embodiments, most of the ice is within 3 mm of the heat exchange surface. In some embodiments, most of the ice is within 2 mm of the heat exchange surface.

[0178] According to some embodiments, a majority of the phase change material is located adjacent to the heat exchange fluid. In some embodiments, at least 30% of the volume of the phase change material is within 5 mm of the heat exchange fluid. In some embodiments, at least 70% of the volume of the phase change material is within 5 mm of the heat exchange fluid. In some embodiments, at least 80% of the volume of the phase change material is within 5 mm of the heat exchange fluid. In some embodiments, at least 40% of the volume of the phase change material is within 5 mm of the heat exchange fluid.

[0179] According to some embodiments, the membrane capsule is flat, and the flow along the channel is turbulent, and the wider channel can be used as a narrower channel to avoid boundary effects due to fluid mixing.

[0180] According to some embodiments, the membrane capsule is configured to meander through a longer path to increase the total contact time between the fluid and the heat exchange surface.

[0181] One aspect of some embodiments of the present invention relates to a heat storage container in a thermal system, wherein heat exchange is performed by fluid flowing through the heat storage container disposed between a fluid inlet and a fluid outlet, and the time spent by the fluid on the heat exchange surface is at least 90% of the flow time between the fluid inlet and the fluid outlet.

[0182] One aspect of some embodiments of the present invention relates to a heat storage container in a thermal system, wherein heat exchange is performed via a fluid flow through the heat storage container, the heat storage container dividing the flow into multiple sub-flows and mixing the multiple sub-flows to reduce temperature stratification within the sub-flows.

[0183] One aspect of some embodiments of the present invention relates to a thermal storage container in a thermal system, the thermal storage container comprising a plurality of membrane cells, each membrane cell having two or more heat exchange surfaces that exchange heat with a fluid flowing through the thermal storage container and the two or more surfaces.

[0184] One aspect of some embodiments of the present invention relates to a thermal storage container in a thermal system, wherein heat exchange is performed via turbulent flow on a heat exchange surface, wherein the heat exchange surface is in contact with a phase change material within the thermal storage container.

[0185] According to some embodiments, the thermal storage container includes one or more portions configured to provide a desired fluid flow profile within at least one of the portions. In some embodiments, providing the fluid flow profile affects the flow profile of downstream portions.

[0186] According to some embodiments, setting a fluid flow profile includes generating a turbulent flow profile. In some embodiments, the desired fluid flow profile includes turbulence intensity. In some embodiments, setting a fluid flow profile includes increasing turbulence intensity.

[0187] According to some embodiments, the thermal storage container has multiple membrane cells, and the flow parameters are set by controlling the flow path or size by adjusting the orientation of the membrane cells. In some embodiments, the flow parameters are modified by positioning the membrane cells in different directions along the length of the container.

[0188] According to some embodiments, the orientation of the membrane cassette in the upstream portion differs from that in the downstream portion. In some embodiments, the orientation of the membrane cassette is changed by laterally oriented the membrane cassette relative to other membrane cassettes.

[0189] According to some embodiments, the thermal storage container extends longitudinally along a longitudinal axis. In some embodiments, the orientation of the membrane cassette is determined relative to the longitudinal axis. In some embodiments, the orientation of the membrane cassette is defined as an angle of rotation about the longitudinal axis. In some embodiments, the orientation of the membrane cassette in certain portions of the container is perpendicular to the orientation of the membrane cassette in other portions. In some embodiments, the orientation of the membrane cassette in one portion is perpendicular to the orientation of the membrane cassette in a downstream or upstream portion.

[0190] According to some embodiments, at least some membrane cells are oriented vertically such that their heat exchange surfaces are in a vertical position. In some embodiments, a vertical position is defined as a heat exchange surface oriented vertically and parallel to the longitudinal axis of the heat storage container. In some embodiments, the membrane cells of certain portions of the container are oriented horizontally such that their heat exchange surfaces are horizontal; in some embodiments, adjacent portions have alternating membrane cell orientations, with some portions in a vertical direction and some portions in a horizontal direction.

[0191] One aspect of some embodiments of the present invention relates to a heat storage container in a thermal system, wherein heat exchange is performed via a fluid flowing through a labyrinth within the heat storage container and adjacent phase change material.

[0192] According to some embodiments, the labyrinth is defined by a membrane containing a phase change material, thus preventing it from mixing with the coolant. In some embodiments, the labyrinth is configured to maintain fluid pathways when the membrane expands due to the freezing of the phase change material. In some embodiments, the labyrinth has multiple spacers to prevent blockage of fluid paths.

[0193] One aspect of some embodiments of the present invention relates to a series-connected thermal storage container or ice block, and to a configuration of heat transfer fluid to selectively bypass the ice block when needed.

[0194] To increase the cooling percentage of the storage capacity of a given structured membrane box (shape and material), a possible configuration is to connect ice blocks in series.

[0195] Some of the inherent advantages of series connections include:

[0196] Downstream membrane boxes, which may still be storing cold or only extracting a small portion of their capacity, may continue to cool the heat transfer fluid to the required temperature (e.g., below 5°C), and the series arrangement of ice blocks may continue to extract cooling capacity from the upstream high-extraction membrane boxes.

[0197] It has fewer connections to the main headers.

[0198] One potential drawback is that it may result in a higher pressure drop compared to connecting ice blocks in a non-series manner or in a shorter series connection.

[0199] In some embodiments, the flow control mechanism is configured as an optional bypass device, which can be selectively installed, for example, as a switching valve or pressure relief valve connected to the discharge header. In this case, to reduce pressure drop, more downstream frozen ice blocks can be bypassed.

[0200] In some embodiments, connecting ice blocks in series and activating a bypass upon receiving a command may enable the required cooling rate while reducing the pressure drop below the required limit.

[0201] Before explaining at least one embodiment of the present invention in detail, it should be understood that the application of the present invention is not necessarily limited to the details of the construction and arrangement of the components and / or methods shown in the following description and / or drawings and / or examples. The present invention can be implemented in various ways or practiced in other embodiments.

[0202] This document describes a thermal energy storage system's heat container and the exchange of heat within the heat storage container of the thermal energy storage system via fluid flow through adjacent phase change materials. Further supplementary descriptions can be found in International Patent Application PCT / IB2018 / 001091.

[0203] Examples of fluid flow:

[0204] refer to Figures 10A to 10B , Figure 10A and Figure 10B This is a simplified schematic diagram of the flow of heat exchange fluid inside a heat storage container according to some embodiments of the present invention.

[0205] According to some embodiments, the thermal storage container is configured to receive heat exchange fluid, transport fluid within the thermal storage container to a heat exchange surface, and output fluid. According to some embodiments, the heat exchange is used to reduce the temperature of the fluid between the inlet and outlet of the thermal storage container. In some embodiments, the heat exchange surface is a cold surface cooled by a phase change material.

[0206] like Figure 10A and Figure 10B As shown, the heat exchange fluid 1004 has the following flow stations within the heat storage container 1002.

[0207] Inlet 1010: In some embodiments, fluid enters the thermal storage container 1002 via a fluid inlet.

[0208] Outlet 1012: In some embodiments, fluid exits the thermal storage container 1002 via a fluid outlet.

[0209] For example, in some embodiments, such as Figure 10A As shown, inlet 1010 and outlet 1012 are located on the same side of thermal storage container 1002. In some embodiments, such as... Figure 10B As shown, inlet 1010 and outlet 1012 are located on opposite sides of thermal storage container 1002'. In some embodiments, inlet 1010 and outlet 1012 are located on different sides of thermal storage container 1002', and they are not opposite each other, for example, they are perpendicular to each other.

[0210] According to some embodiments, between inlet 1010 and outlet 1012, fluid flows through a plurality of stations 1014 having the desired fluid flow profile.

[0211] According to some embodiments, one or more stations 1014 configure the fluid path to be meander. One advantage of meandering is that it increases the flow length within the container 1002 on the heat exchange surface and extends thermal convection according to the length of the heat storage container.

[0212] According to some embodiments, one or more stations 1014 configure the fluid flow to be turbulent. In some embodiments, tortuous flow increases the intensity of turbulence.

[0213] One advantage of turbulence is that it mixes the fluid and prevents the formation of a fluid layer. Fluid mixing can increase the amount of heat exchanged between the fluid and the heat exchange surface per length of the heat storage container. In some embodiments, increased turbulence causes the fluid temperature to drop more rapidly. According to some embodiments, the Reynolds number of the fluid flow within container 1002 / 2' is controlled by a flow pattern defined by flow station 1014. In some embodiments, an increased Reynolds number in one or more stations 1014 may result in a higher heat transfer coefficient. Increasing the Reynolds number may also make the fluid temperature more uniform.

[0214] In some embodiments, the fluid flow 1004 is highly turbulent in at least 35% of the fluid flow path of the thermal storage container 1002 (e.g., at 100 to 300 W / (m³)). 2Within the range of *K). In some embodiments, the fluid flow 1004 is highly turbulent in at least 50% of the fluid flow path (between inlet 1010 and outlet 1012) of the thermal storage container 1002. In some embodiments, the fluid flow 1004 is highly turbulent in at least 70% of the fluid flow path (between inlet 1010 and outlet 1012) of the thermal storage container 1002. In some embodiments, the flow in the remainder of the flow path is low-turbulent. In some embodiments, the flow in the remainder of the flow path is laminar.

[0215] According to some embodiments, when the flow is converted to highly turbulent flow, the increase in fluid pressure drop is less than 15%.

[0216] According to some embodiments, the fluid flow is divided into multiple sub-flows, and the meandering flow of the sub-flows mixes with the sub-flows. A superficial advantage of dividing the flow into multiple sub-flows is increased contact between the flow and the heat exchange surface. A superficial advantage of mixing the sub-flows is reduced temperature gradients within the flow along the flow path.

[0217] like Figure 10A As shown, in some embodiments, one or more flow stations are turns 1016 in the direction of flow 1004, such as U-turns towards the fluid outlet. In some embodiments, flow 1004 has multiple turns 1016 between inlet 1010 and outlet 1012. In some embodiments, the range of the turns is 5 to 90°. In some embodiments, the range of the turns is 15 to 75°. In some embodiments, the range of the turns is 30 to 60°. In some embodiments, the turns are relative to a horizontal plane. In some embodiments, the turns are relative to a vertical plane.

[0218] Exemplary methods for heat exchange fluid flow:

[0219] refer to Figure 11 , Figure 11 This is a simplified flowchart of a method for flowing heat exchange fluid inside a heat storage container according to some embodiments of the present invention.

[0220] Figure 11 One example of an embodiment suitable for causing the heat exchange fluid to flow, the heat exchange fluid having, as Figures 10A to 10B One or more flow patterns are described. Fluid flow can be achieved through the following steps: Generating a flow pattern.

[0221] The heat exchange fluid is injected into the 1102 heat storage container through the fluid inlet.

[0222] According to some embodiments, the fluid is at a rate of 0.2 to 1.5 m³ per refrigerated ton (RT). 3A flow rate of / Hr is pumped into the thermal storage container (where RT is the cooling rate measured in refrigeration tons). In some embodiments, the pumping fluid rate is 0.3 to 1.0 m / s. 3 / Hr. In some embodiments, the pumping fluid rate is 0.5 to 0.7 m3 / Hr.

[0223] According to some embodiments, the thermal storage container is defined as a pressure vessel. In some embodiments, fluid is pumped into the container, which is defined as a pressure vessel, at a pressure of 1 to 4 bar (g). In some embodiments, fluid is pumped into the container, which is defined as a pressure vessel, at a pressure of 1.5 to 3.5 bar (g). In some embodiments, fluid is pumped into the container, which is defined as a pressure vessel, at a pressure of 2 to 3 bar (g). In some embodiments, the container is not defined as a pressure vessel. In some embodiments, fluid is pumped into the container, which is not defined as a pressure vessel, at a pressure of 0.1 to 2 bar (g). In some embodiments, fluid is pumped into the container, which is not defined as a pressure vessel, at a pressure of 0.3 to 1.5 bar (g). In some embodiments, fluid is pumped into the container, which is not defined as a pressure vessel, at a pressure of 0.7 to 1 bar (g).

[0224] The 1104 heat exchange fluid is guided in the heat storage container section.

[0225] According to some embodiments, guide 1104 is used for heat exchange with the phase change material within the section. In some embodiments, guide 1104 includes changing the flow direction toward one or more flow paths within the section.

[0226] According to some embodiments, the container has a uniform membrane box that is installed in a continuous direction and has a continuous uniform cross-section between them, so that there are no multiple sections inside the container.

[0227] 1106 turbulence is generated on the heat exchange surface within the section.

[0228] According to some embodiments, generating 1106 includes increasing the intensity of turbulence.

[0229] The flow meanders 1108 on the heat exchange surface.

[0230] Repeat one or more of the steps 1104, 1106, and 1108. According to some embodiments, the thermal storage container includes multiple sections, and 1110 is repeated once or more for other parts of the thermal storage container. In some embodiments, the number of sections (n) is between 3 and 30. In some embodiments, the number of sections is between 5 and 20. In some embodiments, the number of sections is between 6 and 10. In some embodiments, the repetition of 1110 terminates when the flow is located in a section with a fluid outlet.

[0231] Fluid is output from the thermal storage container via the fluid outlet 1112.

[0232] According to some embodiments, the order of steps 1104 to 1110 is the same as... Figure 11 The order shown is different. For example, meandering 1108 can occur before generating 1106, meandering 1108 can occur simultaneously with generating 1106, or it can partially overlap with generating 1106.

[0233] According to some embodiments, the thermal system includes a plurality of fluidly connected heat storage containers, and steps 1102 to 1112 are repeated for the heat storage containers.

[0234] Structure of a thermal storage container:

[0235] refer to Figures 12A to 12E , Figures 12A to 12E This is a simplified schematic diagram of the side view and cross-section of a thermal storage container according to some embodiments of the present invention.

[0236] According to some embodiments, such as... Figures 12A to 12E As shown, the thermal storage container 1200 includes a shell 1202, a fluid inlet 1204, and a fluid outlet 1206. In some embodiments, the thermal storage container 1200 has a plurality of fluid inlets 1204. In some embodiments, the thermal storage container 1200 has a plurality of fluid outlets 1206, for example, to fluidly connect the container 1200 to a plurality of downstream containers.

[0237] like Figures 12D to 12EThe illustrated thermal storage container 1200 includes multiple segments 1210 (e.g., segments 1210-1 to 1210-4). Each segment 1210 contains one or more membrane cells containing phase change material and having multiple heat exchange surfaces. In some embodiments, the number of segments in the thermal storage container 1200 is greater than 20. In some embodiments, the number of segments in the thermal storage container 1200 is between 3 and 30. In some embodiments, the number of segments in the thermal storage container 1200 is between 5 and 20. In some embodiments, the number of segments in the thermal storage container 1200 is between 6 and 10. In some embodiments, the number of membrane cells in a segment is greater than 3. In some embodiments, the number of membrane cells in a segment is greater than 5. In some embodiments, the number of membrane cells in a segment is greater than 10.

[0238] like Figures 12A to 12C As shown, container 1200 is longitudinal and has a total longitudinal axis X. (As indicated...) Figures 12A to 12C As shown, the cross-section of the housing 1202, taken along the longitudinal axis X, is selectively uniform. In some embodiments, the cross-section of the housing 1200, taken perpendicular to the longitudinal axis X, has a uniform shape with different dimensions along the length of the heat storage container 1200. According to some embodiments, the cross-section of the housing 1200, taken perpendicular to the longitudinal axis X, is polygonal. In some embodiments, the cross-section includes one or more curved edges. In some embodiments, the cross-section has two or more straight edges. Figure 12C As shown, the thermal storage container 1200 has a rectangular cross-section. In some embodiments, the height of the thermal storage container 1200 is shorter than its width, resulting in a lower profile. In some embodiments, the width of the thermal storage container 1200 is shorter than its height, resulting in a narrower profile. In some embodiments, the thermal storage container 1200 has a square cross-section.

[0239] refer to Figure 12D and Figure 12E , Figure 12D and Figure 12E This is a simplified schematic diagram of the cross-sectional view of the thermal storage container 1200 at sections X1-X1 and X2-X2, according to some embodiments of the present invention.

[0240] According to some embodiments, such as... Figures 12D to 12F As shown, each segment 1210 accommodates one or more membrane cells 1212, which contain phase change material and have multiple heat exchange surfaces (e.g., 1214-1 / 2 of membrane cell 1212-1 and 1214-3 / 4 of membrane cell 1212-2).

[0241] According to some embodiments, the membrane cartridge 1212 is positioned to have a plurality of fluid flow channels 1216 between a plurality of heat exchange surfaces. In some embodiments, fluid flow channels 1214 are defined between adjacent heat exchange surfaces 1214. In some embodiments, as described elsewhere herein, at least some membrane cartridges are disposed at a connected pair of membrane cartridges, each membrane cartridge having a heat exchange surface facing the heat exchange surface of the other membrane cartridge, wherein there are spacers between the plurality of heat exchange surfaces, the spacers being fluid channels. In some embodiments, as described elsewhere herein, the plurality of spacers prevent blockage of the channels, for example, when the membrane cartridge expands due to freezing of the phase change material.

[0242] According to some embodiments, channel 1216 defines a flow labyrinth in which flow is guided to multiple changing directions. In some embodiments, the flow labyrinth is adjacent to a heat exchange surface. In some embodiments, when the fluid inlet and fluid outlet are located on opposite sides of the heat storage container, the length of the labyrinth is longer than the length of the heat storage container. In some embodiments, when the fluid inlet and fluid outlet are located on the same side of the heat storage container, the length of the labyrinth is twice the length of the heat storage container.

[0243] refer to Figure 13 and Figure 14 , Figure 13 and Figure 14 This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention.

[0244] Thermal storage containers 1300 and 1400 are similar to thermal storage container 1200, except that the fluid inlet 1304 / 1404 and the fluid outlet 1306 / 1406 are located on the same side of the shell 1302 / 1402. Figure 13 and Figure 14 As shown, the fluid inside containers 1300 / 1400 flows in two directions along the longitudinal axis X. The first direction is defined by the inlet 1304 / 1404, and the second direction is defined by the outlet 1306 / 1406.

[0245] According to some embodiments, containers 1300 / 1400 have partition walls 1308 / 1408 that split fluid flow in two directions. In some embodiments, partition walls 1308 / 1408 increase the structural strength of containers 1300 / 1400. According to some embodiments, separation between sections with different dominant flow directions is achieved by abutting the walls of adjacent membrane cells located at sections with different flow directions (e.g., sections 1410-4 and 1410-5), so that there is no defined flow path between adjacent membrane cells. In some embodiments, abutment is achieved by coupling adjacent membrane cells located at the narrow facets of the membrane cells. In some embodiments, abutment is achieved by pressing the narrow faces of adjacent membrane cells against each other while pressing their opposite faces against the container shell.

[0246] According to some embodiments, such as... Figure 13 As shown in enlarged view A, the isolation wall 1308 has at least one opening 1310. In some embodiments, the opening 1310 is smoothly connected between multiple segments. In some embodiments, the opening 1310 allows fluid flow to change direction, for example, from an internal direction defined by inlet 1304 to an external direction defined by outlet 1306.

[0247] According to some embodiments, such as... Figure 14 As shown, the isolation wall 1308 has one or more conduits 1410 that smoothly connect multiple sections. In some embodiments, the conduits 1410 enable fluid flow to change direction, for example, from an internal direction defined by an inlet 1404 to an external direction defined by an outlet 1406. In some embodiments, the conduits 1410 are disposed on the side of the housing 1402 opposite to the inlet 1410.

[0248] In some embodiments, one or more spacers are present next to the inlet turning point and / or outlet, the spacers being configured to maintain space between the membrane cartridge and the container wall, the space allowing fluid to diffuse between the inlet and the first unprocessed membrane cartridge, and between the last unprocessed membrane cartridge and the outlet.

[0249] An exemplary configuration of the membrane chamber inside the thermal storage container:

[0250] According to some embodiments, the internal configuration of the thermal storage container is defined to control the fluid flow path within the container. In some embodiments, the internal configuration alters the flow direction, resulting in a flow pattern that curves along the length of the thermal storage container.

[0251] like Figures 7A to 7D as well as Figures 12D to 14As shown, the membrane capsule fills the thermal storage container and couples to the wall of the container's shell. This internal configuration of the membrane capsule guides fluid flow across its heat exchange surface, where multiple gaps are defined. In some embodiments, when there is no wall-facing heat exchange surface, there is a flush contact between the membrane capsule and the container wall.

[0252] One potential advantage of directing flow to the heat exchange surface is higher heat dissipation efficiency of the heat capacity stored in the membrane capsule. Another potential advantage is faster cold storage, especially when the container is partially cold-storage.

[0253] like Figures 12D to 12E As shown, according to some embodiments, membrane cartridges 1212 are grouped to assemble one or more segments 1210 within housing 1202. In some embodiments, a group of membrane cartridges 1212 fills most of the internal volume of the segment, leaving only gaps between the heat exchange surfaces of the membrane cartridges to define flow paths / labyrinths.

[0254] According to some embodiments, when the membrane capsule contains frozen phase change material, the gap between the heat exchange surfaces of the membrane capsule is between 0.5 cm and 10 cm. In some embodiments, when the membrane capsule contains frozen phase change material, the gap between the heat exchange surfaces of the membrane capsule is between 2 cm and 7 cm. In some embodiments, when the membrane capsule contains frozen phase change material, the gap between the heat exchange surfaces of the membrane capsule is between 4 cm and 5 cm.

[0255] like Figure 2H , Figure 7A and Figure 14 As shown, one or more segments 1410 include a plurality of membrane cells 114, 715, 1412, which are adjacent to each other at their narrow faces (non-heat exchange surfaces).

[0256] like Figures 12D to 12E As shown, the orientation of the ice film boxes 1212 differs between multiple segments 1210. In some embodiments, the orientation of the film box 1212 in one segment 1210 differs from the orientation of the film box 1212 in a downstream or upstream segment. In some embodiments, the orientation of the film box 1212 is modified by making the film boxes 1212 in some segments 1210 laterally oriented relative to the film boxes 1212 in other segments 1212.

[0257] In some embodiments, segment 1212 is defined as part of a thermal storage container 1200 having a set / group of membrane cassettes 1212 with a consistent orientation. In some embodiments, segment 1212 is defined as part of a thermal storage container 1200 having a set / group of membrane cassettes 1212 of a consistent type. In some embodiments, the type of membrane cassette is defined by its shape. In some embodiments, the type of membrane cassette is defined by the phase change material within it.

[0258] According to some embodiments, the orientation of the membrane cassette 1212 is defined relative to the longitudinal axis X of the heat storage container 1200. In some embodiments, the orientation of the membrane cassette 1212 includes a rotational angle about the longitudinal axis X. Figures 12A to 14 As shown, in some embodiments, the orientation of membrane cartridges 1212 in certain segments 1210 is perpendicular to the orientation of membrane cartridges 1212 in other segments 1210. In some embodiments, the orientation of membrane cartridges 1212 in one segment 1210 (e.g., 1210-2) is perpendicular to the orientation of membrane cartridges 1212 in the downstream or upstream segment 1210 (1210-3).

[0259] like Figures 12A to 14 and Figure 2H , 7A As shown in the examples, according to some embodiments, the orientation of the membrane cassette 1212 in certain sections 1210 is vertical. In some embodiments, the vertical orientation is defined as the membrane cassette 1212 being oriented in a vertical position and parallel to the longitudinal axis X of the thermal storage container (e.g., 114 / 715 / 1212-1). Figures 12A to 14 As shown, in some embodiments, the orientation of the membrane 1212 in certain sections 1210 is horizontal.

[0260] In some embodiments, adjacent segments (e.g., 1210-1 and 1210-2) have a change in the orientation of the membrane 1212, some segments 1210 have a vertical membrane 1212, and some segments 1210 have a horizontal membrane 1212.

[0261] One potential advantage of placing membrane capsules in alternating directions (e.g., horizontal / vertical) is that it alters the fluid flow within the container from horizontal to vertical (and vice versa). As the fluid flows through the gaps in the membrane capsule's heat exchange surfaces, the alternating fluid flow can change the fluid's velocity, turbulence, length, and direction, potentially creating highly turbulent (e.g., eddy currents) flow on the heat exchange surfaces in downstream sections.

[0262] According to some embodiments, the orientation of the membrane cassettes within a segment is not consistent. In some embodiments, within a single segment, the membrane cassettes are oriented laterally to other membrane cassettes. In some embodiments, within a single segment, some membrane cassettes are vertical and some membrane cassettes are horizontal.

[0263] refer to Figure 15A and Figure 15B , Figure 15A and Figure 15B This is a simplified schematic diagram of a cross-sectional view of a thermal storage container according to some embodiments of the present invention.

[0264] like Figure 15A and Figure 15B As shown, the heat storage container 1500 / 1500' selectively includes a plurality of membrane cartridges 1502, each membrane cartridge 1502 having a plurality of heat exchange surfaces 1506 and disposed within a housing 1510 such that the heat exchange surfaces 1506 are laterally oriented in the overall flow direction (on the longitudinal axis X). The internal configuration of the membrane cartridges 1502 within the housing 1510 defines a meandering flow path 1504 along the longitudinal axis X. The membrane cartridges 1502 are oriented via a gap 1508 defined between the membrane cartridges 1502 and the housing 1510 to guide the flow 1504 between the heat exchange surfaces 1506. In some embodiments, for example, as Figure 15A As shown, the angle between the heat exchange surface 1506 and the general flow direction is less than 90°. Figure 15B An example of a membrane capsule with a 90° angle between the heat exchange surface 1506 and the general flow direction is shown.

[0265] According to some embodiments, Figure 15A and Figure 15B The cross-sectional view is a top view of the thermal storage container 1500 / 1500', therefore, the flow 1504 turns at least partially in the horizontal direction. In some embodiments, Figure 15A and Figure 15B The cross-sectional view is a side view of the thermal storage container 1500 / 1500', such that the flow 1504 is at least partially turned in the vertical direction.

[0266] Figure 15A This illustrates a meandering flow path defined by a single membrane capsule 1502. In some embodiments, such as... Figure 15B As illustrated in the example, the meandering flow path 1504 is defined by a set of membrane cartridges 1512. In some embodiments, when blocked by one of the membrane cartridges 1502 in the set of 1512, the path 1504 is redirected, wherein the membrane cartridge 1502 engages with the wall of the housing 1510. In some embodiments, one or more of the membrane cartridges in the set of 1510 do not engage with the wall of the housing 1510, thereby allowing parallel fluid to flow across the heat exchange surfaces of the multiple membrane cartridges.

[0267] refer to Figure 16 , Figure 16 This is a cross-sectional view of a heat storage container according to some embodiments of the present invention.

[0268] like Figure 16 As shown in the example, the thermal storage container 1600 includes a plurality of membrane cells 1602 disposed within a housing 1610 and a plurality of flow-blocking elements 1604 disposed between the membrane cells 1602. During operation, when the flow 1606 flowing along the general flow direction along axis X impacts the flow-blocking element 1604, the profile of the flow 1606 changes. In some embodiments, the direction of the flow 1606 changes upon impact with the flow-blocking element 1604. In some embodiments, impacting the flow-blocking element 1604 enhances the turbulence of the flow 1606.

[0269] According to some embodiments, the cross-sectional view of the thermal storage container 1600 is a top view, so the membrane box is vertical. In some embodiments, the cross-sectional view of the thermal storage container is a side view, so the membrane box is horizontal.

[0270] refer to Figure 17 , Figure 17 This is a cross-sectional view of a heat storage container according to some embodiments of the present invention.

[0271] like Figure 17 As shown in the example, the thermal storage container 1700 may include a plurality of membrane boxes 1704 and 1706 disposed within the housing 1710, wherein the plurality of membrane boxes are oriented perpendicularly to each other about the longitudinal axis X.

[0272] According to some embodiments, the direction of flow 1712 is altered by coupling one or more flow deflectors 1708 between the heat exchange surfaces of membrane 1706. In some embodiments, one or more flow deflectors 1708 are coupled to membrane 1706. In some embodiments, flow deflectors 1708 are ribs defined on the heat exchange surfaces of membrane 1706. In some embodiments, flow deflectors 1708 guide flow 1712 received from upstream membrane 1704 between a plurality of flow deflectors 1708 located downstream of the thermal storage vessel. In some embodiments, flow deflectors 1708 guide flow 1712 received from upstream membrane 1704 to downstream membrane 1714.

[0273] According to some embodiments, the guide flow 1712 between the upstream 1704 and the downstream 1714 is mixed into flow 1712.

[0274] Figure 17 The cross-sectional view in the image shows a top view of the thermal storage container 1700, where the membrane cassette 1704 is vertical. Figure 17 The cross-sectional view in the image shows a top view of the thermal storage container 1700, where the membrane cassette 1704 is horizontal.

[0275] Bidirectional flow on the membrane capsule:

[0276] According to some embodiments, the flow length on the heat exchange surface inside the thermal storage container is extended by guiding the flow, thereby forming a bidirectional flow on one or more membrane cells disposed inside the thermal storage container.

[0277] refer to Figure 18A and Figure 18B , Figure 18A and Figure 18B This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention.

[0278] like Figure 18A and Figure 18B As shown in the example, the heat storage container 1800 has a plurality of membrane cartridges 1802 disposed within a housing 1810. Each membrane cartridge 1802 is box-shaped and has two sides, each having a larger area than the other sides. The two larger sides act as heat exchange surfaces 1812 and extend in a direction perpendicular to the flow 1808. One or more of the heat exchange surfaces 1812 are divided into a first portion 1806-1 and a second portion 1806-2 by membrane cartridge separators 1804. According to some embodiments, the separator 1804 is a rubber sealing ring coupled to one or more sides of the membrane cartridge 1802. In some embodiments, the separator 1804 is a protrusion of the heat exchange surface 1812. In some embodiments, the separator 1804 is a rib formed on the heat exchange surface 1812. In some embodiments, all of the membrane cartridges 1802 include the separator 1804. In some embodiments, a portion of the plurality of membrane cartridges 1802 has the separator 1804, while some of the membrane cartridges 1802 partially have the separator 1804. In some embodiments, some membrane cartridges without separators can cause flow mixing.

[0279] like Figure 18A As shown, the fluid flow in the heat storage container 1800 is a bidirectional flow on the heat exchange surface 1812, flowing in a first direction on a portion of the surface 1812 and in a second direction on another portion of the surface 1812. The flow 1808 begins at the inlet in one direction 1808-1, crosses the first portion 1806-1 of the membrane box 1802, turns at the end wall of the shell 1810, and then resumes its flow in the direction 1808-2 toward the outlet by flowing through the second portion 1806-2 of the membrane box 1802.

[0280] In some embodiments, bidirectional flow results in internal circulation of the phase change fluid within the membrane chamber 1802. In some embodiments, the temperature of a portion of the heat exchange surface at the first portion 1806-1 differs from that at the heat exchange surface at the second portion 1806-2. According to some embodiments, the temperatures of the first portion 1806-1 and the second portion 1806-2 are influenced by the fluid flow, and a temperature gradient is established within the membrane chamber 1802. In some embodiments, the first portion 1806-1 will melt faster than the second portion 1806-2 due to heat exchange with the hotter fluid (the upstream fluid is hotter than the downstream cooled fluid). In some embodiments, the location of the inlet and outlet affects the melting rate. A superficial advantage of the temperature gradient is the circulation of the phase change material within the membrane chamber 1802, which provides a mixing effect. This mixing can break down potential build-up of isolative barriers of the melted phase change material within the 1802 membrane chamber.

[0281] According to some embodiments, when the first portion 1806-1 is the upper portion of the membrane cassette 1802, the phase change material in the upper portion melts faster than in the lower portion. For example... Figure 18B As shown, the internal circulation within membrane chamber 1802 causes the frozen material to float upwards, while the cooling cycle of the fluid flow first melts the upper part 1806-1 of membrane chamber 1802. In this way, the mixing and cooling rate of liquid / ice may be higher than when no phase change material is mixed, because the molten liquid water barrier between the ice and the membrane chamber wall is reduced.

[0282] Another potential advantage of separate membrane chambers is that they allow for faster cold storage. The freezing of the membrane chambers is faster when the phase change material is mixed during the cold fluid flow within the cold storage cycle, during which the cold fluid is injected into the heat storage container through the lower portion of the membrane chamber.

[0283] The geometry of the membrane box:

[0284] As discussed elsewhere in this article and in Figure 2R , 7A and 12A to Figure 14 The membrane capsule shown, according to some embodiments, is a box-shaped or plate-shaped capsule having two surfaces with a larger surface area than the other surface. According to some embodiments, the two larger surfaces act as heat exchange surfaces.

[0285] Larger heat exchange surfaces allow for the flow and heat exchange of larger volumes of fluid within a single channel. In some embodiments, the width and height of the larger surface range from 20 to 60 cm. In some embodiments, the width and height of the larger surface range from 25 to 50 cm. In some embodiments, the width and height of the larger surface range from 30 to 45 cm.

[0286] A narrow membrane chamber can potentially reduce the thermal barrier formed by molten phase change material surrounding the membrane chamber and the non-molten material inside the heat exchange surface. In some embodiments, the minimum width of the membrane chamber in the unfrozen state is in the range of 1 to 10 cm. In some embodiments, the width of the membrane chamber in the unfrozen state is in the range of 2 to 8 cm. In some embodiments, the width of the membrane chamber in the unfrozen state is in the range of 2.5 to 5 cm.

[0287] According to some embodiments, when preparing the thermal storage container 1200 for installation, the step includes placing the membrane assembly 1212 within the housing 1202. In some embodiments, the membrane assembly 1212 is placed in a sliding manner within the housing 1202. In some embodiments, the membrane assembly 1212 is placed within the housing 1202 during the manufacture of the thermal storage container 1200.

[0288] According to some embodiments, the membrane assembly has a rectangular cross-section. In some embodiments, the cross-section matches the cross-section of the housing 1202. In some embodiments, the cross-section is square. A potential advantage of the square cross-section of the membrane assembly and the housing is that the membrane assembly can be installed vertically or horizontally within a section of the thermal storage container without needing to define different membrane assemblies based on the placement orientation.

[0289] According to some embodiments, one or more of the four surfaces of the cascade membrane cartridge having an area smaller than the heat exchange surface are side surfaces configured to support the membrane cartridge when disposed within a heat storage container. In some embodiments, one or more side surfaces are shaped to engage with the container wall. In some embodiments, engaging the side surfaces with the container wall is to eliminate gaps between the outer surface of the membrane cartridge and the heat storage container wall. In some embodiments, the membrane cartridge is shaped to guide fluid flow within the heat storage container via gaps between the membrane cartridges. In some embodiments, the membrane cartridge is located within a container, with gaps between the container's side surfaces and the wall surfaces to guide fluid flow through the gaps.

[0290] refer to Figure 19 , Figure 19 This is a cross-sectional view of a heat storage container according to some embodiments of the present invention.

[0291] According to some embodiments, one or more walls of the thermal storage container are curved. For example... Figure 19 As shown, the cross-section of the thermal storage container 1900 has two curved walls 1910-1 / 1910-2. The thermal storage container 1900 is filled with a plurality of membrane boxes 1904, which are shaped to be placed within the thermal storage container 1900, adjacent to the curved walls 1902 and adjacent membrane boxes. The gaps 1906 between the plurality of membrane boxes 1904 define fluid paths on the heat exchange surfaces of the plurality of membrane boxes 1904.

[0292] According to some embodiments, the membrane box is cylindrical. In some embodiments, the membrane box is cylindrical when the heat storage container does not have curved walls.

[0293] According to some embodiments, the membrane box disposed within the thermal storage container has a combination of concave and convex profiles, thereby defining the gap between the membrane box profiles.

[0294] According to some embodiments, the membrane box is long and twisted along its length. In some embodiments, the membrane box is long and cylindrical. In some embodiments, the membrane box is long and has one or more long planes. In some embodiments, the membrane box is long and has a cross-section in the shape of a cross.

[0295] According to some embodiments, such as Figure 12F As shown, the membrane capsule 1210 includes one or more protruding surfaces 1216 configured to guide fluid flow in a meandering pattern.

[0296] The membrane box can be used with curved or other shaped containers. The membrane box can be customized. The membrane box can have a curved shape.

[0297] Thermal storage container in the system:

[0298] According to some embodiments, the thermal system includes a plurality of thermal storage containers as defined above. In some embodiments, the thermal system includes a plurality of thermal storage containers having the same internal orientation and structure. In some embodiments, the thermal storage containers in the thermal system have uniform external dimensions. In some embodiments, the thermal storage containers in the thermal system have uniform cold storage characteristics (e.g., cold storage rate, cold storage capacity). In some embodiments, the thermal storage containers in the thermal system have uniform cold extraction characteristics (e.g., cold extraction rate, cold extraction temperature).

[0299] In some embodiments, the thermal system includes a plurality of heat storage containers with different internal configurations. In some embodiments, the difference lies in the orientation of the membrane capsules. In some embodiments, the heat storage containers connected to the thermal system have different external dimensions. In some embodiments, the heat storage containers in the thermal system have different cold storage characteristics (e.g., cold storage rate, cold storage capacity). In some embodiments, the heat storage containers in the thermal system have different cooling characteristics (e.g., cooling rate, cooling temperature).

[0300] According to some embodiments, the thermal system includes thermal storage containers of different technologies. In some embodiments, the thermal system includes one or more ice tray containers and one or more thermal storage containers, as disclosed elsewhere herein.

[0301] In some embodiments, containers of different technology types are connected in series. In some embodiments, containers of different technology types are connected in parallel. In some embodiments, one or more controllers are used to coordinate the operation of the containers.

[0302] Figure 20 This is a simplified schematic diagram of a perspective view of a thermal storage container configuration according to some embodiments of the present invention; and

[0303] Figure 21 This is a simplified schematic diagram of a cross-sectional view of a heat storage container according to some embodiments of the present invention.

[0304] Exemplary system parameters:

[0305] In some embodiments of the invention, for example, the length of the flow path in the container (e.g., the intermediate path length of 80% of the flow) is between 1 and 100 meters, such as between 1 and 20 meters, 20 and 50 meters, 50 and 100 meters, and / or intermediate or longer paths, such as between 100 and 200 meters or longer. In some embodiments of the invention, the length is between 15 and 20 meters, for example, approximately 16 meters.

[0306] In some embodiments of the invention, the surface area of ​​the heat exchange surface in the container is between 1 and 200 square meters, for example: between 1 and 30 square meters, between 30 and 80 square meters, between 80 and 200 square meters, and / or an area of ​​intermediate or larger. In some embodiments of the invention, the area is between 30 and 45 square meters, for example: approximately 37 square meters.

[0307] According to some embodiments, the membrane capsule is filled with a phase change material frozen at temperatures ranging from -8.0°C to -2.0°C.

[0308] Because of the requirement for ultra-deep freezing, phase change materials are frozen at relatively low temperatures. This can be achieved by adding nucleating agents and selectively without stirring (e.g., vibration, ultrasound, etc.). In some embodiments, the phase change material is frozen at temperatures from -7°C to -2.5°C. In some embodiments, the phase change material is frozen at temperatures from -5°C to -4°C.

[0309] According to some embodiments, during operation, the volume of fluid flowing within the container in contact with the heat exchange surface is at least 70% of the volume of fluid injected into the container. In some embodiments, the volume of fluid flowing within the container in contact with the heat exchange surface is at least 90% of the volume of fluid injected into the container.

[0310] According to some embodiments, the ratio between the flow cutting area and the area of ​​the heat exchange surface is in the range of 0.008 to 0.05. In some embodiments, the ratio between the flow cutting area and the heat exchange surface area of ​​each ice block is about 1:35600 = 0.000029 cm² / cm², and / or the ratio of each membrane box is about 0.00056 cm² / cm².

[0311] An additional parameter describing the flow in a thermal storage container is the ratio between the flow cross-sectional area and the total heat exchange area of ​​all membrane cells in the container. Note that in some embodiments described herein, the flow cross-sectional area varies along the flow path. In this case, the ratio may optionally be calculated as the ratio between the average flow cross-sectional area along the flow path in the container and the total heat exchange area of ​​all membrane cells in the container. It should be noted that this ratio is between areas and is therefore dimensionless.

[0312] In some embodiments, the ratio between the flow cross-sectional area of ​​all membrane cells in the heat storage container and the total heat exchange area is 4.5 × 10⁻⁶. -5 Up to 45×10 -5 Between, and a typical ratio could be 14 × 10 -5 In some embodiments, the range can be 1×10 -5 Up to 100x10 -5 Between 0.5 × 10⁻⁶. In some embodiments, the range may be between 0.5 × 10⁻⁶. -5 Up to 200×10 -5 between.

[0313] In some embodiments, the flow cut-off area in a container with a total fluid length of 16 meters is between 5 and 20 square centimeters. In some embodiments, the flow cut-off area is between 10 and 15 square centimeters. According to some embodiments, the flow is turbulent for at least 35% of the flow length.

[0314] As disclosed elsewhere herein, a potential advantage of a thermal system with a thermal storage container is a high thermal discharge rate during a cooling cycle. In some embodiments, the discharge rate is at least 70% of the stored energy over a 4-hour period. In some embodiments, the discharge rate is at least 85% of the stored energy over a 4-hour period. In some embodiments, the discharge rate is at least 90% of the stored energy over a 4-hour period. In some embodiments, the discharge rate is at least 85% of the stored energy over a 4-hour period. In some embodiments, the discharge rate is at least 85% of the stored energy over a 4-hour period. In some embodiments, the discharge rate is at least 85% of the stored energy over a 2-hour period. In some embodiments, the discharge rate is at least 75% of the stored energy over a 1-hour period.

[0315] In some embodiments, a high cooling rate is maintained until 70% of the heat capacity stored in the thermal storage container is used. In some embodiments, a high cooling rate is maintained until 80% of the heat capacity stored in the thermal storage container is used. In some embodiments, a high cooling rate is maintained until 90% of the heat capacity stored in the thermal storage container is used.

[0316] Figure 22 This is an example of a data sheet for a thermal storage container according to some embodiments of the present invention.

[0317] According to some embodiments, a container is 4 meters long, guiding the flow in two internal channels (making the total length of the flow 8 meters), and the flow takes 80 seconds within the container. In this example, the fluid velocity is approximately 0.1 to 0.09 meters per second as it flows in the space between membrane cells on the heat exchange surface.

[0318] Now for reference Figures 1A to 1E , Figures 1A to 1E This is a schematic diagram of a thermal energy storage system according to at least some embodiments of the present invention. As shown, the thermal energy storage (TES) system 100 uses an HVAC cooler 102 of an air conditioning (HVAC) system in the facility. Non-limiting examples of facilities include: office buildings, residential buildings, shopping malls, airport terminals, factories, server rooms, or similar facilities. When operating without the system 100 of the present invention, the HVAC cooler 102 cools a third fluid 124, which is then circulated throughout the facility for use by a cooling load unit 130. The third fluid 124 is optionally water.

[0319] As described above, the object of the present invention is to use the TES 100 for “storage cooling”. Alternatively, the same system 100 can be used to store heat. The TES 100 includes a fluid distribution system 104, which includes the components required to distribute a first fluid 120, a second fluid 122, and a third fluid 124 to the entire system 100. Thus, the distribution system 104 includes one or more pumps 106, pipes 108, flow control mechanisms 107 (e.g., valves), and a monitoring component 109 for monitoring temperature and flow rate within the system 100. The monitoring component 109 optionally feeds data to a controller 105, thereby controlling the freezing and / or cooling process by controlling the components of the coolers 102 and 150, HE 170, load cell 130, array 110, and fluid distribution system 104, as further described below. During normal use, the HVAC cooler 102 cools a third fluid 124, which is guided by the fluid distribution system 104 from the HVAC cooler 102 via pipe 108C to pipe 108L, so as to flow through the load machine 130.

[0320] The TES 100 also includes a thermal storage array 110. Array 110 includes multiple ice blocks 112. Each ice block 112 includes multiple ice film boxes 114 surrounded by a first fluid 120. See below for reference. Figures 2A to 2U and Figure 3 The following description will further illustrate embodiments of the ice block 112 and the ice film box 114. The ice film box 114 is a closed or sealed film box containing a second fluid 122. The second fluid 122 is selectively water, which exposes the film box 114 to a low-temperature first fluid 120 surrounding the film box 114, thereby causing the film box 114 to cool, and the second fluid 122 to cool and change phase to ice.

[0321] The first fluid 120 selectively has a lower freezing point than the second fluid 122. Non-limiting examples of the first fluid 120 include ethylene glycol, ethylene glycol mixed with water, brine, or similar fluids. The TES 100 also includes a TES cooler 150 for cooling the first fluid 120 to a temperature below the freezing point of the second fluid 122. The TES cooler 150 is either air-cooled or water-cooled.

[0322] The second fluid 122 is selectively water mixed with an ice nucleating agent. The ice nucleating agent is selectively quartz. The type of quartz used may be, but is not limited to: Herkimer diamond, colorless quartz, amethyst, citrine, rose quartz, chalcedony, cryptocrystalline quartz, agate, chalcedony, aventurine, agate stone, onyx, jasper, milky quartz, smoky quartz, tiger's eye, citrine, emerald, rutilated quartz, or blue-lined quartz. Quartz is inexpensive, readily available, and resistant to repeated freezing cycles of the second fluid. Furthermore, quartz raises the initial freezing temperature required by several degrees. Therefore, the nucleating agent improves the efficiency and responsiveness of the thermal energy storage system 100.

[0323] Optionally, the second fluid 122 includes metal strips floating within the membrane chamber 114, causing the ice within the membrane chamber 114 to form a uniform distribution. Optionally, the metal is aluminum. Optionally, the thickness of the metal strip does not exceed 0.5 mm. Optionally, the length of the metal strip is at most 30 cm, and the width of the metal strip is at most 1 cm. (Reference) Figures 8A to 8B This optional aspect will be explained in more detail.

[0324] Each ice block 112 selectively has, as Figures 2E to 2HThe elongated shape factor shown is used to achieve efficient heat transfer between the membrane 114 and the first fluid 120. The ice blocks 112 with the elongated shape factor selectively have a length L that is at least three or four times greater than their maximum width W and / or height H. The ice blocks 112 can be selectively connected end-to-end to form a long linear module comprising multiple ice blocks 112. The modular structure used and the number of ice blocks 112 allow control over the cooling rate to meet the exact thermal energy storage requirements of each facility, and also provide flexible installation options, such as allowing the array 110 to be shaped as needed. Reference Figure 8A and 8B This optional aspect will be explained in more detail.

[0325] Membrane cartridges 114 are selectively spaced slightly within ice block 112 to increase the overall ratio between the surface area and volume of the second fluid 122 to be frozen. Optionally, ice block 112 contains 65% to 85% of the second fluid 122. Optionally, ice block 112 contains 75% of the second fluid 122. Membrane cartridges 114 selectively contain a polymer, such as polyvinyl chloride or other suitable durable and low-cost material. Membrane cartridges 114 selectively include protrusions or ridges on their outer surface to provide spacing between the cartridges 114 for the flow of the first fluid 120 and for increasing the turbulence of the first fluid 120.

[0326] In use Figure 1A In the system 100 shown, the TES cooler 150 selectively cools the first fluid 120 to a temperature below the freezing point of the second fluid 122. The first fluid 120 is pumped from the TES cooler 150 via conduit 108G and guided by the fluid distribution system 104 via conduit 108T through the array 110 to freeze the second fluid 122 (also referred to herein as the "charging process"). The heated first fluid 120 then leaves the array 110 via conduit 108T and is guided by the fluid distribution system 104 back to conduit 108G to cool the cooler 150 again. During the charging process, the supply of the first fluid 120 can be continuous or discontinuous. The charging process is selectively stopped when the desired temperature of the first fluid 120 is reached in one or more ice blocks 112, or when a predetermined time period has elapsed, or when a predetermined amount of energy has been stored in the array 110. The (fully) cold storage array 110 typically includes multiple membrane capsules 114, which have a second fluid 122 in a frozen state.

[0327] Once array 110 has been cooled, a cooling process (also referred to herein as the cooling extraction process) is used to cool load 130 using array 110. First fluid 120 within array 110 is directed via conduit 108T to distribution system 104 and via conduit 108S to heat exchanger 170, where first fluid 120 cools third fluid 124. Distribution system 104 then directs the cooled third fluid 124 via conduit 108H to conduit 108C to flow through HVAC cooler 102, and then to load 130 (via conduit 108L).

[0328] Alternatively, the third fluid 124 runs parallel to the HVAC cooler 102 via pipe 108H and is delivered directly to the load unit 130 via fluid distribution system 104 through pipe 108L. Since the third fluid 124 is already cooled by the first fluid 120 in HE 170, the HVAC cooler 102 does not need to be activated, thus saving energy. As the first fluid 120 circulates between HE 170 and array 110, a membrane cassette 114 containing frozen second fluid 122 cools the first fluid 120, which then directly or indirectly cools the third fluid 124 and the load unit 130. Selectively, the temperature of the first fluid 120 entering the heat exchanger 170 is between 5°C at the inlet and 10°C at the outlet. As the membrane cassette 114 cools the first fluid 120, the frozen second fluid 122 gradually undergoes a phase change and melts until array 110 no longer sufficiently cools the first fluid 120 and array 110 is considered to have been decooled. The (fully) cooled array 110 typically includes a membrane capsule 114 with a second fluid 122 in liquid state.

[0329] The cold storage process selectively occurs during off-peak hours (times with low grid load), while the cooling extraction process can be selectively performed according to the requirements of the load unit 130, even during peak hours. The cooling extraction process is selectively stopped when the shutdown temperature of the first fluid 120 is reached, or when a predetermined time period has elapsed, or when a predetermined amount of energy is output from the array 110, or under the control of the load unit 130, or when the cooling demand at the load unit 130 decreases to a desired level. During the cold storage process, the flow direction of the first fluid 120 within the array 110 can be the same as or different from the flow direction of the first fluid 120 during the cooling extraction process.

[0330] Alternatively, system 100 is used for heating. For heating, TES cooler 150 selectively operates as a heat pump. TES cooler 150 selectively heats first fluid 120 during off-peak hours. First fluid 120 is pumped from TES cooler 150 via conduit 108G and guided by fluid distribution system 104 via conduit 108T and through array 110 to heat second fluid 122 (also referred to herein as a cold storage process). The cooled first fluid 120 then leaves array 110 and is guided by fluid distribution system 104 through conduit 108T and conduit 108G back to TES cooler 150 for reheating. During heating, the supply of first fluid 120 can be continuous or discontinuous. The heating process is selectively stopped when first fluid 120 reaches a desired temperature in one or more ice blocks 112, or when a predefined time period has elapsed, or when predefined energy is stored in array 110, and in similar circumstances. No phase change occurs in the array.

[0331] Once array 110 has stored cold, a heating process (also referred to herein as a cooling process) is used to heat load 130 via array 110. A first fluid 120 within array 110 is introduced into heat exchanger 170 via distribution system 104 through pipes 108T and 108S, where the first fluid 120 heats a third fluid 124. Distribution system 104 then directs the heated third fluid 124 from pipe 108H through pipe 108C to HVAC cooler 102, and then (via pipe 108L) to load 130. Alternatively, the third fluid 124 may be delivered parallel to HVAC cooler 102 via pipe 108H and directly to load 130 via fluid distribution system 104 to pipe 108L. Since the third fluid 124 has been heated by the first fluid 120 in HE 170, HVAC cooler 102 (acting as a heat pump) may selectively not be activated when the third fluid 124 has been heated to generate energy savings. As the first fluid 120 circulates between the heat exchanger 170 and the array 110, the membrane 114 containing the heated second fluid 122 heats the first fluid 120, and then the first fluid 120 directly or indirectly heats the third fluid 124 and the load machine 130.

[0332] The cold storage process can be carried out during off-peak hours (when the grid load is low), while the cooling process can be carried out according to the requirements of the load unit 130, even during peak hours.

[0333] The monitoring component 109 of the fluid distribution system 104 selectively includes one or more temperature monitors for monitoring at least one of the following: the temperature of the first fluid 120 before entering the array 110; the temperature of the first fluid 120 at any location within the array 110; the temperature of the first fluid 120 after leaving the array 110; the temperature of the second fluid 122 within one or more membrane cartridges 114; the temperature of one or more ice blocks 112; the temperature of the first fluid 120 before entering the HE 170; and the temperature of the first fluid 120 upon leaving the HE 170. Additionally or alternatively, the monitoring component 109 includes one or more flow monitors (not shown) for monitoring at least one of the following within the array 110: the flow of the first fluid 120 before, inside, and after the array 110; and the flow of the first fluid 120 before, inside, and after the HE 170.

[0334] Although Figures 1A to 1E A single instance of the components of coolers 102 and 150, HE 170, load cell 130, array 110, and fluid distribution system 104 is shown, but it should be understood that TES 100 may include any appropriate number of these components.

[0335] Figure 1B System 100 with Figure 1A The same method applies, but the illustrated embodiment includes an air compressor 140. The compressor 140 draws in air 126 from the top of each ice block 112. This air 126 is selectively compressed to between 10 and 20 bar, causing the air 126 to be heated due to compression. The compressed air 126 is then pumped to the bottom of each ice block 112 via an air-to-air heat exchanger 142 and / or an expansion valve (not shown), where its temperature drops to between -20 and -30°C. The air 126 is bubbled through each ice block 112 to further cool the contents, and then discharged through the top of the ice block 112 at between -5 and +5°C. This cold air 126 is then returned to the compressor 140, forming a cooling closed loop 108P. For simplicity, the cooling closed loop 108P is shown as being directly connected to the heat storage array 110; however, the cooling closed loop 108P is selectively part of the fluid distribution system 104 and is controlled as with other piping systems described herein. In this embodiment, the second fluid 122 is selectively combined with salt or other suitable materials to lower the freezing point of the second fluid 122.

[0336] Figure 1C The system is compatible with Figure 1AIt operates in the same manner, but if the condensation cycle of the TES cooler 150 is water-cooled, it includes a heat exchanger 152 supplied from a third fluid 124. In this embodiment, the load machine conduit 108K is adapted to connect to HE 152 in the TES cooler 150. The load machine conduit 108K delivers the third fluid 124, which has been cooled by the HVAC cooler 102, and typically the temperature of the third fluid is between, but not limited to, 7 and 12°C.

[0337] The TES cooler 150 then cools the first fluid 120 to a temperature below the freezing point of the second fluid 122 via HE 154, allowing the first fluid 120 to be pumped through array 110 to freeze the second fluid 122 within the diaphragm 114. In other embodiments, the cooling process subsequently occurs in HE 170. This arrangement improves the energy efficiency of the TES cooler 150, which can be adequately supplied with cooled third fluid 124 when the load unit 130 is partially or completely unused, such as, but not limited to, nighttime use in office buildings. Selectively, when the outside temperature is low and electricity costs are low, the HVAC cooler 102 cools the third fluid 124 at night for more efficient and cheaper energy use. Because the water-cooled TES cooler 150 is more efficient, it can also be smaller than in other embodiments using air-cooled coolers.

[0338] Figure 1D The system combines Figure 1B and Figure 1C The function is to provide TES cooler 150 connected to a third fluid via HE 152, and to be supplemented by cooling from compression from air compressor 140.

[0339] Figure 1E The system is compatible with Figure 1A It works in the same manner, but in the illustrated embodiment, some or all of the ice block 112 does not include the membrane box 114. Figure 1E In this embodiment, TES 100 is used to store a first fluid 120 in ice block 112. Therefore, the first fluid 120 is cooled by cooler 150, and the cooled first fluid 120 is then pumped into ice block 112 for storage and use at other times to cool a third fluid (via HE 170). As described above, non-limiting examples of the first fluid 120 include: ethylene glycol, ethylene glycol mixed with water, salt mixed with water, or other combinations of these or other fluids to form a "slush" or similar fluid.

[0340] Now for reference Figures 2A to 2U , Figures 2A to 2U These are diagrams of ice blocks, ice film boxes, and thermal storage arrays according to at least some embodiments of the present invention. Figures 2A to 2DA preferred embodiment of the cassette 114 is shown. The cassette 114 includes a filling nozzle 202 positioned at the upper corner of the cassette 114 to allow the cassette 114 to be filled to its maximum capacity with the second fluid 122 while still effectively packing the cassette 114. The cassette 114 optionally includes narrow-side spacers 204 and wide-side spacers 206. When provided, spacers 204 and 206 form gaps between the cassettes 114 when the cassette 114 is packed within an ice block 112. These gaps allow the first fluid 120 to flow between the cassettes 114, thereby freezing the second fluid 122 within the cassette 114. The cassette 114 has a high ratio of depth D to length L and height H to create a larger surface area around the thinner ice block, allowing for more efficient heat transfer of the second fluid (122).

[0341] Figures 2E to 2H A preferred embodiment of an ice block 112 comprising membrane cartridges 114 is shown. The ice block 112 includes a rectangular housing 220 for enclosing a plurality of membrane cartridges 114. The membrane cartridges 114 are packaged together to maximize the amount of second fluid 122 contained within the ice block 112. Each end of the ice block is equipped with an alignment or support plate 227 for aligning the membrane cartridges 114 and sealing the block end plate 226 so that the ice block 112 is waterproof when sealed. The ice block 112 is connected to the array 110 via inlet / outlet pipes 224. Mounting brackets 222 are used to mount the ice block 112 in a fixed position within the array 110, as described below. Except for the inlet / outlet pipes 224 and interconnecting pipes 228 for connecting the ice block, the ice block 112 is completely sealed to completely contain the first fluid 120 flowing through it.

[0342] Optionally, the ice block 112 has dimensions of 50 × 50 × 400 cm. Optionally, the ice block 112 has a volume of 1000 liters, containing 75% (750 liters) of the second fluid 122. Optionally, the ice block 112 has an energy storage capacity of 19.8 trh / 69 kWh. Alternatively, the ice block 112 has dimensions of 25 × 25 × 400 cm. The dimensions of the ice block 112 are chosen to provide a balance between sufficient energy storage and the modularity of the array's construction.

[0343] Figures 2I to 2N A preferred embodiment of the ice block 112 in a flexible configuration of the hot storage array 110 is shown. The ice block 112 serves as a building block for configuring the array 110 with any desired layout and capacity. Figure 2I and Figure 2J As shown, ice blocks 112 are stacked together, laid end-to-end, and also adjacent to each other. Inlet / outlet pipes 224 and interconnecting pipes 228 are then used to provide fluid connectivity for the first fluid 120 between the ice blocks 112 in the array. The ice blocks 112 are fluidly connected in parallel or alternately in series, or in an alternating combination of parallel and series connections.

[0344] like Figures 2K to 2N As shown, once array 110 is constructed to the required capacity (number of ice blocks 112) and shape (arrangement of ice blocks 112), insulating plate 230 is attached to the outer surface of array 110 to completely insulate the array and retain heat storage within the ice blocks 112. This configuration saves on the total insulation required because only the entire outer surface of array 110 needs insulation, rather than every surface of each ice block 112. Array 110 is selectively assembled on top of base frame 232, which is selectively insulated on its bottom surface.

[0345] Once array 110 has been arranged in the desired configuration (e.g.: Figure 2M rectangular box or Figure 2N A flat platform (or any combination of these forms) can be used to create any structural configuration required for a specific installation, which can be integrated into the structure to which the thermal storage system 100 is applied. As a non-limiting example, Figure 2N The platform can be used as a floor, or it can be erected vertically to serve as a wall, or it can be used as both a floor and a wall, or it can be used as a raised platform inside, beside, or above the building / structure to which the TES system 100 is applied.

[0346] Figures 20 to 2R An additional preferred embodiment of an ice block 112 comprising a membrane 114 is shown, wherein the membrane 114 is narrower in the middle portion, thereby forming gaps between the membrane 114 for the flow of a first fluid 120.

[0347] Figures 2S to 2U Other preferred embodiments of the diaphragm box 114 are shown, wherein the diaphragm box 114 includes a widened central portion with supporting bulges 250, such that the upper portion 256 and the lower portion 254 do not collapse when ice forms inside the diaphragm box 114. When the diaphragm box 114 is packaged within an ice block 112, bulges 250 and 252 form gaps between the diaphragm boxes 114. These gaps are necessary to allow the first fluid 120 to flow between the diaphragm boxes 114, thereby freezing the second fluid 122 inside the diaphragm box 114. The diaphragm box 114 also includes a plurality of protrusions 260. The plurality of protrusions 260 increase the Reynolds number of the first fluid 120 outside the diaphragm box 114, thereby resulting in greater turbulence of the first fluid 120, and thus better ice formation distribution inside the diaphragm box 114.

[0348] Figure 2V A side view of a membrane cartridge 114 with multiple protrusions 260, ridges 252, and filling nozzles 202 is shown. The placement of the filling nozzles ensures that they do not exceed the general external shape of the rectangular membrane cartridge 114. Figure 2W Shown in another side view Figure 2V The membrane box is perpendicular to Figure 2V The view. Figure 2X Shown in the front view Figure 2V and Figure 2W The diagram shows a membrane capsule 114, with its wide side and the general flow direction 290 of the first fluid 120. The membrane capsule 114 has a plurality of protrusions 260, the arrangement of which provides a flow path for the first fluid through the membrane capsule 114 in a zigzag pattern 291 (or serpentine pattern). The zigzag pattern 291, in the context of the invention, is characterized by the repeated changing of the flow direction. Alternatively, the zigzag pattern 291 is characterized by the regular changing of the flow direction. More preferably, at least in a portion of the zigzag pattern, the zigzag pattern is approximately symmetrical about a centerline. Reference numeral 292 refers to a flat area of ​​the membrane capsule 114 between the plurality of protrusions 260. Figure 2Y A perspective view of membrane box 114 is shown, as shown in Figures 2v, 2W and 2X.

[0349] Now for reference Figure 3 , Figure 3 An ice film box according to at least some embodiments of the present invention is shown. For example... Figure 3 As shown, membrane cartridges 114Cy are selectively provided in a cyclohexane shape. During use, multiple cyclohexane-shaped membrane cartridges 114Cy are placed within ice block 112 to allow free settling within the ice block 112. Therefore, membrane cartridges 114Cy are not fixed within the ice block 112. The irregular shape of the cyclohexane-shaped membrane cartridges 114Cy results in a high fill factor within the ice block 112, while simultaneously creating gaps that allow the first fluid 120 to flow around the membrane cartridges 114Cy to freeze the second fluid 122 therein. Furthermore, multiple cyclohexane-shaped membrane cartridges 114C also provide defined flow paths within the ice block 112C, because when multiple cyclohexane-shaped membrane cartridges 114C are placed within a closed volume, these defined cyclohexane-shaped membrane cartridges 114C will create a defined geometric pattern for these membrane cartridges 114C.

[0350] Now for reference Figure 4 , Figure 4 A cylindrical ice block according to at least some embodiments of the present invention is shown. In such... Figure 4 In the optional embodiment shown, ice block 112C is cylindrical and includes membrane cartridges 114C disposed in one or more arrays. Optionally, multiple arrays are placed at different heights within ice block 112C. Optionally, the cylindrical ice block 112C is adapted for placement underground. Ice block 112C is made of a conduit including a spiral metal reinforcement (not shown) extending along the outer side of ice block 112C to place it underground. Optionally, the volume of ice block 112C is between 100 and 10,000 cubic meters.

[0351] Now for reference Figure 5A, Figure 5A This demonstrates a TES system capable of activating independent subsets of ice blocks via a controller. Figure 5B A flowchart showing the operation of the TES system is provided. Figure 5C Experimental data demonstrating the operation of a TES system according to at least some embodiments of the present invention are shown. Figure 5A As shown, the TES system 100 follows... Figure 1A The TES system 100 was built and is in operation. Selectively, Figures 1A to 1E Any embodiment may be as described in reference Figure 5B The method described above is used. Figure 5A In one embodiment, system 100 includes N ice blocks 112, where N is an integer greater than 2. It should be understood that, as described above, array 110 selectively includes as many ice blocks 112 as possible to provide sufficient thermal energy storage. The ice blocks 112 are interconnected with interconnecting pipes 228 using inlet / outlet pipes 224 and further interconnected using components of fluid distribution system 104. Flow controller 107 of fluid distribution system 104 enables array 110 to be partitioned into subsets 520 of ice blocks 112, which can be individually activated in the manner described below.

[0352] As described above, the first fluid 120 flows through the ice block 112 for both cold storage and cooling. Figure 5B In the cooling process 500, the cooling process is activated in step 501. The steps of process 500 are selectively controlled by controller 105, which, as described above, controls the components of system 100. Activation of the cooling process may involve multiple steps, such as, but not limited to, activating pump 106, opening or closing valves in flow controller 107, and monitoring the temperature and flow rate of fluids 120, 122, and 124 using monitoring component 109.

[0353] In step 502, as part of the activation process, controller 105 activates a first subset 520A of ice blocks 112, and the first fluid 120 is pumped only through this first subset 520A and not through any other ice blocks 112. Figure 5A As shown, the first subset 520A includes ice blocks 112A and 112B; however, any number of ice blocks 112, even a single ice block 112, may be included in the subset, and examples of two ice blocks 112 in subset 520 should not be considered limiting. Optionally, multiple subsets 520 are activated in step 502. The first fluid 120 is cooled while the second fluid 122 is heated as it passes through the first subset 520A. In step 503, the temperature of the first fluid 120 is monitored, for example, by monitoring component 109 as the first fluid 120 leaves array 110. Optionally, the temperatures of other fluids in system 100 are also measured in step 503.

[0354] In determination step 504, monitoring component 109 indicates whether the monitored temperature has risen above a defined threshold. If the monitored temperature does not exceed the threshold, controller 105 takes no action and continues monitoring step 503. When monitoring component 109 indicates that the temperature has risen above a defined threshold (selectively defined in controller 105), it means that the second fluid 122 passing through subset 520A is no longer adequately cooled by subset 520A because the temperature of the second fluid 122 in subset 520A has risen. In a non-limiting example, when the temperature of the first fluid 120 rises by more than 5°C at the outlet of array 110, subset 520A no longer adequately cools the first fluid 120.

[0355] In determination step 505, controller 105 checks whether all subsets of ice blocks 112 have been activated. If it is determined that no subset of ice blocks 112 is activated, in step 506, controller 105 activates the next subset 520B of ice blocks 112. As described above, although... Figure 5A The subset 520B shown includes only ice blocks 112C and 112D, but this should not be considered a limitation, and subset 520B may include any number of ice blocks 112. Subset 520B is selectively activated in addition to subset 520. Alternatively, subset 520 is deactivated when subset 520B is activated. Selectively, multiple subsets are activated in step 506. Activation of subset 520B results in a temperature reduction monitored by monitoring component 109 in step 503.

[0356] Repeat steps 503, 504, and 505, as follows: Figure 5B As shown, the cooling process continues until all available subsets of ice blocks 112 (at most subset 520N) are determined to have been used in step 505, and the cooling process 500 is stopped in step 507.

[0357] Figure 5C Displays experimental data from the TES system operation. For example... Figure 5CAs shown in the graph, the temperature of the first fluid 120 was monitored at the outlet of array 110 and plotted as line 532, which is a function of the time elapsed since the cooling process was activated. In the experimental system, three ice blocks 112 were activated at time 0, and as shown, the temperature rose from -5°C to approximately 5°C (at time point 530). At time point 530, in addition to the initial three ice blocks, another ice block was activated, which immediately lowered the outlet temperature shown in graph 532 to approximately 0°C. As the fourth ice block was also cooled, the temperature gradually rose again to approximately 5°C. As can be seen from experimental graph 532, the gradual activation of a subset of ice blocks 112 or ice blocks 520 results in more balanced cooling of the TES system 100, a longer cooling time resulting in a longer TES cooling time for the load machine 130, and better utilization of each fully cooled ice block 112.

[0358] Now for reference Figures 6A to 6G , Figures 6A to 6G Spacers for use in ice blocks according to at least some embodiments of the invention are shown. Spacers 600 and 620 are inserted between membrane boxes 114 within an ice block 112. The ice block 112 may optionally include a plurality of spacers 600 or spacers 620.

[0359] Alternatively, ice block 112 may include a combination of spacers 600 and 620.

[0360] Figure 6D and Figure 6E Two membrane boxes 114 are shown, one of which is not in the cooling ( Figure 6D ) and cold storage ( Figure 6E Any spacer 600 or 620 in the state. Figure 6F and Figure 6G Two membrane chambers 114 are shown, with spacer 620 in the cooling position. Figure 6F ) and cold storage ( Figure 6G (State). For simplicity, two membrane boxes 114 are shown, and it is clear that any number of membrane boxes and spacers can be provided within the ice block 112 as needed. The purpose of spacers 600 and 620 is to maintain a minimum flow area 630 around the membrane boxes 114. The flow area 630 is necessary because when the membrane box 114 is fully chilled (the second fluid 122 (e.g., water) has turned to ice), the membrane box 114 expands. Figure 6E This expansion of membrane 114 can be achieved by contracting the flow region 630. Figure 6E This prevents the flow of the first fluid 120, thereby preventing the first fluid 120 from passing through the ice block and 112, and preventing the effective cooling of the first fluid 120. Furthermore, when the second fluid 122 (e.g., water) is in a cooling state... Figure 6DWhen the membrane 114 contracts and the flow area 630 between the membranes 114 increases, the first fluid velocity decreases significantly, which affects the heat transfer used for cooling and cold storage.

[0361] exist Figure 6A In this embodiment, spacers 600 are fitted between the membrane capsules 114 to ensure a sufficient flow area 630, preventing the membrane capsules 114 from expanding to fill the flow area. Orifices 604 in the spacers 600 allow the first fluid 120 to flow through. When the membrane capsules 114 are cooled, flexible vanes 602 open from the spacers 600 to occupy the flow area 630, thereby increasing the first fluid velocity.

[0362] exist Figure 6B , 6C In the embodiments of 6F and 6G, spacers 620 are fitted between the membrane cassettes 114 to ensure sufficient flow area 630 so that the membrane cassettes 114 do not expand when frozen to fill the flow area 630. Figure 6C The cross-section A'-A' of spacer 620 is shown. The gap 624 between the vertical rod 621 and the horizontal rod 622 in spacer 620 allows the first fluid 120 to flow. Figure 6F As shown, spacer 620 is installed between membrane capsule 114 and vertical rod 621, and horizontal rod 622 increases the flow rate of the first fluid through flow region 630. Figure 6G As shown, when the membrane 114 is cooled and expanded, the spacer 620 prevents the membrane 114 from blocking the flow area 630, thereby ensuring that the first fluid 120 continues to flow around the membrane 114.

[0363] Now for reference Figures 7A to 7D , Figures 7A to 7D Ice block 112, namely thermal energy storage unit 711, is shown.

[0364] Figure 7AThe thermal energy storage unit 711 includes a tube 712 having an elongated, hollow shape. The tube 712 is selectively made of metal, such as carbon steel or stainless steel. A front element 713A and a rear element 713B are provided to close both ends of the tube, thereby providing a rectangular housing. Elements 713A and 713B are also selectively made of metal, such as stainless steel or carbon steel, and provide means for mounting the thermal energy storage unit 711 to, for example, a support device (not shown). The front element 713A and the rear element 713B have an inlet 714A and an outlet 714B, respectively. The inlet 714A and the outlet 714B can be connected to other thermal energy storage units 112, pipes 10, and / or fluid distribution systems 104. Within the tube 712, a plurality of membrane boxes 715 are provided. The membrane boxes 715 have a plate or brick shape. Furthermore, the membrane boxes 715 have a concave or recessed shape on their main surface (i.e., their wide side). The configuration of the membrane cartridges 715 within the tube is selectively configured by a plurality of horizontally arranged stacks 717 of the membrane cartridges 715 (i.e., stacked in the width direction of the tube 712). For example, 16 or 8 membrane cartridges 715 may form a stack 717 of membrane cartridges 715. The plurality of stacks 717 are arranged sequentially along the length of the tube 712. The membrane cartridges contain a phase change material as a second fluid 122 (e.g., water) and a preferred nucleating agent (e.g., quartz). Spaces 716 are provided between the membrane cartridges 715 and between the membrane cartridges and the tube 712, wherein a first fluid 120 (e.g., a water / ethylene glycol mixture) may flow within the tube 712 from inlet 714A to outlet 714B.

[0365] This configuration enables efficient heat exchange between the first fluid 120 and the second fluid 122 via the wall of the membrane 715. The actual heat exchange rate between the membrane 715 and the first fluid 120 depends on several factors, including the flow rate, the effective area of ​​the contact surface between the first fluid 120 and the membrane 715, and the type of flow (e.g., turbulent or laminar). Figure 7A The proposed implementation improves upon all of these factors. This will be explained in more detail below.

[0366] The elongated shape of the tubes in the stacked configuration of the diaphragm boxes 715 defines the remaining free space within the space 716, resulting in multiple predetermined flow paths 718 for the first fluid approaching the diaphragm boxes. The total flow of the first fluid 120 at the inlet 714A is divided into multiple predetermined flow paths 718, each flow path 718 passing through multiple diaphragm boxes along the length of the tube 712. Furthermore, the diaphragm boxes 715 are configured such that the flow paths 718 are defined in both the frozen (expanded) state and the non-frozen (non-expanded) state of the diaphragm boxes 715. In other words, multiple predefined or fixed flow channels for the first fluid 120 are provided between the diaphragm boxes 715, while taking into account the volume changes of the diaphragm boxes due to volume changes of the second fluid, particularly when the phase changes. Therefore, a predefined system of multiple flow paths 718 for the first fluid 120 for heat exchange is provided compared to conventional tank-type thermal energy storage units. The flow of the heat transfer fluid in conventional tank-type thermal energy storage units is highly random, where, for example, the first fluid has difficulty reaching the edge of the tank.

[0367] Furthermore, the plate shape of the membrane 715 geometrically increases the surface area of ​​the membrane 715 (i.e., its surface-to-volume ratio), wherein the largest surface area (i.e., the wide side) of the membrane 715 advantageously defines its main surface for heat exchange.

[0368] Accordingly, Figure 7A Each flow path 718 has a narrow shape aligned parallel to the main surface of the membrane 715. The narrow shape defining the flow path 718 utilizes the main surface of the membrane 715, thereby increasing the heat transfer rate. In other words, the configuration of the above-described thermal energy storage unit 711 significantly increases the effective area of ​​the contact surface for heat exchange while keeping the pressure drop at an acceptable level (e.g., below 1 bar).

[0369] The elongated shape of tube 712 provides a defined flow path for the first fluid 120, which is significantly longer than in conventional systems. As a result, heat exchange between the first fluid 120 and the multiple stacks 717 is optimized, as the stacks 717 are gradually activated during frosting or defrosting of the membrane capsule 715.

[0370] In addition, the average length of the flow path is increased to be longer than the length L of tube 712. This further increases the heat transfer rate.

[0371] Figure 7B The cross-section of the empty tube 712 is shown. Figure 7C A cross-section of tube 712 is shown, including a stack 717 of membrane capsules 715 and liquid (non-freezing) water. Therefore, Figure 7C The thermal energy storage unit 711 is completely cooled. Figure 7DA cross-section of tube 712 is shown, including the stack 717 of membrane capsules 715 and chilled / solid water. Therefore, Figure 7D The thermal energy storage unit 711 is completely cooled. Ideally, if we assume there is no membrane box 715, Figure 7B The tube 712 has a total cross-section (i.e., cross-sectional area) for the tube 712A used for the first fluid 120. If a stack 717 of membrane cartridges 715 is placed within the tube 712, a narrow flow path is provided between the membrane cartridges 715; Figure 7C In this context, one of these narrow flow paths 718 is indicated by multiple circles, which indicate the flow direction of the first fluid 120. For the first fluid 120, the flow path 718 is arranged in a cross-sectional area between each of the two membrane capsules 120 (one of these free-flowing cross-sectional areas of the flow path is in...). Figure 7C (represented by reference numeral 718A in the attached drawing), and Figure 7C On the left and right sides, respectively, between the wall of tube 120 and the outermost left and right membrane boxes 715. Figure 7C In the figure, one of these cross-sectional regions that define the flow path 718 is indicated by reference numeral 718A. Figure 7D Showing with Figure 7C With almost identical configurations, the key difference lies in the smaller remaining cross-sectional area of ​​the flow of the first fluid 120 between the membrane capsules 715, which expands due to the frozen second fluid 122 inside the membrane capsules 715. Figure 7D The designation 718B denotes one of these free-flowing cross-sectional regions, which defines the flow path 718 of the first fluid 120. The arrangement of multiple stacks 717 provides a continuous flow path 718 generally along the length of the tube from the front end to the rear end. The average length of these flow paths 718 is longer than the length of the tube 712 itself. Optionally, the stacks 717 of membrane cartridges 715 have the same number of membrane cartridges 715. Optionally, the stacks 717 are arranged adjacent to each other continuously, such that the flow path 718 is provided by the multiple stacks 717 themselves.

[0372] Because water expands in volume during cold storage / freezing. Figure 7C The membrane box 715 is more than Figure 7BThe membrane capsule 715 requires more space. This effect is also known as the "breathing effect" of the membrane capsule 715. Due to this breathing effect, the remaining space of the first fluid 120 changes depending on the state of the second fluid 122 within the membrane capsule 715. The breathing effect of the membrane capsule 715 must be considered when defining the flow path 718. First, the stack 717 must be adjusted so that the flow path 718 is not blocked in both cold storage and cold extraction states. Second, the stack 717 must be adjusted so that the flow path 718 provides an acceptable pressure drop in both the refrigerated and unrefrigerated membrane capsule 715 states. Third, the overall thermodynamic configuration of the thermal energy storage unit 711 must be optimized. This includes, in particular, the hydrodynamics of the first fluid 120 in the flow path 718, which should be configured to allow for effective heat transfer between the membrane capsule 715 and the first fluid 120.

[0373] The first item mentioned above is to ensure that the flow of the first fluid 120 can be provided at any time.

[0374] The second point above is explained in more detail below. The longer the flow path and the smaller its cross-sectional area, the greater the increase in pressure drop. The disadvantages of increased pressure drop are higher pumping power consumption (i.e., higher system losses and lower overall system efficiency) and increased mechanical requirements on the entire system. Therefore, the pressure drop from the inlet 714A to the outlet 714B of the thermal energy storage unit must be less than 1 bar (atmosphere). Optionally, the thermal energy storage unit is configured such that the pressure drop is less than 0.5 bar in both its fully storable and fully exhaust states.

[0375] Regarding the third point above, the ratio of the combined length of multiple tubes (or a single very long tube) to the flow cut-off area is in the range of approximately 40 to 200 (cm / cm²), and selectively in the range of approximately 60 to 150 (cm / cm²). These ratios of the flow cut-off area to the combined length of the multiple tubes (i.e., the total length of the multiple tubes 712 connected in series) provide an effective heat transfer rate with an acceptable pressure drop.

[0376] On the one hand, this allows the membrane box placed closest to the inlet more time (due to the reduced heat transfer rate caused by the melting of ice inside the membrane box) to continue transferring heat to the first fluid 120 with a lower heat transfer rate and a lower exchange temperature, while the membrane box 715 located further downstream of the flow of the first fluid 120 continues its heat transfer with a higher heat transfer rate.

[0377] The term "flow-cut-area" is a number, calculated as follows:

[0378] AFFCAp=(TCSA-(CCSA-LS+CCSA-FS) / 2×CPS) / CPS

[0379] The variables mentioned above are defined as follows:

[0380] AFFCAp: Average free-flow cut area per membrane capsule

[0381] TCSA: Total usable cross-sectional area of ​​the pipe 712A (see...) Figure 7B );

[0382] CCSA-LS: Liquid second fluid (i.e., cooled state, see...) Figure 7C The cross-sectional area of ​​the membrane box is 715.

[0383] CCSA-FS: Second fluid in frozen state (i.e., cold storage state, see...) Figure 7D The cross-sectional area of ​​the membrane box is 715.

[0384] CPS: The number of 715 diaphragm boxes installed in parallel.

[0385] According to the formula above, the average free-flow cross-sectional area (AFFCAp) of each diaphragm capsule 715 is used to calculate the total available flow area in the cross-section of the tube. Then, this result is used to calculate the average cross-sectional flow area of ​​each diaphragm capsule, i.e., the flow cut area.

[0386] The calculated flow cut area can be used to calculate the gamma ratio, which is a good indicator of the heat transfer efficiency between the membrane and the first fluid, as shown below:

[0387] Gamma ratio: Combined length of multiple tubes / flow cutting area, for example, using centimeters as the unit of length and square centimeters as the unit of area, [cm / square centimeter].

[0388] The gamma ratio depends on several factors, some of which include membrane capsule characteristics and flow path characteristics.

[0389] The gamma ratio [GR] (as described above, the ratio between the linear length of the flow path of the heat transfer fluid (in centimeters) and the free-flow cross-sectional area (in square centimeters) of each membrane box) depends on the thermal performance of the membrane box installed in the ice block and other additional parameters.

[0390] A high gamma ratio can allow for sufficient heat exchange interaction between the membrane and the heat transfer fluid to melt most of the stored energy in the ice at an ideal rate. On the other hand, a high gamma ratio typically means a longer stroke and narrower channels, which can result in a high pressure drop, potentially leading to higher pumping losses and / or higher mechanical loads on the ice block shell.

[0391] Generally, the correlation between GR and membrane performance [CP] and the heat transfer coefficient [HTC] of the heat transfer fluid is as follows:

[0392] GR = K * (1 / CP * HTC)

[0393] Where K is an empirical factor.

[0394] Typical factors that improve (increase) CP:

[0395] The ratio of membrane box area to membrane box volume (cm²) 2 / cm 3 );

[0396] The reciprocal of the thickness of the membrane box (1 / cm);

[0397] The material of the membrane casing wall (thermal conductivity) (W / (m*K)). By way of some non-limiting examples: the thermal conductivity of HDPE is about 0.5 (W / (m*K)), and the thermal conductivity of aluminum is about 200 (m / (m*K)); and

[0398] Using internal heat transfer strips

[0399] Typical factors that improve (enhance) HTC:

[0400] The length of the flow path configured with a curved configuration;

[0401] The average Reynolds number of the flow is high, which is usually determined by the fluid velocity and the hydraulic diameter of the "flow cut zone";

[0402] The local Reynolds number, through some non-limiting examples, depends on the variation of the diaphragm capsule along the flow path, protrusions on the capsule wall, and turbulence generators in the flow path. A turbulence generator is a device that transforms a laminar boundary layer into a turbulent boundary layer. A turbine may include baffles, angular metal strips, helical blades, or coiled metal strips inserted into the flow path.

[0403] A combined length of multiple tubes with a gamma ratio of approximately 150 cm / cm² to the flow cut area is a valuable example. Systems configured according to the above requirements demonstrate a yield value (the percentage of the second fluid melting during a 4-hour cooling rate) greater than 80%, an acceptable outlet temperature of the first fluid below 5°C, and an acceptable pressure drop (approximately 0.5 bar). Increasing the ratio to 200 cm / cm² (with the membrane capsule shape according to the embodiment explained above) increases the pressure drop beyond the desired limit. Reducing the ratio to below 40 cm / cm² reduces the yield value ratio during cooling to 50%. Ratios in the range of 60 to 90 cm / cm² will also result in reasonable efficiency for unit 711. Furthermore, compared to conventional "encapsulated ice" systems, the embodiments described provide a flat and stable cooling profile (behavior).

[0404] In some embodiments, such as those described in the section titled “Ice Blocks Connected in Series and / or Parallel” below, the first ice block may achieve a higher “gamma ratio” of 200 to 500 (cm / cm²) while still avoiding the problem of pressure drop.

[0405] It should be noted that the range and values ​​of the above gamma ratios are based on the results of the theory and actual experiments in the above embodiments.

[0406] Figure 8A A membrane cartridge 114 with a filling nozzle 202 of a predefined diameter is shown. Flat metal strips 801 are provided such that they are disposed within the membrane cartridge 114. The width of the metal strips is adapted to the diameter of the filling nozzle 202, allowing the metal strips to be inserted into the membrane cartridge 114. It should be noted that... Figure 8A The metal strip 801 placed in the filling nozzle 202 is shown for illustrative purposes only. The membrane box 114 ultimately used for the thermal storage unit is equipped only with the metal strip 801 located entirely inside the membrane box 114. The length of the metal strip 801 is preferably sized so that it fits well with the length of the membrane box 114. In this way, the metal strip 801 will be held in the proper position inside the membrane box 114 and will affect most of the internal volume of the membrane box 114. Selectively, multiple metal strips are used to improve the overall heat transfer efficiency of the membrane box 114. These metal strips 801 serve as heat transfer elements, which improve heat transfer inside the membrane box 114 and increase the overall heat transfer efficiency of the individual membrane box.

[0407] Figure 8B A membrane cartridge 114 with a filling nozzle 202 of a predefined diameter is shown. Helical flat metal strips 802 are provided such that they are disposed within the membrane cartridge 114. The width of the metal strips is adapted to the diameter of the filling nozzle 202, allowing the metal strips to be inserted into the membrane cartridge 114. It should be noted that... Figure 8A The metal strip 802 placed in the filling nozzle 202 is for demonstration purposes only. The spiral flat metal strip 802 provides better heat distribution inside the membrane capsule 114.

[0408] Figure 9A A rigid spacer 620 is shown, having a vertical rod 621, a horizontal rod 622, and a gap 624 between the rods. A rigid spacer 600 is disposed between two adjacent membrane cells 114. (Reference) Figure 6B and Figure 6C And corresponding explanations. For example, the rigid spacer can be with Figures 7A to 7D The embodiments described in the context are used in combination.

[0409] As the membrane chamber wall deflects toward the adjacent membrane chamber wall during cold storage (i.e., when the second fluid 122 freezes), the horizontal bar 622 maintains a free flow path in its vicinity. This allows for parallel flow 650 of the first fluid 120, which will cause the ice to melt across the entire width of the membrane chamber. The vertical bar will generate turbulence, which will improve the heat transfer coefficient between the membrane chamber wall and the flow of the first fluid 120, as indicated by the curved arrow 640.

[0410] Figure 9B A flexible spacer 600 with fins 602 is shown. The flexible spacer 600 is disposed between two adjacent membrane cells 114. (Reference) Figure 6A And corresponding explanations. Furthermore, multiple protrusions 603 are provided to generate more turbulence. For example, the flexible spacer 600 can be... Figures 7A to 7D The embodiments described in the context are used in combination.

[0411] A flexible spacer 600 equipped with vanes 602 is placed, the vanes 602 being preloaded to press against the flat walls of adjacent diaphragm cells 114. This forces the first fluid to flow through the narrow gap between the flat walls of the diaphragm cells 114. This increases the heat transfer rate between the first fluid 120 and the diaphragm cells 114. Additionally, the turbulence of the flow increases. This is due to… Figure 9B The line 900 indicates that the minimum gap (i.e., the minimum size of the gap) during the cold storage stage should be approximately 1 mm on each side.

[0412] Furthermore, the flexible spacer 600 can be configured such that the gap increases to approximately 3 to 5 millimeters on each side (due to ice melting). This will advantageously result in the fluid flow velocity of the first fluid 120 being reduced to one-quarter (1 / 4) of its maximum velocity in the pipe.

[0413] The winglets are pre-configured to expand away from the vertical plate and move toward the membrane box wall, maintaining a narrow flow gap for the first fluid 120 near the membrane box 114, and preventing performance degradation as described above.

[0414] Ice blocks connected in series and / or parallel:

[0415] To increase the cooling percentage of the storage capacity of a given membrane structure (shape and material), a possible structure is a series of ice blocks.

[0416] Downstream membrane cells, which may still be fully refrigerated or only have a small portion of their capacity for cooling, may continue to cool the heat transfer fluid to the required temperature (e.g., below 5°C), and the series arrangement of ice blocks may continue to draw cooling capacity from the upstream high-cooling membrane cells.

[0417] Another potential advantage of cascading ice blocks is the reduced number of connections to the main manifold.

[0418] This setup may have the disadvantage of producing a higher pressure drop than non-series or shorter series connections of ice blocks, especially in the first stage of cooling. Possible reasons include:

[0419] The required flow rate is determined by the required cooling rate and the temperature difference (between the inlet and outlet of the heat exchanger);

[0420] The cooling rate may be affected by the storage cooling capacity of the ice block array and the target cooling cycle. Therefore, if a large number of ice blocks are connected in series, a higher cooling rate may be required to maintain the required cooling cycle.

[0421] The pressure drop increases in a factor of three (3) because the pressure drop is proportional to the length of the flow multiplied by the square of the flow velocity.

[0422] As a non-restrictive example:

[0423] The number of ice blocks in the tandem configuration is increased from two (2) to three (3) in the tandem configuration:

[0424] (A) Exemplary reference values ​​for two ice blocks:

[0425] Capacity: 2 × 10 = 20 RTH

[0426] The expected cooling time is 4 hours.

[0427] The calculated cooling rate is 5RT.

[0428] The calculated emission flow rate (based on a temperature difference of 5°C) is 5 × 0.6 = 3 square meters per hour.

[0429] The pressure drop in the first stage of emissions is 0.3 bar (typical test result).

[0430] (3) Using the example values ​​of the three ice blocks above:

[0431] Capacity: 3 × 10 = 30 RTH

[0432] The expected cooling time is 4 hours.

[0433] The calculated cooling rate is 7.5RT.

[0434] The calculated emission flow rate (based on a 5°C temperature difference) is 7.5 × 0.6 = 4.5 square meters per hour.

[0435] The pressure drop in the first stage of emissions is 0.3 × 1.53 = 0.3 × 3.375 = 1.0125 bar.

[0436] It should be noted that the pressure drop of the three ice blocks appears to be higher than a typical expected limit.

[0437] In some embodiments, at the initial stage of the cooling cycle, by way of a non-limiting example, the temperature of the heat transfer fluid leaving the second ice block and entering the third ice block is very close to 0°C. As a result, the available temperature difference for heat transfer in the intermediate heat exchanger is higher than 5°C, and can be as high as 7 to 8°C, so the flow rate can be reduced to keep the inlet pressure under the desired limit.

[0438] In some embodiments, a bypass device, such as an on / off valve or a pressure reducing valve connected to the discharge manifold (see below), may be selectively installed. Figures 23A to 23C and Figure 24 (as described in the text), the final freezing brick can be selectively bypassed to further reduce pressure drop.

[0439] In some embodiments, the combination of the phenomena described herein and the thermal storage container may achieve the desired cooling rate while keeping the pressure drop below the desired limits.

[0440] In some embodiments, the bypass configuration is selectively applied to any number of tandem ice blocks, ranging from 3 to 5 tandem ice blocks, or even from 2 to 10 tandem ice blocks.

[0441] Now for reference Figure 23A , Figure 23A This is a simplified illustration of an ice block and bypass mechanism according to an exemplary embodiment of the present invention.

[0442] Figure 23A The display shows a minimal configuration: two ice blocks 2304 and 2316 connected in series and a valve 2310.

[0443] In some embodiments, valve 2312 may be a pressure reducing valve.

[0444] In some embodiments, valve 2312 may be a valve controlled by controller 2312 (selectively an electrical controller), a valve controlled by control software, or a valve controlled by a control computer via a network.

[0445] The inflowing fluid 2302 flows through the first ice block 2304, and continues to flow through the second ice block 2316 connected in series with the first ice block 2304, and then flows out. Figure 23A The configuration shown is 2318.

[0446] In some embodiments, valve 2312 allows heat transfer fluid to flow out, bypassing the second ice block 2316. Figure 23A The configuration shown is 2314. It should be noted that when valve 2312 allows heat transfer to flow through valve 2312, most or all of the heat transfer fluid will typically flow through valve 2312 because the resistance provided by this fluid path is less than the resistance to flow through the second ice block 2316.

[0447] Now for reference Figure 23B , Figure 23B This is a simplified illustration of an ice block and two valves according to an exemplary embodiment of the present invention.

[0448] Figure 23B A more complex configuration was shown: two ice blocks 2324 and 2338 connected in series, and two valves 2330 and 2331.

[0449] In some embodiments, the first valve 2331 may be a valve controlled by a controller 2333 (selectively an electrical controller), a valve controlled by control software, or a valve controlled by a control computer via a network. The first valve 2331 is selectively controlled to open or close.

[0450] In some embodiments, the second valve 2330 may be a pressure relief valve, since closing the first valve 2331 may generate back pressure for the flow of the heat transfer fluid.

[0451] In some embodiments, the second valve 2330 may be a valve controlled by the controller 2332, and selectively, the second valve 2330 is opened when the first valve 2331 is closed.

[0452] The inflowing fluid 2322 passes through the first ice block 2324, and continues to flow through the first valve 2331 and the second ice block 2336 connected in series with the first ice block 2324, and then flows out 2339 as shown. Figure 23B The configuration is shown. When the first valve 2331 is closed and the second valve 2330 is open, the heat transfer fluid bypasses the second ice block 2338 and then flows out of 2334 as shown. Figure 23B The configuration shown.

[0453] The above Figure 23A and Figure 23B Two possible configurations are shown that allow the heat transfer fluid to bypass the ice block. One of these configurations can be optionally placed between any upstream and downstream ice block.

[0454] For the three-block configuration, another bypass configuration is described below. Those skilled in the art can combine additional configurations based on the description provided herein.

[0455] Now for reference Figure 23C , Figure 23C This is a simplified illustration of three ice blocks and a valve according to an exemplary embodiment of the present invention.

[0456] Figure 23C The configuration of three ice blocks 2342, 2344, and 2354 connected in series is shown, along with a valve 2348.

[0457] In some embodiments, valve 2348 may be a pressure reducing valve.

[0458] In some embodiments, valve 2348 is a valve controlled by controller 2350 (selectively an electrical controller), selectively a valve controlled by control software, or a valve controlled by a control computer via a network. Valve 2350 is selectively controlled to open or close.

[0459] The incoming heat transfer fluid 2322 flows through the first ice block 2324, into the second ice block 2344 connected in series with the first ice block 2342 (2343), continues to flow into the third ice block 2354 connected in series with the second ice block 2344 (2345), and flows out through 2356. Figure 23C The configuration shown.

[0460] When valve 2348 opens, the heat transfer fluid bypasses the third ice block 2354 and flows out of 2351. Figure 23C The configuration shown.

[0461] Now for reference Figure 24 , Figure 24 This is a simplified flowchart of a method for heat exchange via a heat transfer fluid flowing through a heat storage container according to an exemplary embodiment of the present invention.

[0462] Figure 24 The methods include:

[0463] Provides a thermal energy storage system (2402), including a thermal storage container; a heat transfer fluid input; piping connecting at least some thermal storage containers in series; a flow control mechanism; and a heat transfer fluid output; and

[0464] A control signal is provided to the flow control mechanism to open the flow path of the heat transfer fluid to bypass the downstream heat storage container 2404.

[0465] Flow control of thermal energy storage systems:

[0466] When a thermal storage container freezes a large portion of its capacity, the temperature of the outflowing heat transfer fluid (HTF) may be lower than the required temperature. The energy transferred from the thermal energy storage system depends on the flow rate of the HTF leaving the system and the temperature of the HTF.

[0467] In some embodiments, when the temperature of the HTF exiting a system with multiple containers connected in series is lower than the desired temperature, one or more containers in the series can be selectively bypassed to provide an HTF close to the desired temperature.

[0468] In some embodiments, when the temperature of the HTF exiting the system is lower than the desired temperature, one or more of the following methods are used to reduce the flow rate of the HTF exiting the system:

[0469] Use a flow control valve to reduce the flow rate; and

[0470] A variable frequency drive (VFD) is used to provide operation for the variable speed pump.

[0471] For example, when the temperature of the outflowing HTF is 2°C instead of 5°C, the flow rate can be reduced by a ratio of 5 / 8 (=0.6).

[0472] Reducing the flow rate may have a beneficial effect of reducing the pressure drop in the system, with a ratio that may be 5. 2 / 8 2 (=0.4).

[0473] Now for reference Figure 25 , Figure 25 It is a collection of graphs showing the results of an experiment performed using an exemplary embodiment of the present invention.

[0474] exist Figure 25 The first line shows:

[0475] The first graphic 2501 shows the relative humidity during the experiment;

[0476] The second graph, 2502, shows the temperature during the experiment;

[0477] The third graph, 2503, shows the global solar radiation during the experiment;

[0478] The fourth graph, 2504, shows the total energy delivered during the experiment, which was 18.189 TRH (tons of refrigerant per hour).

[0479] Figure 2505 shows the ice volume equivalent to the total energy delivered, which is 687.56 kg; and

[0480] The sixth figure, 2506, shows the energy equivalent, expressed as 55041.29 kcal.

[0481] Figure 25 The bottom row shows the seventh figure 2510, which displays some parameters during the experiment.

[0482] The seventh graph, 2509, displays the X-axis of time (from 19:00 to after 22:30), the left Y-axis of temperature (degrees Celsius), and the right Y-axis of temperature (degrees Celsius). The left Y-axis is related to some lines in the seventh graph.

[0483] The seventh graphic, 2509, shows:

[0484] The first line, 2510, displays power in tons of refrigerant. The power ratio at the end of the cooling cycle is 3.554.

[0485] The second line, 2511, displays the flow rate based on the right Y-axis. At the end of the cooling cycle, the flow rate was 2.967 cubic meters per hour.

[0486] The third line, 2512, displays the temperature of the cold water flowing out. At the end of the cooling cycle, the temperature of the cold water flowing out was 5.229℃.

[0487] Line 2513 shows the temperature of the relatively hot water entering the system. At the end of the cooling cycle, the temperature of the relatively hot water entering the system was 8.852°C; and

[0488] The fifth line, 2514, displays the ambient temperature at the experimental site. The ambient temperature at the end of the cooling cycle was 28°C.

[0489] It is anticipated that many related thermal storage containers will be developed during the mature patent term of this application, and the scope of the term thermal storage container is intended to include all such new technologies in advance.

[0490] As used in this article, the term “about” refers to -60% and +200%.

[0491] The terms “including,” “contains,” “includes,” “implies,” “has,” and their variations mean “including but not limited to.”

[0492] The term "composed of" means "including and limited to".

[0493] The term "consistently of" means that a composition, method, or structure may include additional ingredients, steps, and / or portions, but only if the additional ingredients, steps, and / or portions do not substantially alter the essential and novel features of the claimed composition, method, or structure.

[0494] As used herein, unless the context clearly specifies otherwise, the singular forms “a”, “an” and “the” include plural references.

[0495] In this application, various embodiments of the invention may be presented in a range format. It should be understood that the range format is merely for convenience and brevity and should not be construed as an inflexible limitation of the scope of the invention. Therefore, it should be assumed that the range description has specifically disclosed all possible subranges and individual numerical values ​​within said ranges. For example, a description of a range such as 1 to 6 should be considered to have specifically disclosed subranges, such as 1 to 3, 1 to 4, 1 to 5, 2 to 4, 2 to 6, 3 to 6, etc., and individual numbers within said ranges, such as 1, 2, 3, 4, 5, and 6. This applies to any range width.

[0496] Whenever a range of numbers is indicated here, it means that any referenced numbers (fractions or integers) within the indicated range are included. The phrases “range between the first indicated number and the second indicated number” and “range from the first indicated number to the second indicated number” are used interchangeably herein and mean including the first and second indicated numbers and all fractions and integers between them.

[0497] It should be understood that, for clarity, certain features of the invention described in the context of a single embodiment may also be provided in combination in a single embodiment. Conversely, for brevity, various features of the invention described in the context of a single embodiment may also be provided individually or in any suitable sub-combination, or appropriately provided in any other described embodiment of the invention. Certain features described in the context of various embodiments should not be considered essential features of those embodiments unless the embodiments would not function without these elements.

[0498] Although the invention has been described in conjunction with specific embodiments thereof, many alternatives, modifications, and variations will be apparent to those skilled in the art. Therefore, the invention is intended to include all such alternatives, modifications, and variations falling within the spirit and broad scope of the appended claims.

[0499] All publications, patents, and patent applications mentioned in this specification are incorporated herein by reference in their entirety, to the same extent that each individual publication, patent, or patent application is expressly and individually indicated to be incorporated herein by reference. Furthermore, any reference or designation in this application should not be construed as an admission that such reference is prior art to the invention. Where section headings are used, they should not be construed as necessarily limiting.

[0500] Furthermore, any priority documents of this application are incorporated herein by reference in their entirety.

[0501] Reference table of icon numbers

[0502] Energy Storage (TES) System 100

[0503] Cooler 102 / 150

[0504] Fluid distribution system 104

[0505] Controller 105

[0506] Pump 106

[0507] Flow control mechanism 107

[0508] Pipeline 108 to 108T

[0509] Monitoring Component 109

[0510] Array 110

[0511] Ice bricks 112, 112B, 112C, 112D

[0512] Ice film box 114, 114C, 114Cy

[0513] First Fluid 120

[0514] Second fluid 122

[0515] Third Fluid 124

[0516] Air 126

[0517] Cooling load machine 130

[0518] Air compressor 140

[0519] Heat exchangers (HE) 142, 152, 170

[0520] Filling nozzle 202

[0521] Narrow side spacer 204

[0522] Wide side spacer 206

[0523] Rectangular casing 220

[0524] Mounting bracket 222

[0525] Inlet / outlet pipe 224

[0526] End plate 226

[0527] Support panel 227

[0528] Interconnection pipe 228

[0529] Frame 232

[0530] 250, 252

[0531] Lower part 254

[0532] Upper part 256

[0533] 260 protrusions

[0534] General flow direction 290

[0535] Bending mode 291

[0536] Cooling process 500

[0537] Subsets 520, 520A, 520B

[0538] Spacers 600, 620

[0539] 602 wing

[0540] Protrusion 603

[0541] Vertical bar 621

[0542] Horizontal bar 622

[0543] Gap 624

[0544] Flow area 630

[0545] Curved Arrow 640

[0546] 650

[0547] Pipe 712

[0548] The total cross-sectional area of ​​the pipe is 712A.

[0549] Front-end component 713A

[0550] Back-end component 713B

[0551] Entrance 714A

[0552] Export 714B

[0553] Membrane box 715

[0554] Space 716

[0555] Stacked membrane boxes 717

[0556] Flow path 718

[0557] The cross-sectional area of ​​the second fluid in free flow is 718A.

[0558] The free-flow cross-sectional area of ​​the second fluid in the frozen state is 718B.

Claims

1. A heat storage container for heat exchange in a thermal system, characterized in that: The heat storage container exchanges heat via a fluid flowing through a phase change material disposed inside the heat storage container, the heat storage container comprising: A thermal storage container shell, comprising multiple adjacent parts; One fluid inlet and one fluid outlet; and Multiple membrane capsules containing the phase change material and defining multiple channels, the multiple channels being configured to guide the flow of the fluid at different portions of the multiple portions within the housing; in: The membrane box has a flat shape; The membrane box includes a plurality of bulges, one of which forms a widened central portion of the membrane box, and the plurality of bulges form gaps between the plurality of membrane boxes. The membrane box also includes a plurality of protrusions and a plurality of flat regions located between the plurality of protrusions, the flat regions defining a flow path between the plurality of protrusions. An actual fluid flow length from the fluid inlet to the fluid outlet is greater than a direct length of the fluid flow through the entire section measured between the fluid inlet and the fluid outlet; The membrane cells located in adjacent portions of the plurality of portions have alternating orientations; some of the membrane cells in a first portion of the plurality of portions are vertically oriented, and some of the membrane cells in the portion adjacent to the first portion are horizontally oriented; the orientation is defined as the position of a heat exchange surface relative to the longitudinal axis of the heat storage container.

2. The thermal storage container as described in claim 1, characterized in that: The plurality of protrusions are configured such that the flow path of the fluid through the membrane is provided in a tortuous pattern, characterized in that the flow direction is regularly changed.

3. The thermal storage container as described in claim 1, characterized in that: The actual fluid flow length from the fluid inlet to the fluid outlet is more than twice the straight-line length of the fluid flow through the entire section measured between the fluid inlet and the fluid outlet.

4. The thermal storage container as described in claim 1, characterized in that: The thermal storage container includes one or more turbulence generators.

5. The thermal storage container as described in claim 1, characterized in that: The membrane includes a quartz nucleating agent.

6. The thermal storage container as described in claim 1, characterized in that: The heat exchange surface of the membrane is disposed within the housing and is oriented transversely to a longitudinal axis of the heat storage container.

7. The thermal storage container as described in claim 1, characterized in that: The plurality of protrusions have one or more of the following characteristics: (a) they are adapted to increase turbulence in the fluid; (b) Having a generally hemispherical shape, the generally hemispherical shape having a first radius and a second radius; wherein the second radius is at least 50% smaller than the first radius; as well as (c) The fluid flow is configured such that it is forced to bend and repeatedly change direction.

8. The thermal storage container as described in claim 1, characterized in that: The membrane boxes are placed inside the heat storage container, and at least some of the membrane boxes have a plane of their flat shape perpendicular to at least some of the other membrane boxes.

9. The thermal storage container as described in claim 1, characterized in that: The ratio between the average cross-sectional area of ​​the heat storage container along the flow path of the heat storage container and the total heat exchange area of ​​all the membrane cells in the heat storage container is between 4.5 × 10⁻⁶. -5 Up to 45×10 -5 between.

10. The thermal storage container as described in claim 1, characterized in that: The ratio between the average cross-sectional area of ​​the heat storage container along the flow path of the heat storage container and the total heat exchange area of ​​all the membrane cells in the heat storage container is between 1×10. -5 Up to 100×10 -5 between.

11. The thermal storage container as described in claim 1, characterized in that: The heat storage container has a gamma ratio greater than 150 cm / cm², wherein the gamma ratio is defined as a ratio between a linear length of the flow path of the fluid and a free-flow cross-sectional area of ​​each membrane, wherein the linear length is in centimeters and the free-flow cross-sectional area is in square centimeters.

12. The thermal storage container as described in claim 1, characterized in that: The heat storage container is rectangular; The ratio of the length to the width of the heat storage container is in the range of 4 to 50; and The ratio of the width to the height of the thermal storage container is in the range of 0.5 to 2.

13. The thermal storage container as described in claim 1, characterized in that: The heat storage container also includes a plurality of spacers inserted between the membrane boxes; The plurality of spacers ensure that the fluid flows through the thermal storage container: and When the phase change material melts, the plurality of spacers cause turbulence as the gap between the membranes increases.

14. The thermal storage container according to any one of claims 1 to 13, characterized in that: One or more upstream membrane cells are laterally positioned within the housing relative to one or more downstream membrane cells located downstream of the housing.

15. A structure, characterized in that: The structure includes the thermal storage container of claim 1, wherein the structure includes at least one thermal storage container disposed in the structure, wherein: The structure is selected from the group consisting of: a wall; A floor; and A roof.

16. A method for heat exchange via a fluid flowing through a heat storage container as claimed in claim 1, characterized in that: The method includes: The fluid is injected into the heat storage container through a fluid inlet; Heat exchange occurs between the fluid and phase change material located inside the plurality of membrane cells within the heat storage container; and The fluid is discharged from the thermal storage container via a fluid outlet.

17. The method as described in claim 16, characterized in that: The flow direction of the fluid is modified by making the fluid inside the heat storage container flow in a meandering manner.

18. The method as described in claim 16, characterized in that: The actual fluid flow length from the fluid inlet to the fluid outlet through the thermal storage container is more than twice the straight-line length of the fluid flow through the entire section measured between the fluid inlet and the fluid outlet.

19. The method as described in claim 16, characterized in that: The flow direction of the fluid is modified by changing the orientation of one or more membrane cells disposed at the thermal storage container.

20. The method as described in claim 16, characterized in that: Multiple membrane boxes are placed inside the heat storage container, and at least some of the membrane boxes have a plane of their flat shape perpendicular to at least some of the other membrane boxes.

21. The method according to any one of claims 16 to 20, characterized in that: The flow direction of the fluid is modified by alternating between turbulent and meandering flows within the thermal storage container.

22. The method as described in claim 16, characterized in that: The heat exchange surfaces of the plurality of membrane cells are disposed within the housing, and the heat exchange surfaces of the membrane cells are oriented transversely to a longitudinal axis of the heat storage container.

23. The method as described in claim 16, characterized in that: In at least 35% of the fluid flow path within the thermal storage container, the fluid flow generates a flow rate greater than 100 W / (m²). 2 The thermal conductivity coefficient of K.

24. A thermal energy storage system, characterized in that: The thermal energy storage system includes: Multiple thermal storage containers as described in claim 1; One heat transfer fluid inlet; A pipe connects at least some of the heat storage containers connected in series; A flow control mechanism; and One heat transfer fluid outlet; The flow control mechanism is configured to allow the heat transfer fluid to bypass at least one heat storage container and reach the heat transfer fluid outlet without passing through the heat storage container.

25. The thermal energy storage system as described in claim 24, characterized in that: The flow control mechanism is an electrically operated valve, and the thermal energy storage system also includes a controller for controlling the electrically operated valve.

26. The thermal energy storage system as described in claim 25, characterized in that: The controller is configured to receive control commands via a communication line.

27. The thermal energy storage system as described in claim 24, characterized in that: The flow control mechanism is a pressure reducing valve.

28. A method for heat exchange via a heat transfer fluid flowing through a heat storage container, characterized in that, The method includes: supply: A thermal energy storage system, comprising: The plurality of thermal storage containers used in a thermal system as described in claim 1, wherein the thermal storage containers exchange heat via a heat transfer fluid flowing through a phase change material disposed inside the thermal storage container; One heat transfer fluid inlet; A pipe connects at least some of the heat storage containers connected in series; A flow control mechanism; and One heat transfer fluid outlet; The flow control mechanism is configured to allow the heat transfer fluid to bypass a heat storage container and reach the heat transfer fluid outlet without passing through the heat storage container; and A control signal is provided to the flow control mechanism to open a flow path for the heat transfer fluid, allowing the heat transfer fluid to bypass more downstream heat storage containers.

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