Lightweight two-phase flow phase change regenerator

Abstract

The invention provides a lightweight two-phase flow phase change regenerator device. Comprising a regenerator shell (5), a phase change material (13) containing a coiled pipe (15), a parallel flow plate (14), a cold accumulation module composed of a cold accumulation side liquid separator (8) and a cold accumulation side liquid collector (9), and a cold supply module composed of a cold supply side liquid separator (10) and a cold supply side liquid collector (11). The space between the parallel flow plates (14) is filled with phase change materials (13) containing serpentine pipes (15), the serpentine pipes (15) are inserted into the phase change materials (13) in a penetrating mode, a modular structure with the phase change materials (13) and the parallel flow plates (14) stacked alternately is formed, the serpentine pipes (15) bear the cold storage function of the cold storage module, and flow channels in the parallel flow plates bear the heat exchange function of the cold supply module. According to the phase change regenerator, the requirement of a single-phase flow cooling scene can be met, stable operation of a two-phase flow working condition can be achieved by introducing a two-phase refrigerant into the phase change regenerator, and the response speed of a system to a dynamic load is effectively increased.

Description

Technical Field

[0001] This invention relates to the field of thermal energy storage and equipment thermal management technology, and in particular to a lightweight two-phase flow phase change cold storage device. Background Technology

[0002] Cold storage technology plays a crucial role in peak shaving and load balancing in energy systems. It not only effectively mitigates peak loads and improves energy efficiency, but also enables cross-domain transfer of cold energy across time and space, making it a core supporting technology in cold and heat energy management systems. Among various cold storage technologies, phase change (PCM) cold storage has gained widespread attention in recent years due to its significant advantages, including high energy density, excellent temperature stability during phase change, and compact system architecture. PCM absorbs or releases large amounts of latent heat during phase transitions, achieving efficient energy storage and controllable release. It has already been widely applied in building energy conservation, cold chain logistics, industrial refrigeration, and thermal management of electronic devices.

[0003] Currently, many applications, such as directed energy weapons, electromagnetic guns, phased array radar T / R modules, drone power batteries, fast-charging batteries for new energy vehicles, industrial laser processing equipment, and high-density servers in data centers, exhibit unique heating characteristics characterized by "high instantaneous power density, short heating duration, and long intervals." For example, directed energy weapons experience concentrated heat of 10kW-100kW within 1-200 seconds during combat, with intervals ranging from 10 minutes to several hours; fast-charging batteries for new energy vehicles generate 5kW-20kW of heat during 25-35 seconds of fast charging, with intervals exceeding 30 minutes; and industrial laser processing equipment achieves heat flux densities of 10W / cm²-30W / cm² during 10-60 seconds of processing, with intervals of 5-20 minutes. The heat dissipation effect in these scenarios directly determines the performance and lifespan of the equipment, which places stringent demands on phase change cold storage technology to provide "high-power cooling during the heating phase, efficient cold storage during the intermittent phase, and lightweight design." However, existing phase change cold storage solutions generally have limitations in scenario adaptability—either the heat exchange power is too low to match the instantaneous high-power demand, or the size and weight are too large to fit into compact installation spaces. Furthermore, there is a lack of unified adaptation design for the common needs of different scenarios, which makes it impossible to reuse the same technology across scenarios, resulting in high R&D and application costs.

[0004] As the core functional carrier of phase change cold storage technology, the phase change accumulator (PCM) comprises a PCM (Polymerized Module) and a heat exchange structure. Its structural configuration has a decisive impact on the energy storage density, charging / discharging rate, and operational stability of the cold storage system. Currently, typical structural forms in engineering applications include shell-and-tube, plate, finned, and parallel-flow heat exchangers. Among these, the serpentine tube accumulator is characterized by its compact structure, high cold storage density, and simple manufacturing process. Its fabrication typically only requires bending the tubes and then pressing them with the PCM. However, this structure is limited by the finned heat exchange area, where the heat transfer between the tube and shell sides is limited to the tube walls, resulting in low heat exchange efficiency and making it unsuitable for the rapid cooling demands of instantaneous high-power heating scenarios. In contrast, the parallel-flow structure, with its high compactness, large heat exchange area per unit volume, and suitability for miniaturized and high-density applications, has become increasingly popular. This has become a key research direction for improving cold storage efficiency. Its typical design involves distributing the heat transfer fluid through a manifold to parallel microchannels within several flat tubes. The flat tube walls serve as a heat transfer interface to achieve efficient heat exchange with the surrounding PCM. By increasing the contact area and optimizing the flow field distribution through a multi-channel parallel design, the phase change heat transfer rate is significantly improved. However, existing parallel flow cold accumulators generally suffer from the design bias of "overemphasizing a single performance"—using complex fins to pursue the cold storage rate, which leads to the compression of the PCM filling space and a reduction in energy storage density, making it difficult to meet the needs of long-term intermittent cold storage. At the same time, it adds extra weight and volume to the device, failing to meet the lightweight requirements of various scenarios.

[0005] Existing technologies, whether serpentine tube accumulators or parallel flow accumulators, cannot simultaneously meet the high energy storage density, high cooling power, and rapid response requirements of the above-mentioned scenarios. The existing traditional structures have inherent contradictions in their design, such as "difficulty in balancing cold storage capacity and cooling rate, inability to coordinate lightweight design with efficient heat exchange, and insufficient adaptability to multiple scenarios".

[0006] Currently, existing technologies lack solutions that combine phase change cold storage devices with two-phase flow refrigerant technology, especially lacking a unified adaptation design for "instantaneous high-power intermittent scenarios". Traditional solutions either can only be adapted to single-phase flow working fluids, resulting in limited heat exchange efficiency, or although they attempt to combine two-phase flow, they have not been optimized for the common characteristics of "high-power cooling during the heating phase and low-power cold storage during the intermittent phase", thus failing to fully leverage the latent heat exchange advantages of two-phase flow working fluids. Summary of the Invention

[0007] Embodiments of the present invention provide a lightweight two-phase flow phase change accumulator to effectively improve the cold storage and release efficiency of the phase change accumulator.

[0008] To achieve the above objectives, the present invention adopts the following technical solution.

[0009] A lightweight two-phase flow phase change accumulator device includes: an accumulator shell (5) installed on the outside of the main structure of the two-phase flow phase change accumulator, a phase change material (13) containing a serpentine tube (15), a parallel flow plate (14) including a parallel flow plate outlet end (7) and a parallel flow plate inlet end (12) connected, a accumulator module composed of a accumulator side distributor (8) and a accumulator side collector (9), and a cooling module composed of a cooling side distributor (10) and a cooling side collector (11).

[0010] The parallel flow plates (14) are filled with phase change material (13) containing serpentine tubes (15). The serpentine tubes (15) are inserted into the phase change material (13), forming a modular structure in which the phase change material (13) and the parallel flow plates (14) are stacked alternately. The serpentine tubes (15) undertake the cold storage function of the cold storage module, and the flow channels in the parallel flow plates undertake the heat exchange function of the cooling module. The cooling capacity and cold storage / discharge power of the two-phase flow phase change cold storage device can be adjusted by adjusting the number of phase change materials (13) and parallel flow plates (14).

[0011] Preferably, the inlet end of the serpentine tube (15) is equipped with the cold storage side distributor (8) and the cold storage fluid inlet pipe (1), the outlet end of the serpentine tube (15) is equipped with the cold storage side collector (9) and the cold storage fluid outlet pipe (2), the inlet end (12) of the parallel flow plate is equipped with the cold supply side distributor (10) and the cold release fluid inlet pipe (3), and the outlet end (7) of the parallel flow plate is equipped with the cold supply side collector (11) and the cold release fluid outlet pipe (4).

[0012] The parallel flow plate inlet end (12) evenly distributes the cooling fluid to each channel, and the parallel flow plate outlet end (7) collects and recovers the cooling fluid; the cooling side distributor (10) evenly distributes the cooling fluid entering through the cooling fluid inlet pipe (3) to each parallel flow plate, and then the cooling side cold storage side collector (11) collects the fluid and flows out from the cooling fluid outlet pipe (4).

[0013] Preferably, the cold storage module has a built-in phase change material (13), and a serpentine tube (15) is embedded in the center of the phase change material (13) for transporting heat exchange fluid; the diameter and spacing of the serpentine tube (15) are adjusted according to the required heat exchange area; the inlet end of the serpentine tube (15) distributes the cold storage fluid flowing in from the cold storage fluid inlet pipe (1) through the cold storage side distributor (8), and distributes the cold storage fluid evenly to each serpentine tube (15); the outlet end of the serpentine tube (15) transmits the cold storage fluid recovered by the straight cylinder cold storage side collector (9) to the cold storage fluid outlet pipe (2), and then the cold storage fluid is discharged by the cold storage fluid outlet pipe (2).

[0014] Preferably, a certain number of parallel flow channels are arranged on the parallel flow plate (14). The diameter and number of the parallel flow channels are adjusted according to the required heat exchange area. Each parallel flow channel is a rectangular flow channel or a rounded rectangular flow channel. The parallel flow channels are distributed at equal intervals or at non-equal intervals as needed. The length and width dimensions of each parallel flow channel are selected according to the heat release power requirements.

[0015] Preferably, the phase change cold storage device uses a modular design to adjust the cold storage capacity, cold storage power, and cold release power, with a total cold storage capacity... The number of phase change material plates (13) Compared with the cold storage capacity of a single plate The product is determined as follows:

[0016] n

[0017] Mass of phase change material filling within a single plate and phase transition enthalpy Decide;

[0018] Total cold storage capacity The number of cold storage modules Power of a single cold storage module The product is determined;

[0019]

[0020] The heat transfer area and overall heat transfer coefficient of the serpentine tube and working fluid temperature difference Decide;

[0021] Total cooling power The number of parallel flow plates 14 Power of a single parallel flow plate The product is determined by the power of a single parallel flow plate. Heat exchange area of ​​the flow channel Overall heat transfer coefficient and working fluid temperature difference The product is determined;

[0022]

[0023] .

[0024] Preferably, the total heat exchange area of ​​the phase change cold storage device is... The heat transfer area of ​​a single circular flow channel is determined by both the heat transfer area of ​​a single flow channel and the number of flow channels. Heat transfer area of ​​single rectangular and rounded rectangular flow channels = ,in Inner diameter , For cross-sectional dimensions, The length of the flow channel;

[0025] By adjusting , , The total heat exchange area of ​​the phase change cold storage is adjusted by the value of [value]. This allows for the adjustment of the heat exchange power of the phase change accumulator.

[0026] Preferably, the liquid distribution holes in the parallel flow plate outlet end (7) and the parallel flow plate inlet end (12) are designed in a stepped manner from the inlet end to the outlet end, and the maximum orifice diameter of the parallel flow plate outlet end (7) and the parallel flow plate inlet end (12) does not exceed the maximum orifice diameter of the parallel flow channel, and the minimum orifice diameter is not less than 1 / 2 of the minimum orifice diameter of the parallel flow channel.

[0027] Preferably, the materials of the parallel flow plate outlet end (7) and the parallel flow plate inlet end (12) are the same as or compatible with the material of the parallel flow plate (14), and the parallel flow plate outlet end (7), the parallel flow plate inlet end (12) and the parallel flow plate (14) are connected by welding, brazing or mechanical sealing.

[0028] Preferably, the working fluid in the serpentine tube (15) and the parallel flow plate (14) is selected from one or more of the single-phase flow coolants that utilize sensible heat to carry cold energy; or, one or more of the two-phase flow refrigerants that utilize latent heat of phase change are selected.

[0029] Preferably, the phase change material is selected from one or more composite systems of water-expanded graphite composites, various paraffin-expanded graphite composites, fatty acid-expanded graphite composites, and polyol-expanded graphite composites; the phase change temperature range of the phase change material is -10℃ to 25℃, the phase change enthalpy is not less than 200kJ / kg, and the thermal conductivity is not less than 2W / (m・K).

[0030] Preferably, fasteners (6) are installed on the cold storage housing (5), and the material of the cold storage housing is selected from carbon steel, stainless steel, aluminum alloy, copper and titanium alloy, and the thickness of the cold storage housing is set according to the pressure requirements.

[0031] As can be seen from the technical solutions provided by the embodiments of the present invention above, the present invention provides a novel two-phase flow phase change accumulator that combines the advantages of a serpentine tube heat exchanger and a parallel flow accumulator, in order to solve the technical problem that existing accumulators are unable to simultaneously achieve high energy storage density, high cooling power and fast response. It is particularly suitable for the heat dissipation needs of heat-generating bodies with instantaneous high power intermittent heating characteristics, such as directed energy weapons, electromagnetic guns, phased array radars, UAV power batteries, fast charging batteries for new energy vehicles, industrial laser processing equipment, and high-density servers in data centers.

[0032] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and will become apparent from the description or may be learned by practice of the invention. Attached Figure Description

[0033] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0034] Figure 1 A structural diagram of a lightweight two-phase flow phase change regenerator provided in an embodiment of the present invention;

[0035] Figure 2 This is a partial schematic diagram of a phase change cold storage structure provided in an embodiment of the present invention;

[0036] Figure 3 A schematic diagram showing the curves of the single-phase coolant outlet temperature and cold storage power on the cold storage side of a phase change cold accumulator under certain conditions, provided for an embodiment of the present invention.

[0037] Figure 4 This is a schematic diagram showing the changes in the outlet temperature of the single-phase hot fluid on the cooling side and the cooling power over time under certain conditions for a phase change cold storage unit provided in an embodiment of the present invention.

[0038] Figure 5 A schematic diagram showing the changes in the outlet temperature of the two-phase coolant on the storage side and the storage power over time under certain conditions for a phase change accumulator provided in an embodiment of the present invention.

[0039] Figure 6 This is a schematic diagram showing the changes in outlet temperature and cooling power of the two-phase hot fluid on the cooling side of a phase change cold storage unit under certain conditions, as provided in an embodiment of the present invention.

[0040] 1. Cold storage fluid inlet pipe; 2. Cold storage fluid outlet pipe; 3. Cold release fluid inlet pipe; 4. Cold release fluid outlet pipe; 5. Cold accumulator shell; 6. Cold accumulator fixing components; 7. Parallel flow plate outlet end; 8. Cold storage side distributor; 9. Cold storage side collector; 10. Cold supply side distributor; 11. Cold supply side and cold storage side collector; 12. Parallel flow plate inlet end; 13. Phase change material; 14. Parallel flow plate; 15. Serpentine tube. Detailed Implementation

[0041] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0042] Those skilled in the art will understand that, unless specifically stated otherwise, the singular forms “a,” “an,” “the,” and “the” used herein may also include the plural forms. It should be further understood that the term “comprising” as used in this specification means the presence of the stated features, integers, steps, operations, elements, and / or components, but does not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof. It should be understood that when we say an element is “connected” or “coupled” to another element, it can be directly connected or coupled to the other element, or there may be intermediate elements. Furthermore, “connected” or “coupled” as used herein can include wireless connections or couplings. The term “and / or” as used herein includes any and all combinations of one or more of the associated listed items.

[0043] It will be understood by those skilled in the art that, unless otherwise defined, all terms used herein (including technical and scientific terms) have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. It should also be understood that terms such as those defined in general dictionaries should be understood to have the same meaning as in the context of the prior art, and should not be interpreted in an idealized or overly formal sense unless defined as herein.

[0044] To facilitate understanding of the embodiments of the present invention, the following will provide further explanation and description with reference to the accompanying drawings and several specific embodiments. These embodiments do not constitute a limitation on the embodiments of the present invention.

[0045] This invention combines the advantages of serpentine tube accumulators and parallel flow accumulators to develop a phase change accumulator structure that is compact, has low flow resistance, excellent heat transfer efficiency, high energy storage density, and can adapt to various instantaneous high power demands.

[0046] The present invention provides a lightweight two-phase flow phase change cold storage device with high energy storage density and high power, as shown in the following embodiment: Figure 1 As shown, it includes: a cold storage fluid inlet pipe 1, a cold storage fluid outlet pipe 2, a cold release fluid inlet pipe 3, a cold release fluid outlet pipe 4, a cold storage tank shell 5, fasteners 6, a parallel flow plate outlet end 7, a cold storage side distributor 8, a cold storage side collector 9, a cold supply side distributor 10, a cold supply side collector 11, a parallel flow plate inlet end 12, a phase change material 13, a parallel flow plate 14, and a serpentine tube 15.

[0047] The aforementioned phase change accumulator includes an accumulator shell 5 installed on the outside of the main structure of the accumulator, a phase change material 13 containing a serpentine tube 15, a parallel flow plate 14 including a parallel flow plate outlet end 7 and a parallel flow plate inlet end 12 connected together, a accumulator module composed of a accumulator side distributor 8 and a accumulator side collector 9, a cooling module composed of a cooling side distributor 10 and a cooling side collector 11, and accumulator fasteners installed on the outside of the main structure of the accumulator.

[0048] The space between the parallel flow plates 14 is filled with phase change material 13, and serpentine tubes 15 are inserted in the phase change material 13; the cold storage side distributor 8 and the cold storage side collector 9 are connected by a flange, and the cold supply side distributor 10 and the cold storage side collector 11 are connected by a flange.

[0049] Preferably, the main structure of the cold storage unit is composed of parallel flow plates, the ends of the parallel flow plates, and a cold storage unit shell. The space between the two parallel flow plates is filled with phase change material containing serpentine tubes, forming a modular structure with alternating stacks of phase change material and parallel flow plates. Specifically, one layer of phase change material 13 and one layer of parallel flow plates 14 are arranged alternately. The serpentine tubes primarily perform the cold storage function, while the flow channels in the parallel flow plates primarily perform the heat exchange function on the cooling side. By adjusting the quantity of phase change material 13 and parallel flow plates 14, the cold storage capacity and cold storage / discharge power of the entire phase change cold storage unit can be flexibly adjusted.

[0050] The phase change cold storage device of this invention achieves precise adjustment of cold storage capacity and cold storage / discharge power through modular design. Total cold storage capacity. The number of phase change material plates 13 Compared with the cold storage capacity of a single plate The product is determined as follows:

[0051] n

[0052] Mass of phase change material filling within a single plate and phase transition enthalpy Decide.

[0053] Total cold storage capacity The number of cold storage modules (and phase change material plates) Consistent quantity Power of a single cold storage module The product is determined.

[0054]

[0055] The heat transfer area and overall heat transfer coefficient of the serpentine tube and working fluid temperature difference Decide.

[0056] Total cooling power The number of parallel flow plates 14 Power of a single parallel flow plate The product is determined by the power of a single parallel flow plate. Heat exchange area of ​​the flow channel Overall heat transfer coefficient and working fluid temperature difference The product is determined. And , , Typically, maintaining consistency in linkage allows for linear adjustment of various performance aspects based on the aforementioned relationships simply by adding or removing modules, without altering the core structure of a single module, thus quickly adapting to different scenario requirements.

[0057]

[0058]

[0059] The inlet end of the serpentine tube 15 is equipped with a cold storage side distributor 8 and a cold storage fluid inlet pipe 1, and the outlet end of the serpentine tube 15 is equipped with a cold storage side collector 9 and a cold storage fluid outlet pipe 2. The inlet end 12 of the parallel flow plate is equipped with a cold supply side distributor 10 and a cold release fluid inlet pipe 3, and the outlet end 7 of the parallel flow plate is equipped with a cold supply side collector 11 and a cold release fluid outlet pipe 4.

[0060] Fasteners 6 are installed on the cold storage housing 5. These fasteners 6 are used to ensure the stability of the overall structure of the phase change cold storage and to fix the phase change cold storage in a preset position.

[0061] The phase change energy storage module of the phase change energy storage unit incorporates a phase change material 13, which is a composite material made of expanded graphite and one of the following: water, tetradecane, etc. It possesses high thermal conductivity and high enthalpy characteristics, enabling rapid energy storage and release. A serpentine tube 15 is embedded in the center of the phase change material 13 for transporting the heat exchange fluid. The serpentine tube 15 is formed by bending a straight tube of a specific material. The diameter, number of straight tubes, and number of bends of the serpentine tube 15 can be set according to actual needs. Furthermore, the diameter and spacing (i.e., the number of straight tubes) of the serpentine tube 15 can be adjusted according to the required heat exchange area to adapt to different energy storage requirements. The inlet end of the serpentine tube 15 distributes the cold storage fluid flowing in from the cold storage fluid inlet pipe 1 through the brass cold storage side distributor 8, so that the cold storage fluid is evenly distributed to each serpentine tube 15; the outlet end of the serpentine tube 15 transfers the cold storage fluid recovered through the straight cylinder cold storage side collector 9 to the cold storage fluid outlet pipe 2, and then the cold storage fluid is discharged by the cold storage fluid outlet pipe 2.

[0062] The cooling module of the cold regenerator is centered around a parallel flow plate 14. A certain number of parallel flow channels are arranged on the parallel flow plate 14. The diameter and number of these channels can be adjusted according to the required heat exchange area to adapt to different cooling needs. Each channel is either rectangular or rounded-corner rectangular. The length and width dimensions of each parallel flow channel can be selected according to the heat dissipation power requirements. The parallel flow channels are evenly spaced or distributed with non-uniform spacing as needed to optimize flow field uniformity. The dimensions of each channel within the plate can be the same or different to adapt to different scenario requirements.

[0063] The parallel flow path parameters of the cold storage module can be adjusted using the following logic:

[0064] Total cooling power The number of parallel flow plates 14 Power of a single parallel flow plate The product is determined by the power of a single parallel flow plate. Heat exchange area of ​​the flow channel Overall heat transfer coefficient and working fluid temperature difference The product is determined;

[0065]

[0066] Total heat exchange area The heat transfer area of ​​a single flow channel and the number of flow channels are both determined by the flow channel itself; circular flow channels... Rectangular / rounded rectangular flow channels = ,in Inner diameter , For cross-sectional dimensions, This refers to the flow channel length. To increase cooling power, the flow channel diameter can be increased (e.g., by widening the channel opening). or , This can be achieved by increasing the number of flow channels. In practice, the optimal combination of "large diameter, few channels" or "small diameter, many channels" can be selected based on flow resistance and installation space. The length and width dimensions of the flow channels are adjusted according to the heat dissipation power requirement: when increased power is needed, the flow channel length can be increased. Alternatively, the cross-sectional dimensions can be adjusted; if power reduction or flow resistance optimization is required, the adjustments can be made in the opposite direction. Simultaneously, the dimensions of each flow channel can be set to be the same or differentiated (e.g., fine-tuning the dimensions of edge flow channels) to ensure flow field uniformity and stable heat exchange efficiency.

[0067] The parallel flow plate inlet end 12 evenly distributes the cooling fluid to each channel, and the parallel flow plate outlet end 7 collects and recovers the cooling fluid; the cooling side distributor 10 evenly distributes the cooling fluid entering through the cooling fluid inlet pipe 3 to each parallel flow plate, and then the cooling side cold storage side collector 11 collects the fluid and flows out from the cooling fluid outlet pipe 4.

[0068] By increasing or decreasing the number of phase change material plates and parallel flow plates, the energy storage density and cooling power of the device can be adjusted to meet the requirements of different applications. Figure 1 The cold storage accumulator shown has a cooling capacity greater than 100kW and is composed of a large number of alternating cold storage / cooling modules. In contrast, the cold storage accumulators in embodiments two and three have a cooling capacity of 30.8kW. This difference in cooling capacity and cold storage capacity does not require significant design changes or reprocessing of the cold storage / cooling modules; only the number of phase change material plates and parallel flow plates needs to be adjusted. Aside from the module design within the cold storage accumulator or the structural innovation of this cold storage / cooling module stacking, this innovative modular adjustment method is also the core innovation that this invention needs to protect.

[0069] The serpentine tubes interspersed in the phase change material are made of one or more of the following materials: titanium alloy (such as TC4, TC6), aluminum alloy (such as 6061, 5052), copper (such as T2, T3), and copper alloy (such as H62, H65). The inner diameter of the serpentine tubes can be designed according to specific cold storage requirements. Various bending or arrangement methods of the serpentine tubes within the plate are all within the protection scope of this invention. The inlet end of the serpentine tubes is connected to the cold storage side distributor, and the outlet end is connected to the cold storage side collector.

[0070] The parallel flow plate outlet end 7 and the parallel flow plate inlet end 12 respectively undertake the functions of liquid separation and liquid collection of the parallel flow working fluid. In order to ensure the uniformity of the working fluid flow in each channel of the parallel flow plate and to ensure that the fluid flow path length of each channel is consistent, the liquid separation holes in the parallel flow plate outlet end 7 and the parallel flow plate inlet end 12 are designed in a stepped manner from the inlet end to the end, with the maximum hole diameter not exceeding the maximum diameter of the parallel flow plate channel and the minimum hole diameter not less than 1 / 2 of the minimum diameter of the channel.

[0071] Preferably, the material of the parallel flow plate is selected from stainless steel (such as 304, 316, 316L), aluminum alloy (such as 6063, 7075), copper (such as T2, T3), and titanium alloy (such as TC4); the material of the end of the parallel flow plate is the same as or a compatible heat-conducting metal material as the parallel flow plate material, and the two are connected by welding, brazing or mechanical sealing, or even by an integrated extrusion method to form the main heat-conducting structure of the cold accumulator.

[0072] Preferably, the working fluid in the serpentine tube and the parallel flow pipe can be one or a mixture of several single-phase flow coolants that utilize sensible heat to carry cold energy, such as ethylene glycol aqueous solution, water, propylene glycol solution, brine, methanol aqueous solution, and ethanol aqueous solution; or one or a mixture of several two-phase flow refrigerants that utilize latent heat of phase change, such as R22, R134A, R32, R410A, R507, R1234yf, and R1234ze.

[0073] Preferably, the phase change material is selected from one or more composite systems of water-expanded graphite composite material, various paraffin-expanded graphite composite material, fatty acid (such as stearic acid, palmitic acid)-expanded graphite composite material, and polyol (such as pentaerythritol)-expanded graphite composite material; the phase change temperature range of the phase change material is -10℃ to 25℃, the phase change enthalpy is not less than 200kJ / kg, and the thermal conductivity is not less than 2W / (m・K).

[0074] Preferably, a brass-coated cold storage side distributor 8 is used to distribute the working fluid on the cold storage side, and a straight-cylinder cooling side distributor 10 is used to distribute the working fluid on the parallel flow plate; both the cold storage side and the cooling side collectors are straight-cylinder distributors; the connections between each distributor and collector and the delivery pipe and the collection pipe are made by standard flanges.

[0075] Preferably, the material of the cold storage tank shell is selected from one of carbon steel (such as Q235, Q345), stainless steel (such as 304, 316), aluminum alloy (such as 5052, 6061), copper (such as T2), and titanium alloy (such as TC4); the thickness of the shell is set according to the pressure requirements to adapt to the pressure level requirements under different application scenarios.

[0076] Example 1:

[0077] In this embodiment of the invention, the PCM in the phase change regenerator is a water-expanded graphite composite phase change material with a phase change temperature of 0°C, a phase change enthalpy of 300 kJ / kg, and a thermal conductivity of 7.5 W / m·K. The heat exchange area of ​​the pipes is designed according to the heat exchange requirements of the regenerator end, and the serpentine tubes inside the PCM plate are designed with a specific structure; the thickness of the PCM plate is designed according to the energy storage requirements. The cooling side is a parallel flow plate, and the number of flow channels, the diameter of the flow channels, and the length of the flow channels are all designed according to the heat exchange requirements of the device. In this embodiment, the device is composed of 10 PCM plates stacked with 10 parallel flow plates, and the inlet and outlet are designed with a liquid distributor / regenerator-side liquid collector.

[0078] In the cold storage experiment, the heat exchange fluid used was a 50% (v / v) ethylene glycol single-phase coolant. The inlet temperature of the ethylene glycol coolant was -8℃, and the mass flow rate of the ethylene glycol coolant was 750 kg / h. The cold accumulator was initially stationary at room temperature for 48 hours, during which the PCM was completely liquefied. The initial temperature was room temperature. The cold storage performance of the cold accumulator was then tested by introducing the coolant under the above conditions at room temperature.

[0079] Figure 3 The test results of the cold storage accumulator's outlet temperature and cold storage power under the above conditions are presented. Observing the curve of the cold storage side outlet temperature changing with time, it is found that the cold storage side outlet temperature can approach the -8℃ inlet temperature of the coolant after 20 minutes, indicating that it can almost complete cold storage within 20 minutes. Observing its cold storage power curve, it is found that its average power over 20 minutes is 3.21kW, and the cold storage capacity of the cold storage accumulator is calculated to be 3.8MJ, which belongs to a high energy density cold storage device. This figure can demonstrate the characteristics of short cold storage time and high energy density of the device of the present invention.

[0080] Example 2:

[0081] The cold storage device design is consistent with that of Embodiment 1 above, meaning that Embodiment 2 and Embodiment 1 use the same cold storage device. The cold storage devices that can be designed according to this invention include, but are not limited to, cold storage devices with this energy storage density and cooling power.

[0082] In the cooling experiment, a 50% (v / v) ethylene glycol single-phase solution was used as the heat exchange fluid. The inlet temperature of the ethylene glycol coolant was 22℃, and the mass flow rate of the ethylene glycol coolant was 1500 kg / h. The regenerator was initially frozen at -4℃ for 48 hours, during which the PCM completely solidified, resulting in an initial outlet temperature of -4℃. The heat exchange fluid under the above conditions was introduced, and the outlet temperature was continuously monitored for 90 seconds to test the cooling performance of the regenerator.

[0083] Figure 4The curves showing the changes in outlet temperature and cooling power over time under the cooling mode of the cold storage device under the above conditions are presented. Under these conditions, the average cooling power of the cold storage device can reach 30.8kW within 90s. This power of the cold storage device is sufficient to cope with high-power cooling application scenarios. Moreover, the measured weight of the cold storage device (including interface, fasteners, insulation layer, and other structures) is only 38kg, which is a lightweight cooling equipment with high energy storage density per unit mass. It can be widely used in vehicle-mounted cooling systems that require high energy storage density and high cooling power.

[0084] Example 3

[0085] The cold storage device design is consistent with that of Embodiment 1 above, that is, Embodiment 3 and Embodiment 1 use the same cold storage device. The cold storage devices that can be designed according to the present invention include, but are not limited to, cold storage devices with this energy storage density and cooling power.

[0086] In the cold storage experiment, the heat exchange fluid used was two-phase refrigerant R22, with an R22 inlet temperature of -10℃ and a mass flow rate of 500 kg / h. The cold accumulator was initially stationary at room temperature for 48 hours, during which the PCM was completely liquefied. The initial temperature was room temperature. The cold storage performance of the cold accumulator was then tested by introducing the refrigerant under the above conditions at room temperature.

[0087] Figure 6 The test results of the cold storage accumulator's outlet temperature and cold storage power under the above conditions are presented. Observing the curve of the cold storage side outlet temperature changing with time, it is found that the cold storage side outlet temperature can approach the -10℃ inlet temperature of the coolant after 20 minutes, indicating that it can almost complete cold storage within 20 minutes. Observing its cold storage power curve, it is found that its average power over 20 minutes is 3.3kW, and the cold storage capacity of the cold storage accumulator is calculated to be 3.96MJ, which belongs to a high energy density cold storage device. This figure can demonstrate the characteristics of short cold storage time and high energy density of the device of the present invention.

[0088] Example 4

[0089] The cold storage device design is consistent with that of Embodiment 1 above, that is, Embodiment 4 and Embodiment 1 use the same cold storage device. The cold storage devices that can be designed according to the present invention include, but are not limited to, cold storage devices with this energy storage density and cooling power.

[0090] In the cooling experiment, R134A refrigerant was used as the heat exchange fluid, with an inlet temperature of 24℃ and a ethylene glycol coolant mass flow rate of 800 kg / h. The refrigerant was initially frozen at -8℃ for 48 hours, during which the PCM completely solidified. The heat exchange fluid under the above conditions was introduced, and the outlet temperature was continuously monitored for 90 seconds to test the refrigerant's cooling performance. By monitoring the inlet and outlet temperature difference and flow rate, the average cooling power supplied by the refrigerant within the above 90 seconds was found to be 37.5 kW. The inlet and outlet temperature curves and the cooling power curve are as follows. Figure 6As shown. This power of the cold storage device is sufficient to meet the application scenarios requiring high-power cooling. In fact, the measured weight of the cold storage device (including the interface, fasteners, insulation layer and other structures) is only 38kg, which is a lightweight cooling equipment with high energy storage density per unit mass. It can be widely used in vehicle cooling systems that require high energy storage density and high cooling power.

[0091] In summary, the phase change refrigerant designed in this embodiment of the invention can not only meet the cooling requirements of single-phase flow scenarios, but also achieve stable operation in two-phase flow conditions by introducing two-phase refrigerant internally. Compared with single-phase flow, the two-phase flow mode can significantly enhance short-term heat exchange efficiency by utilizing a large amount of latent heat exchange during the phase change process of the working fluid. It performs particularly well in short-term rapid heat exchange scenarios with instantaneous high power heating in various scenarios, effectively improving the system's response speed to dynamic loads and providing a better solution for the cold storage-release process in high power density scenarios.

[0092] This invention innovatively integrates a serpentine tube heat exchanger with a parallel flow plate heat exchanger, specifically addressing the problem of instantaneous high-power intermittent heating in laser weapon chips, shipborne electromagnetic guns, and phased array radar T / R components (concentrated heating of 10kW-500kW within 1-200 seconds, with an interval of 10 minutes to several hours): On the cold storage side, a combination of "serpentine tube + high thermal conductivity composite phase change material" is used. Taking advantage of the serpentine tube's small space occupation and light weight (weight per unit power ≤ 1.2kg / kW), combined with flexibly adjustable tube diameter and spacing, the device achieves lightweight design while ensuring high energy storage density, adapting to the strict space and weight constraints of vehicle-mounted, airborne, and shipborne equipment; On the cooling side, a fully parallel microchannel parallel flow structure is adopted, combined with the phase change latent heat exchange mechanism of two-phase flow refrigerant, which can quickly remove heat in instantaneous scenarios such as weapon launch and high-intensity radar operation, avoiding overheating failure of core components. By using an alternating stacking layout of "cold storage and cooling modules", the volumetric power density is further optimized while taking into account vibration resistance. This makes it suitable for mobile combat scenarios such as off-road and navigation, effectively overcoming the inherent defects of traditional phase change cold storage devices, such as insufficient cooling power, low cold energy release efficiency, and difficulty in achieving lightweight design.

[0093] This invention achieves an innovative breakthrough in working fluid adaptability: the serpentine tube on the cold storage side can use single-phase flow working fluids such as water and ethylene glycol to achieve stable cold storage through sensible heat transfer, and can also be adapted to two-phase flow to improve cold storage efficiency by utilizing the latent heat of phase change; the fully parallel microchannel structure working fluid of the parallel flow channel on the cooling side supports single-phase flow working fluids such as water and ethylene glycol to achieve efficient convective heat transfer through optimized flow channels, and can also enhance short-term heat transfer by combining the latent heat exchange mechanism of phase change of two-phase flow working fluids. Thus, through the bidirectional compatibility of single-phase and two-phase flow working fluids on the cold storage side and the cooling side, it can flexibly adapt to the cold storage duration and rapid cooling demand of different scenarios, breaking through the limitations of traditional structural working fluid selection.

[0094] This invention constructs a standardized and modular development system that highly meets the diverse and differentiated needs of various scenarios: Only the "PCM cold storage module with serpentine tubes" and the "parallel flow cooling module" need to be prefabricated. By increasing or decreasing the stacking quantity of these two types of modules (e.g., 5 modules for 10kW-20kW fast-charging batteries for new energy vehicles / drone power batteries, 10 modules for 30kW phased array radar / industrial laser equipment, 30 modules for 100kW directed energy weapons / electromagnetic guns), and by processing corresponding material shells and liquid distribution / collection devices, the cold storage capacity and cold storage / discharge power (covering a range of 10kW-500kW cold discharge power) can be adjusted as needed. This design eliminates the need to redevelop core modules and the overall structure, shortening the development cycle of high-power equipment heat dissipation systems and reducing the development costs of products with different power specifications. Simultaneously, while ensuring structural compactness and lightweight design, it ensures that all specifications of products maintain high energy storage density and efficient heat exchange characteristics in various application environments, significantly improving adaptability to multiple scenarios and the potential for large-scale application.

[0095] Those skilled in the art will understand that the accompanying drawings are merely schematic diagrams of one embodiment, and the modules or processes shown in the drawings are not necessarily essential for implementing the present invention.

[0096] The various embodiments in this specification are described in a progressive manner. Similar or identical parts between embodiments can be referred to mutually. Each embodiment focuses on describing the differences from other embodiments. In particular, for apparatus or system embodiments, since they are basically similar to method embodiments, the description is relatively simple; relevant parts can be referred to the descriptions in the method embodiments. The apparatus and system embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the modules can be selected to achieve the purpose of this embodiment according to actual needs. Those skilled in the art can understand and implement this without creative effort.

[0097] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A lightweight two-phase flow phase change cold storage device, characterized in that, include: The accumulator shell (5) installed on the outside of the main structure of the two-phase flow phase change accumulator, the phase change material (13) containing the serpentine tube (15), the parallel flow plate (14) connected by the parallel flow plate outlet end (7) and the parallel flow plate inlet end (12), the accumulator module composed of the accumulator side distributor (8) and the accumulator side collector (9), and the cooling module composed of the cooling side distributor (10) and the cooling side collector (11); The parallel flow plates (14) are filled with phase change material (13) containing serpentine tubes (15). The serpentine tubes (15) are inserted into the phase change material (13) to form a modular structure in which the phase change material (13) and the parallel flow plates (14) are stacked alternately. The serpentine tubes (15) undertake the cold storage function of the cold storage module, and the flow channels in the parallel flow plates undertake the heat exchange function of the cooling module. The cooling capacity and cold storage power of the two-phase flow phase change cold storage device can be adjusted by adjusting the number of phase change materials (13) and parallel flow plates (14).

2. The apparatus according to claim 1, characterized in that, The inlet end of the serpentine tube (15) is equipped with the cold storage side distributor (8) and the cold storage fluid inlet pipe (1), the outlet end of the serpentine tube (15) is equipped with the cold storage side collector (9) and the cold storage fluid outlet pipe (2), the inlet end (12) of the parallel flow plate is equipped with the cold supply side distributor (10) and the cold release fluid inlet pipe (3), and the outlet end (7) of the parallel flow plate is equipped with the cold supply side collector (11) and the cold release fluid outlet pipe (4). The parallel flow plate inlet end (12) evenly distributes the cooling fluid to each channel, and the parallel flow plate outlet end (7) collects and recovers the cooling fluid; the cooling side distributor (10) evenly distributes the cooling fluid entering through the cooling fluid inlet pipe (3) to each parallel flow plate, and then the cooling side cold storage side collector (11) collects the fluid and flows out from the cooling fluid outlet pipe (4).

3. The apparatus according to claim 1, characterized in that, The cold storage module has a built-in phase change material (13), and a serpentine tube (15) is embedded in the center of the phase change material (13) for transporting heat exchange fluid. The diameter and spacing of the serpentine tube (15) are adjusted according to the required heat exchange area. The inlet end of the serpentine tube (15) distributes the cold storage fluid flowing in from the cold storage fluid inlet pipe (1) through the cold storage side distributor (8) and distributes the cold storage fluid evenly to each serpentine tube (15). The outlet end of the serpentine tube (15) transmits the cold storage fluid recovered by the straight cylinder cold storage side collector (9) to the cold storage fluid outlet pipe (2), and then the cold storage fluid is discharged by the cold storage fluid outlet pipe (2).

4. The apparatus according to claim 1, characterized in that, The parallel flow plate (14) has a certain number of parallel flow channels arranged on it. The diameter and number of the parallel flow channels are adjusted according to the required heat exchange area. Each parallel flow channel is a rectangular flow channel or a rounded rectangular flow channel. The parallel flow channels are distributed at equal intervals or at non-equal intervals as needed. The length and width dimensions of each parallel flow channel are selected according to the heat release power requirements.

5. The apparatus according to claim 4, characterized in that, The phase change cold storage device adjusts the cold storage capacity, cold storage power, and cold release power through a modular design, with a total cold storage capacity... The number of phase change material plates (13) Cold storage capacity of a single plate The product is determined as follows: n Mass of phase change material filling within a single plate and phase transition enthalpy Decide; Total cold storage capacity The number of cold storage modules Power of a single cold storage module The product is determined; The heat transfer area and overall heat transfer coefficient of the serpentine tube and working fluid temperature difference Decide; Total cooling power The number of parallel flow plates 14 Power of a single parallel flow plate The product is determined by the power of a single parallel flow plate. Heat exchange area of ​​the flow channel Overall heat transfer coefficient and working fluid temperature difference The product is determined; 。 6. The apparatus according to claim 1, characterized in that, The total heat exchange area of ​​the phase change cold storage The heat transfer area of ​​a single circular flow channel is determined by both the heat transfer area of ​​a single flow channel and the number of flow channels. Heat transfer area of ​​single rectangular and rounded rectangular flow channels = ,in Inner diameter , For cross-sectional dimensions, The length of the flow channel; By adjusting , , The total heat exchange area of ​​the phase change cold storage is adjusted by the value of [value]. This allows for the adjustment of the heat exchange power of the phase change accumulator.

7. The apparatus according to claim 1, characterized in that, The liquid distribution holes in the parallel flow plate outlet end (7) and the parallel flow plate inlet end (12) are designed in a stepped manner from the inlet end to the outlet end, and the maximum orifice diameter of the parallel flow plate outlet end (7) and the parallel flow plate inlet end (12) does not exceed the maximum orifice diameter of the parallel flow channel, and the minimum orifice diameter is not less than 1 / 2 of the minimum orifice diameter of the parallel flow channel.

8. The apparatus according to claim 1, characterized in that, The materials of the parallel flow plate outlet end (7) and the parallel flow plate inlet end (12) are the same as or compatible with the material of the parallel flow plate (14), and the parallel flow plate outlet end (7), the parallel flow plate inlet end (12) and the parallel flow plate (14) are connected by welding, brazing or mechanical sealing.

9. The apparatus according to claim 1, characterized in that, The working fluid in the serpentine tube (15) and the parallel flow plate (14) is selected from one or more of the single-phase flow coolants that utilize sensible heat to carry cold energy; or, one or more of the two-phase flow refrigerants that utilize latent heat of phase change are selected. The phase change material is selected from one or more composite systems of water-expanded graphite composite material, various paraffin-expanded graphite composite materials, fatty acid-expanded graphite composite materials, and polyol-expanded graphite composite materials. The phase change temperature range of the phase change material is -10℃ to 25℃, the phase change enthalpy is not less than 200kJ / kg, and the thermal conductivity is not less than 2W / (m・K).

10. The apparatus according to claim 1, characterized in that, Fasteners (6) are installed on the cold storage shell (5). The material of the cold storage shell is selected from carbon steel, stainless steel, aluminum alloy, copper and titanium alloy. The thickness of the cold storage shell is set according to the pressure requirements.

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