Heat storage and heat exchange device and heat pump system

Abstract

The application discloses a heat storage and exchange device and a heat pump system. The heat storage and exchange device comprises a shell component, a first pipeline and a second pipeline. The shell component has a cavity, and a phase change heat storage and exchange medium is arranged in the cavity. The first pipeline is at least partially arranged in the cavity and is used for at least conveying a first fluid. The second pipeline is at least partially arranged in the cavity and is used for at least conveying a second fluid. The first pipeline and the second pipeline are at least partially wound with each other. The application can solve the problem that the arrangement design of the heat disc tube in the inner container is unreasonable in the prior art, and the heat exchange efficiency of the phase change heat storage device is easily affected.

Description

Technical Field

[0001] This application relates to the field of heat pump technology, and more specifically, to a heat storage and heat exchange device and a heat pump system. Background Technology

[0002] In traditional triple-heat pump air conditioning systems, domestic hot water heat exchangers typically employ either coaxial heat exchangers or plate heat exchangers. However, both coaxial heat exchangers and plate heat exchangers have some drawbacks, such as poor heat exchange efficiency and the inability to provide instant hot water.

[0003] With the upgrading of energy efficiency in heat pump systems and the enhancement of user demands, phase change thermal storage devices utilizing phase change materials (PCMs) as the heat transfer medium have emerged. These devices mainly consist of an outer shell, an inner tank, and heat exchange coils. The inner tank is filled with PCM, and the heat exchange coils are embedded within it. Energy is efficiently stored and released through the heat absorption / release phase change process of the PCM during temperature changes. However, the existing design of the heat exchange coils within the inner tank is often flawed, easily affecting the heat exchange efficiency of the phase change thermal storage device. Utility Model Content

[0004] The main purpose of this application is to provide a thermal storage and heat exchange device and a heat pump system to solve the problem that the unreasonable arrangement design of the heat coil in the inner tank in the prior art easily affects the heat exchange efficiency of the phase change thermal storage device.

[0005] According to one aspect of this application, a thermal storage and heat exchange device is provided, comprising: A housing component having a cavity filled with a phase change heat storage and heat exchange medium; A first conduit, at least partially disposed within the cavity, is used for at least conveying a first fluid; A second conduit, at least partially disposed within the cavity, is used for at least conveying a second fluid; The first pipeline and the second pipeline are at least partially intertwined.

[0006] Furthermore, the first conduit located within the cavity is arranged in a spiral shape to form a spiral gap, and the second conduit located within the cavity is arranged in a spiral shape and embedded within the spiral gap.

[0007] Furthermore, the first pipe and the second pipe located within the cavity are spirally wound into a long strip structure, and the long strip structure is repeatedly bent within the cavity.

[0008] Furthermore, along the direction from the bottom to the top of the cavity, the elongated structure is repeatedly bent into multiple layers, and in each layer, the elongated structure is repeatedly bent along the length or width direction of the shell component.

[0009] Furthermore, the phase change thermal storage and heat exchange medium covers the outer surfaces of the first pipeline and the second pipeline; and / or, The phase change thermal storage and heat exchange medium has a predetermined gap with the top of the cavity; The cavity is further provided with at least one load-bearing plate, and both the first pipe and the second pipe are installed on the load-bearing plate; and / or, The outer surface of the housing component is covered with an insulation layer; and / or, The housing component includes a bottom shell and a cover, the bottom shell having the cavity, and the cover covering the bottom shell to seal the cavity.

[0010] Furthermore, the cavity is also provided with a plurality of heat-conducting fins, which are spaced apart along the length of the shell component to divide the cavity into a plurality of sub-chambers. Each sub-chamber contains the phase change heat storage and heat exchange medium, and the first pipeline and the second pipeline pass through the heat-conducting fins.

[0011] Furthermore, the heat-conducting fins are provided with through holes, and the first pipe and the second pipe are located in the through holes. The cross-sectional area of ​​the through holes is greater than the sum of the cross-sectional areas of the first pipe and the second pipe.

[0012] Furthermore, the radius of the through hole is R, the distance between the geometric center of the first pipe and the geometric center of the second pipe is D, and the radius of the outer diameter of the first pipe or the second pipe is r, wherein R, D and r satisfy the relationship: 2R≥D+2r.

[0013] Furthermore, the first pipeline includes a first inlet, a first outlet, and a first delivery section. The first inlet and the first outlet are both located outside the housing component, and the first delivery section is connected between the first inlet and the first outlet and is located inside the cavity. The second pipeline includes a second inlet, a second outlet, and a second delivery section. The second inlet and the second outlet are both located outside the housing component, and the second delivery section is connected between the second inlet and the second outlet and is located inside the cavity. The first inlet, the first outlet, the second inlet, and the second outlet are all located on the same side of the housing component, with the first inlet and the second inlet both located near the bottom of the cavity, and the first outlet and the second outlet both located near the top of the cavity.

[0014] Furthermore, the distance D between the geometric center of the first pipeline and the geometric center of the second pipeline satisfies the relationship: 15mm ≤ D ≤ 16mm; and / or, The radius r of the outer diameter of the first pipeline satisfies the following relationship: 4mm ≤ r ≤ 5mm; and / or, The outer diameter radius r of the second pipeline satisfies the following relationship: 4mm ≤ r ≤ 5mm; and / or, Along the radial direction of the first pipeline, the wall thickness d1 of the first pipeline satisfies the relationship: 0.2mm ≤ d1 ≤ 0.4mm; and / or, Along the radial direction of the second conduit, the wall thickness d2 of the second conduit satisfies the relationship: 0.2mm ≤ d2 ≤ 0.4mm; and / or, The cavity contains heat-conducting fins, each with a through-hole. The radius R of the through-hole satisfies the following relationship: 10mm ≤ R ≤ 14mm; and / or, The through-hole has a center bisector, and the line connecting the geometric center of the first pipe and the geometric center of the through-hole is the first connecting line. The angle θ between the first connecting line and the center bisector satisfies the following relationship: 40°≤θ≤50°; and / or, Along the length of the housing component, the winding length L of the first and second pipes after winding satisfies the following relationship: 450mm ≤ L ≤ 550mm; and / or, The torsion angle φ of the spiral winding of the first and second pipes satisfies the following relationship: 1700°≤φ≤1900°; and / or, The cavity contains heat-conducting fins, and the thickness t of the heat-conducting fins along the length of the shell component satisfies the following relationship: 0.05mm ≤ t ≤ 0.25mm; and / or, The cavity contains multiple heat-conducting fins. Along the length of the housing component, the spacing h between two adjacent heat-conducting fins satisfies the following relationship: 1.0 mm ≤ h ≤ 4.5 mm; and / or... A load-bearing plate is provided inside the cavity. Along the length of the shell component, the thickness t1 of the load-bearing plate satisfies the following relationship: 2mm≤t1≤4mm.

[0015] Furthermore, the cavity is also provided with heat-conducting fins, the heat-conducting fins including copper fins; and / or, The cavity is also equipped with a load-bearing plate, which includes a stainless steel plate; and / or, The first conduit includes a copper pipe; and / or, The second conduit includes a copper pipe; and / or, The housing component includes a stainless steel housing; and / or, The outer surface of the housing component is covered with an insulation layer, the insulation layer comprising a polyurethane layer; and / or, One of the first fluid and the second fluid is a refrigerant, and the other is water.

[0016] On the other hand, this application also provides a heat pump system, which includes the above-mentioned heat storage and heat exchange device.

[0017] By intertwining the first and second pipes at least partially, the effective contact area between the two pipes can be increased, the heat transfer path between the first fluid in the first pipe and the second fluid in the second pipe can be shortened, the thermal resistance between the first and second pipes can be reduced, and the heat of the first fluid can be directly and quickly transferred to the second fluid through the pipe wall, or the heat of the second fluid can be transferred to the first fluid, thus effectively improving the heat exchange efficiency of the heat storage and heat exchange device. Attached Figure Description

[0018] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings: Figure 1 This is a schematic diagram of the structure of the heat storage and heat exchange device (without the cover) disclosed in the embodiments of this application; Figure 2 This is a schematic diagram of the structure of the heat storage and heat exchange device disclosed in the embodiments of this application; Figure 3 This is a cross-sectional view of the heat storage and heat exchange device disclosed in the embodiments of this application from a first-view perspective. Figure 4 This is a schematic diagram of the structure of the first pipeline, the second pipeline, and the heat-conducting fins disclosed in the embodiments of this application; Figure 5 This is a cross-sectional view of the heat storage and heat exchange device disclosed in the embodiments of this application from a second perspective. Figure 6 This is a schematic diagram of the structure of the first pipeline, the second pipeline, and the through hole disclosed in the embodiments of this application; Figure 7 This is a schematic diagram of the structure in which the first and second pipelines disclosed in the embodiments of this application are intertwined; Figure 8 This is a schematic diagram of the load-bearing plate disclosed in the embodiments of this application; Figure 9 This is a schematic diagram of the structure of the heat-conducting fins disclosed in the embodiments of this application; Figure 10 This is an enlarged view of the first and second pipelines disclosed in the embodiments of this application within the through hole.

[0019] The above figures include the following reference numerals: 10. Shell component; 101. Cavity; 102. Sub-chamber; 11. Bottom shell; 12. Cover; 20. First pipeline; 201. Helical gap; 21. First inlet; 22. First outlet; 23. First conveying section; 30. Second pipeline; 31. Second inlet; 32. Second outlet; 33. Second conveying section; 40. Long strip structure; 50. Phase change heat storage and heat exchange medium; 60. Heat-conducting fins; 61. Through hole; 611. Center line; 70. Load-bearing plate; 80. Insulation layer; 90. First connecting line. Detailed Implementation

[0020] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0021] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0022] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0023] As mentioned in the background section, existing phase change thermal energy storage devices mainly consist of an outer shell, an inner liner, and heat exchange coils. The inner liner is filled with a phase change material, and the heat exchange coils are embedded within the phase change material. Energy is efficiently stored and released through the heat absorption / release phase change process of the phase change material during temperature changes. However, the arrangement of the heat exchange coils within the inner liner in existing devices is unreasonable and can easily affect the heat exchange efficiency of the phase change thermal energy storage device. Therefore, the inventors of this application have designed a new thermal energy storage and heat exchange device that can at least improve the heat exchange efficiency of the phase change thermal energy storage device. The thermal energy storage and heat exchange device of this application will be described in detail below with reference to the accompanying drawings.

[0024] See Figures 1 to 4 As shown, according to an embodiment of this application, a heat storage and heat exchange device is provided, which includes a shell component 10, a first pipeline 20, and a second pipeline 30.

[0025] Specifically, the shell component 10 has a cavity 101 filled with a phase change heat storage and heat exchange medium 50; a first pipe 20 is at least partially disposed in the cavity 101 for at least conveying a first fluid; a second pipe 30 is at least partially disposed in the cavity 101 for at least conveying a second fluid; wherein the first pipe 20 and the second pipe 30 are at least partially intertwined. It should be noted that "intertwined" in this application includes the first pipe 20 and the second pipe 30 being directly attached and intertwined, and the first pipe 20 and the second pipe 30 maintaining a certain gap but still being intertwined.

[0026] In this embodiment, the cavity 101 provides a stable space for the phase change thermal storage medium 50, which can efficiently store and release heat based on its own phase change characteristics. It is worth mentioning that the phase change thermal storage medium 50 absorbs heat when it melts from a solid to a liquid state and releases heat when it solidifies from a liquid state to a solid state. It is understood that, since the first pipe 20 and the second pipe 30 in this embodiment are at least partially intertwined, when the first fluid (such as a high-temperature fluid) transported by the first pipe 20 and the second fluid (such as a low-temperature fluid) transported by the second pipe 30 flow in the cavity 101, the intertwined first pipe 20 and the second pipe 30 increase the contact interface between them, forming a spiral or spiral surface contact pattern with a longer length and a wider contact interface. This not only increases the effective contact area between the first pipe 20 and the second pipe 30, but also shortens the heat transfer path between the first fluid and the second fluid. As a result, the heat of the first fluid in the first pipe 20 can be quickly and directly transferred to the second fluid in the second pipe 30 without going through a complex path, effectively improving the heat exchange efficiency of the heat storage and heat exchange device. Meanwhile, the phase change heat storage medium 50 inside the cavity 101 can fully contact the intertwined first pipe 20 and second pipe 30. At this time, the phase change heat storage medium 50 can quickly absorb and store the heat transferred by the first pipe 20 through its own phase change process, avoiding heat loss, and can quickly transfer heat to the second pipe 30, further ensuring the heat exchange efficiency of the heat storage heat exchange device. Of course, in this embodiment, the first fluid can be a low-temperature fluid, and the second fluid can be a high-temperature fluid.

[0027] In other words, by at least partially intertwining the first pipe 20 and the second pipe 30, this embodiment can expand the effective contact area between the two pipes, shorten the heat transfer path between the first fluid in the first pipe 20 and the second fluid in the second pipe 30, reduce the thermal resistance between the first pipe 20 and the second pipe 30, and allow the heat of the first fluid to be directly and quickly transferred to the second fluid through the pipe wall, or the heat of the second fluid to be transferred to the first fluid, effectively improving the heat exchange efficiency of the thermal storage and heat exchange device. In addition, the double-twisted pipe twisting and winding arrangement can also effectively reduce the problem of insufficient thermal storage and heat exchange efficiency caused by the dead zone of thermal storage and heat release formed by the tubular fluid passage and the square shell in the prior art.

[0028] like Figure 3 and Figure 7As shown, in some embodiments, the first conduit 20 located within the cavity 101 is arranged in a spiral shape to form a spiral gap 201, and the second conduit 30 located within the cavity 101 is also arranged in a spiral shape and embedded within the spiral gap 201. This arrangement allows the first conduit 20 and the second conduit 30 to be arranged compactly and orderly within the cavity 101, avoiding space waste caused by messy conduit arrangement and minimizing the ineffective gaps between the first conduit 20 and the second conduit 30.

[0029] Meanwhile, by arranging both the first pipe 20 and the second pipe 30 in a spiral shape, this embodiment extends the length of the first pipe 20 and the second pipe 30 within the cavity 101. Furthermore, the second pipe 30 is embedded within the spiral gap 201, resulting in a large-area, close-range contact between the two pipes along their overall extension direction. This increases the contact range between the two pipes and the phase change heat storage medium 50 within the cavity 101, allowing the phase change heat storage medium 50 to more fully fill the gap between the two pipes. When the first pipe 20 transports the first fluid and the second pipe 30 transports the second fluid, heat can be rapidly transferred between the two pipes via the phase change heat storage medium 50. Simultaneously, the spirally wound structure of the first pipe 20 and the second pipe 30 reduces heat loss during the transfer process, further improving the heat exchange rate and energy utilization efficiency of the entire heat storage and heat exchange device, ensuring that the device can stably perform its dual functions of heat storage and heat exchange during operation.

[0030] like Figures 3 to 4 As shown, in some embodiments, the first pipe 20 and the second pipe 30 located within the cavity 101 are spirally wound into a long strip structure 40, which is repeatedly bent within the cavity 101. In this embodiment, the spiral winding of the first pipe 20 and the second pipe 30 allows the two pipes to form a larger contact interface in the extending direction, increasing the contact area between the first pipe 20, the second pipe 30, and the phase change heat storage medium 50. This also provides a more efficient path for heat transfer between the two pipes. Furthermore, the repeated bending of the long strip structure 40 within the cavity 101 not only efficiently utilizes the space inside the cavity 101, avoiding space waste due to the length limitation of a single long strip structure 40, but also ensures that the heat exchange units formed by the spiral winding are evenly distributed within the cavity 101, reducing heat exchange blind spots and effectively improving the heat exchange efficiency of the heat storage heat exchange device.

[0031] In other words, when the first pipe 20 and the second pipe 30 respectively transport the first fluid and the second fluid, the large-area contact caused by the spiral winding allows heat to be efficiently conducted between the first pipe 20 and the second pipe 30. The uniform layout formed by the reciprocating bends allows the phase change heat storage and heat exchange medium 50 to fully contact the first pipe 20 and the second pipe 30, further improving the heat exchange efficiency. At the same time, it ensures the stability and uniformity of heat transfer during the operation of the entire device, allowing the device to achieve better heat storage and heat exchange performance within a limited volume.

[0032] like Figure 3 As shown, in some embodiments, the elongated structure 40 is repeatedly bent into multiple layers along the direction from the bottom to the top of the cavity 101, and in each layer, the elongated structure 40 is repeatedly bent along the length or width direction of the housing component 10. It should be noted that the "length direction of the housing component 10" in this application refers to... Figure 1 The direction indicated by the middle arrow X; "the width direction of housing component 10" refers to... Figure 1 The direction indicated by the middle arrow Y.

[0033] Specifically, the multi-layered elongated structure 40 allows the elongated structure 40, formed by the spiral winding of the first pipe 20 and the second pipe 30, to form a uniform and dense distribution within the cavity 101. This not only increases the total contact between the pipes and the phase change heat storage medium 50, but also allows the phase change heat storage medium 50 to more fully envelop each section of the pipe, reducing heat accumulation or transfer lag caused by uneven distribution of local pipes. When the fluid flows in the pipes, heat can be rapidly transferred through the large-area contact of the phase change heat storage medium 50. The multi-layered and directional bending layout ensures consistent heat exchange efficiency at different heights and planar positions within the cavity 101, effectively improving the heat storage and heat exchange stability of the entire device, allowing the device to achieve more efficient energy conversion and utilization within the limited volume of the cavity 101.

[0034] In some embodiments, the phase change heat storage medium 50 covers the outer surfaces of the first pipe 20 and the second pipe 30. This arrangement allows for a large-area, close contact between the phase change heat storage medium 50 and the first and second pipes 20 and 30, eliminating gaps between the two pipes and the phase change heat storage medium 50. This allows the heat carried by the first fluid in the first pipe 20 to be quickly transferred through the pipe wall to the phase change heat storage medium 50. The medium efficiently absorbs and stores heat due to its phase change properties, avoiding heat loss due to gaps in the transfer path. Simultaneously, when the second pipe 30 needs to acquire heat, the energy stored in the phase change heat storage medium 50 can be directly and uniformly conducted to the pipe wall of the second pipe 30 through the contact interface formed by the covering, and then transferred to the second fluid, ensuring a stable and efficient heat release process.

[0035] Of course, in other embodiments, the heat carried by the second fluid in the second pipe 30 can be quickly transferred through the pipe wall to the phase change heat storage medium 50. When the first pipe 20 needs to obtain heat, the energy stored in the phase change heat storage medium 50 can be transferred to the pipe wall of the first pipe 20 and then to the first fluid.

[0036] like Figure 3 As shown, in some embodiments, the phase change heat storage medium 50 and the top of the cavity 101 have a predetermined gap. Specifically, when the phase change heat storage medium 50 absorbs heat and changes from a solid to a liquid state, its volume will expand accordingly. The predetermined gap can prevent the phase change heat storage medium 50 from generating excessive pressure due to expansion and squeezing the cavity 101, the first pipeline 20, or the second pipeline 30, thus preventing the cavity 101 structure from deforming and causing leakage of the phase change heat storage medium 50 or failure of pipeline sealing.

[0037] To improve the thermal conductivity of thermal storage and heat exchange devices, such as Figures 1 to 4 As shown, in some embodiments, the cavity 101 is further provided with a plurality of heat-conducting fins 60. The plurality of heat-conducting fins 60 are spaced apart along the length direction of the shell component 10 to divide the cavity 101 into a plurality of sub-cavities 102. Each sub-cavity 102 contains a phase change heat storage and heat exchange medium 50. The first pipe 20 and the second pipe 30 pass through the heat-conducting fins 60. It can be understood that the heat-conducting fins 60 have high thermal conductivity, which can quickly receive and transfer heat in the cavity 101, providing an efficient heat conduction path for the heat absorption, heat storage and heat release of the phase change heat storage and heat exchange medium 50. When the first or second fluid is a high-temperature fluid, heat is not only directly transferred to the surrounding phase change heat storage medium 50 through the pipe wall of the first pipe 20 or the pipe wall of the second pipe 30, but also conducted to the heat-conducting fins 60 through the first pipe 20 or the second pipe 30. The heat-conducting fins 60 then rapidly diffuse the heat to the phase change heat storage medium 50 in each sub-chamber 102, accelerating the heat absorption and storage of the phase change heat storage medium 50. When the first pipe 20 or the second pipe 30 requires heat, the heat released by the medium in each sub-chamber 102 can be efficiently gathered to the pipe wall of the corresponding first pipe 20 or second pipe 30 through the heat-conducting fins 60, improving the heat transfer efficiency to the fluid in the first pipe 20 or the second pipe 30.

[0038] like Figure 6 and Figure 10As shown, in some embodiments, the heat-conducting fins 60 are provided with through holes 61, and the first pipe 20 and the second pipe 30 are disposed in the through holes 61. The cross-sectional area of ​​the through holes 61 is greater than the sum of the cross-sectional areas of the first pipe 20 and the second pipe 30. It should be noted that, in this application, "the cross-sectional area of ​​the through hole 61" refers to the area of ​​the cross-section obtained by cutting the through hole 61 along a direction perpendicular to the extension direction of the first pipe 20 or the second pipe 30; "the cross-sectional area of ​​the first pipe 20" refers to the area of ​​the cross-section obtained by cutting the first pipe 20 along a direction perpendicular to its own extension direction; and "the cross-sectional area of ​​the second pipe 30" refers to the area of ​​the cross-section obtained by cutting the second pipe 30 along a direction perpendicular to its own extension direction.

[0039] Specifically, the through-hole 61 allows the phase change heat storage medium 50 to flow between the sub-chambers 102 after being heated and melted. This enables the phase change heat storage medium 50 to be gradually and evenly dispersed during the heating cycle, avoiding excessive local pressure caused by local accumulation of the medium and further improving the uniformity of the phase change heat storage medium 50 distribution within the cavity 101. Simultaneously, since the cross-sectional area of ​​the through-hole 61 in this embodiment is larger than the sum of the cross-sectional areas of the first pipe 20 and the second pipe 30, when the first pipe 20 and the second pipe 30 deform due to changes in the temperature of the transported fluid, rigid compression between the first pipe 20 and the inner wall of the through-hole 61 during expansion can be avoided, thus preventing wear on the outer wall of the pipes or cracking of the fins. In addition, the extra space inside the through hole 61 can be filled with the phase change heat storage and heat exchange medium 50, so that the phase change heat storage and heat exchange medium 50 can more fully wrap the first pipe 20 and the second pipe 30, avoiding the medium from not being able to fit the pipe due to the through hole 61 being too narrow, and enhancing the heat transfer effect between the pipe and the medium.

[0040] like Figure 10 As shown, in some embodiments, the radius of the through hole 61 is R, the distance between the geometric center of the first pipe 20 and the geometric center of the second pipe 30 is D, and the radius of the outer diameter of the first pipe 20 or the second pipe 30 is r. R, D, and r satisfy the relationship: 2R ≥ D + 2r. This arrangement ensures that when the first pipe 20 and the second pipe 30 pass through the through hole 61, they will not directly contact the inner wall of the through hole 61 due to insufficient space. This avoids collision and wear between the first pipe 20 and the second pipe 30 and the hole wall during installation. It also provides deformation space for the first pipe 20 and the second pipe 30 due to thermal expansion and contraction caused by temperature changes during operation, preventing damage to the first pipe 20 or the second pipe 30 or the heat-conducting fins 60 caused by rigid compression. At the same time, the reserved gap space can meet the needs of the phase change heat storage medium 50 to flow between each sub-chamber 102, ensuring that the phase change heat storage medium 50 can smoothly circulate between different sub-chambers 102 after being heated and melted.

[0041] like Figures 1 to 3 As shown, in some embodiments, the first pipeline 20 includes a first inlet 21, a first outlet 22, and a first conveying section 23. The first inlet 21 and the first outlet 22 are both located outside the housing component 10, and the first conveying section 23 is connected between the first inlet 21 and the first outlet 22 and is located inside the cavity 101. The second pipeline 30 includes a second inlet 31, a second outlet 32, and a second conveying section 33. The second inlet 31 and the second outlet 32 ​​are both located outside the housing component 10, and the second conveying section 33 is connected between the second inlet 31 and the second outlet 32 ​​and is located inside the cavity 101. The first inlet 21, the first outlet 22, the second inlet 31, and the second outlet 32 ​​are all located on the same side of the housing component 10, and the first inlet 21 and the second inlet 31 are both located near the bottom of the cavity 101, and the first outlet 22 and the second outlet 32 ​​are both located near the top of the cavity 101.

[0042] Specifically, this embodiment, by placing the first inlet 21, the first outlet 22, the second inlet 31, and the second outlet 32 ​​on the same side of the housing component 10, facilitates centralized connection and maintenance of the first pipeline 20 and the second pipeline 30 with external systems, thereby reducing the installation complexity caused by the dispersed arrangement of the first pipeline 20 and the second pipeline 30 on the housing component 10. Simultaneously, by placing the first inlet 21 and the second inlet 31 near the bottom of the cavity 101, and the first outlet 22 and the second outlet 32 ​​near the top of the cavity 101, this embodiment can reduce the contact thermal resistance of bottom heat exchange through the pressure of the phase change heat storage medium 50 itself, thereby enhancing the heat transfer efficiency between the first pipeline 20, the second pipeline 30, and the phase change heat storage medium 50, effectively improving the heat exchange efficiency of the device.

[0043] Specifically, assuming the first fluid is a high-temperature fluid and the second fluid is a low-temperature fluid. When the phase change heat storage medium 50 is in the heat storage stage, its temperature is lower than that of the first fluid. At this time, the high-temperature first fluid enters the first conveying section 23 from the first inlet 21 at the bottom of the cavity 101 and will preferentially contact the phase change heat storage medium 50 at the bottom of the cavity 101. Since the bottom of the cavity 101 is the initial inflow area of ​​the first fluid, the highest temperature first fluid here can form the maximum temperature difference with the lowest temperature bottom phase change heat storage medium 50, laying the foundation for efficient heat exchange. As the first fluid flows upward along the first conveying section 23, its heat is continuously transferred to the phase change heat storage medium 50 along the way, causing the temperature of the first fluid itself to gradually decrease, and the temperature difference between it and the phase change heat storage medium 50 in the upper part (and eventually the top) of the cavity 101 also gradually decreases. During this process, the phase change heat storage medium 50 at the bottom of the cavity 101 melts due to absorbing heat first. The pressure generated by the volume expansion after melting will force the gap between the bottom first pipe 20 and the phase change heat storage medium 50 to be filled, directly reducing the contact thermal resistance of the area with the largest temperature difference (i.e., the bottom area), so that the heat transfer efficiency of the high temperature difference area can be maximized.

[0044] When the phase change heat storage medium 50 is in the heat release stage, its temperature is higher than that of the second fluid. At this time, the low-temperature second fluid, after entering the second conveying section 33 from the second inlet 31 at the bottom of the cavity 101, will preferentially contact the phase change heat storage medium 50 at the bottom of the cavity 101. Because the phase change heat storage medium 50 at the bottom has released heat first, its temperature is lower than that of the phase change heat storage medium 50 in the upper part (to the top) of the cavity 101. Therefore, a large initial temperature difference can be formed between the low-temperature second fluid and the bottom phase change heat storage medium 50. As the second fluid flows upward along the second conveying section 33, it continuously absorbs the heat released by the phase change heat storage medium 50 along the way, and its own temperature gradually increases. The temperature difference between it and the phase change heat storage medium 50 at the top of the cavity 101, which has a higher temperature, also gradually decreases. During this process, the phase change heat storage medium 50 at the bottom solidifies due to continuous heat release. During solidification, volume shrinkage occurs. Meanwhile, the phase change heat storage medium 50 at the top of the cavity 101, which is still in a liquid state, will flow downwards under its own gravity to fill the gaps caused by solidification and shrinkage at the bottom. This ensures that the phase change heat storage medium 50 in the area with the largest initial temperature difference at the bottom is always in full contact with the second pipeline 30, so that the contact thermal resistance in this area is always at a low level.

[0045] like Figure 3 and Figure 5As shown, in some embodiments, at least one load-bearing plate 70 is also provided inside the cavity 101, and the first pipe 20 and the second pipe 30 are both installed on the load-bearing plate 70. Specifically, the load-bearing plate 70 is used to support and fix the first pipe 20 and the second pipe 30, preventing the first pipe 20 and the second pipe 30 from relative displacement due to device vibration, temperature fluctuation or medium phase change expansion, and ensuring that the heat transfer efficiency will not decrease due to changes in the position of the pipes.

[0046] For example, in this embodiment, the load-bearing plate 70 includes one, two, or more. Figure 3 The diagram shows the case where the load-bearing plate 70 includes two plates.

[0047] like Figure 5 As shown, in some embodiments, the outer surface of the housing component 10 is covered with an insulation layer 80. This arrangement can reduce the heat exchange between the phase change heat storage medium 50 inside the cavity 101 and the external environment, thereby reducing heat loss from the heat storage and heat exchange device.

[0048] like Figures 1 to 2 As shown, in some embodiments, the housing component 10 includes a bottom shell 11 and a cover 12. The bottom shell 11 has a cavity 101, and the cover 12 is placed on the bottom shell 11 to seal the cavity 101. Specifically, in this embodiment, by placing the cover 12 on the bottom shell 11 to seal the cavity 101, the phase change heat storage medium 50 can be firmly locked inside the cavity 101, preventing the phase change heat storage medium 50 from overflowing due to thermal expansion or leaking due to device tilting. It also isolates dust, moisture, and other impurities in the outside air from entering the cavity 101, preventing impurities from adhering to the outer walls of the first pipe 20 and the second pipe 30 or the surface of the heat-conducting fins 60 and affecting heat transfer. At the same time, the separate structure of the bottom shell 11 and the cover 12 makes filling and replacing the phase change heat storage medium 50 more convenient. When it is necessary to replenish the new phase change heat storage medium 50, or when the phase change heat storage medium 50 needs to be replaced due to long-term performance degradation, there is no need to disassemble the entire shell component 10. Simply open the cover 12 to directly add material into the cavity 101, or clean the old medium and refill it, which simplifies the operation process and saves maintenance time.

[0049] In some embodiments, the distance D between the geometric center of the first conduit 20 and the geometric center of the second conduit 30 (e.g., ...) Figure 10 As shown, the following relationship is satisfied: 15mm≤D≤16mm. For example, D can be set to 15mm, 15.1mm, 15.2mm, 15.3mm, 15.4mm, 15.5mm, 15.6mm, 15.7mm, 15.8mm, 15.9mm, 16mm, etc.

[0050] Specifically, this embodiment ensures that the distance D between the geometric center of the first pipe 20 and the geometric center of the second pipe 30 satisfies the relationship: 15mm≤D≤16mm. This not only provides sufficient space for the first pipe 20 and the second pipe 30 within the cavity 101, preventing the outer walls of the pipes from being too close together and squeezed due to excessive spacing, or hindering the flow of the phase change heat storage medium 50 between the two pipes, but also ensures that the phase change heat storage medium 50 can fill the gap between the first pipe 20 and the second pipe 30 and fully wrap the outer wall of each pipe, providing sufficient contact area for heat transfer. Furthermore, it prevents the waste of space within the cavity 101 due to excessive spacing, allowing the first pipe 20 and the second pipe 30 to maintain a reasonable distribution density within the limited volume of the cavity 101.

[0051] In some embodiments, the radius r of the outer diameter of the first conduit 20 (e.g., Figure 10 As shown, the following relationship is satisfied: 4mm≤r≤5mm. For example, r can be set to 4mm, 4.1mm, 4.2mm, 4.3mm, 4.4mm, 4.5mm, 4.6mm, 4.7mm, 4.8mm, 4.9mm, 5mm, etc.

[0052] Specifically, in this embodiment, by ensuring that the radius r of the outer diameter of the first pipe 20 satisfies the relationship: 4mm≤r≤5mm, it can ensure that the first pipe 20 has sufficient structural strength, avoid the pipe wall of the first pipe 20 being too thin due to the radius being too small, thereby preventing the first pipe 20 from deforming or breaking when subjected to internal fluid pressure or in contact with the phase change heat storage medium 50, and ensuring the sealing and stability of fluid transportation. At the same time, it can also prevent the first pipe 20 from occupying too much space in the cavity 101 due to the radius being too large, avoiding squeezing the filling space of the phase change heat storage medium 50, or causing the distance between the first pipe 20 and the second pipe 30 to be too large.

[0053] In some embodiments, the radius r of the outer diameter of the second conduit 30 (e.g., Figure 10 As shown, the following relationship is satisfied: 4mm≤r≤5mm. For example, r can be set to 4mm, 4.1mm, 4.2mm, 4.3mm, 4.4mm, 4.5mm, 4.6mm, 4.7mm, 4.8mm, 4.9mm, 5mm, etc.

[0054] Specifically, in this embodiment, the radius r of the outer diameter of the second pipe 30 satisfies the relationship: 4mm≤r≤5mm. This ensures that the second pipe 30 has sufficient structural strength, preventing the pipe wall of the second pipe 30 from being too thin due to an excessively small radius. This prevents the second pipe 30 from deforming or breaking when subjected to internal fluid pressure or in contact with the phase change heat storage medium 50, thus ensuring the sealing and stability of fluid transportation. At the same time, it also prevents the second pipe 30 from occupying too much space in the cavity 101 due to an excessively large radius, thus avoiding squeezing the filling volume of the phase change heat storage medium 50 or causing the distance between the two pipes to be too large.

[0055] In some embodiments, along the radial direction of the first conduit 20, the wall thickness d1 of the first conduit 20 (e.g., ...) Figure 10 As shown, the following relationship is satisfied: 0.2mm≤d1≤0.4mm. For example, d1 can be set to 0.2mm, 0.22mm, 0.24mm, 0.26mm, 0.28mm, 0.3mm, 0.32mm, 0.34mm, 0.36mm, 0.38mm, 0.4mm, etc.

[0056] Specifically, this embodiment ensures that the wall thickness d1 of the first pipeline 20 satisfies the relationship: 0.2mm≤d1≤0.4mm. This not only gives the first pipeline 20 sufficient structural toughness and pressure-bearing capacity, preventing it from easily breaking or leaking when transporting fluid due to excessive wall thickness, or deforming when in contact with the phase change heat storage medium 50 and affected by thermal expansion and contraction, thus ensuring the stability and sealing of fluid transport, but also prevents the increase in thermal resistance of the first pipeline 20 due to excessive wall thickness. This avoids excessive heat loss during heat transfer between the inside and outside of the first pipeline 20 (from the fluid inside the pipe to the medium outside the pipe, or from the medium outside the pipe to the fluid inside the pipe), ensuring that heat can efficiently penetrate the pipe wall of the first pipeline 20 for transfer.

[0057] In some embodiments, along the radial direction of the second conduit 30, the wall thickness d2 of the second conduit 30 (e.g., Figure 10 As shown, the following relationship is satisfied: 0.2mm≤d2≤0.4mm. For example, d2 can be set to 0.2mm, 0.22mm, 0.24mm, 0.26mm, 0.28mm, 0.3mm, 0.32mm, 0.34mm, 0.36mm, 0.38mm, 0.4mm, etc.

[0058] Specifically, this embodiment ensures that the wall thickness d2 of the second pipeline 30 satisfies the relationship: 0.2mm≤d2≤0.4mm. This not only gives the second pipeline 30 sufficient structural toughness and pressure-bearing capacity, preventing it from easily breaking or leaking when transporting fluid due to excessive wall thickness, or deforming when in contact with the phase change heat storage medium 50 and affected by thermal expansion and contraction, thus ensuring the stability and sealing of fluid transport, but also prevents the second pipeline 30 from increasing its own thermal resistance due to excessive wall thickness. This avoids excessive heat loss during heat transfer between the inside and outside of the second pipeline 30 (from the fluid inside the pipe to the medium outside the pipe, or from the medium outside the pipe to the fluid inside the pipe), ensuring that heat can efficiently penetrate the pipe wall of the second pipeline 30 for transfer.

[0059] In some embodiments, the cavity 101 has heat-conducting fins 60, the heat-conducting fins 60 having through holes 61, and the radius R of the through holes 61 (e.g., Figure 10 As shown, the following relationship is satisfied: 10mm≤R≤14mm. For example, R can be set to 10mm, 10.5mm, 11mm, 11.5mm, 12mm, 12.5mm, 13mm, 13.5mm, 14mm, etc.

[0060] Specifically, this embodiment ensures that the radius R of the through hole 61 satisfies the relationship: 10mm≤R≤14mm. This not only accommodates the installation requirements of the first pipe 20 and the second pipe 30, ensuring that the first pipe 20 and the second pipe 30 can be smoothly installed in the through hole 61, but also reserves a reasonable gap between the inner wall of the through hole 61 and the outer wall of the pipe, allowing the phase change heat storage and heat exchange medium 50 to flow between each sub-chamber 102. This avoids the medium circulation being hindered by the gap being too small or the heat transfer being dispersed due to the gap being too large. It also ensures the structural strength of the heat-conducting fins 60 themselves, preventing the effective heat conduction area on the heat-conducting fins 60 from being reduced due to the radius of the through hole 61 being too large, thus weakening the heat conduction and diffusion capacity, or the dual pipes and reserved flow space being too small, thus affecting the overall layout of the device.

[0061] like Figure 10 As shown, in some embodiments, the through hole 61 has a center line 611, and the line connecting the geometric center of the first pipe 20 and the geometric center of the through hole 61 is the first connecting line 90. The angle θ between the first connecting line 90 and the center line 611 satisfies the relationship: 40°≤θ≤50°. For example, θ can be set to 40°, 41°, 42°, 43°, 44°, 45°, 46°, 47°, 48°, 49°, 50°, etc.

[0062] Specifically, this embodiment ensures that the angle θ between the first connecting line 90 and the center line 611 satisfies the relationship: 40°≤θ≤50°. This ensures that the first pipe 20 and the second pipe 30 will not be close to the hole wall on one side due to distribution offset within the through hole 61. This makes the flow channel of the phase change heat storage medium 50 reserved in the through hole 61 more uniform. At the same time, it can also meet the functional requirements of the heat-conducting fins 60 separating the sub-chambers 102. This ensures that the first pipe 20 maintains a fixed angle with the center line 611 when passing through each layer of fins, avoiding pipe twisting within the cavity 101 due to angle deviation. This ensures its smooth extension from the bottom inlet to the top outlet. At the same time, it allows the second pipe 30 to be stably distributed based on symmetrical angles, further enhancing the uniformity of contact between the two pipes and the phase change heat storage medium 50.

[0063] In some embodiments, along the length direction of the housing component 10, the winding length L after the first conduit 20 and the second conduit 30 are wound together (e.g., ... Figure 7 As shown, the following relationship is satisfied: 450mm≤L≤550mm. For example, L can be set to 450mm, 460mm, 470mm, 480mm, 490mm, 500mm, 510mm, 520mm, 530mm, 540mm, 550mm, etc.

[0064] Specifically, in this embodiment, by ensuring that the winding length L of the first pipe 20 and the second pipe 30 after winding satisfies the relationship: 450mm≤L≤550mm, sufficient extension space can be provided for the first pipe 20 and the second pipe 30 within the cavity 101. This ensures that the first pipe 20 and the second pipe 30 form a sufficient heat exchange contact area through winding, allowing the first fluid in the first pipe 20 or the second fluid in the second pipe 30 to have sufficient time to exchange heat with the phase change heat storage medium 50 within the cavity 101 during the flow from the bottom inlet to the top outlet. This avoids insufficient contact area and inadequate heat exchange due to excessively short winding length.

[0065] In some embodiments, the torsion angle φ of the spiral winding of the first conduit 20 and the second conduit 30 (e.g.) Figure 7 As shown, the following relationship is satisfied: 1700°≤φ≤1900°. For example, φ can be set to 1700°, 1720°, 1740°, 1760°, 1780°, 1800°, 1820°, 1840°, 1860°, 1880°, 1900°, etc.

[0066] Specifically, when φ is less than 1700°, the twist angle of the spiral winding of the first pipe 20 and the second pipe 30 is too small, which easily leads to the first pipe 20 and the second pipe 30 being wound too loosely, thereby reducing the contact area between the first pipe 20 and the second pipe 30 and the phase change heat storage heat exchange medium 50, resulting in insufficient heat transfer; when φ is greater than 1900°, the twist angle of the spiral winding of the first pipe 20 and the second pipe 30 is too large, which easily leads to the first pipe 20 and the second pipe 30 being wound too tightly, thereby squeezing the flow space of the phase change heat storage heat exchange medium 50 in the gap between the first pipe 20 and the second pipe 30. When the efficient heat exchange space between the pipes decreases, the effective volume of the phase change material decreases accordingly, and the overall heat storage and release efficiency of the system is thus suppressed.

[0067] In some embodiments, the cavity 101 has heat-conducting fins 60, and the thickness t of the heat-conducting fins 60 along the length direction of the housing component 10 is (e.g., ...). Figure 9 As shown, the relationship is satisfied: 0.05mm≤t≤0.25mm. For example, t can be set to 0.05mm, 0.10mm, 0.15mm, 0.20mm, 0.25mm, etc.

[0068] It is understandable that thinner fins result in a larger heat transfer area per unit volume, but this reduces mechanical rigidity and makes them more prone to deformation. Conversely, excessively thick fins increase thermal resistance and cost, while reducing fin efficiency. Specifically, when t is less than 0.05 mm, the thickness of the heat-conducting fin 60 is too thin, leading to decreased mechanical rigidity and easy deformation. When t is greater than 0.25 mm, the thickness of the heat-conducting fin 60 is too thick, increasing its weight and space requirements, resulting in higher manufacturing costs and increased thermal resistance. In other words, this embodiment ensures that the thickness t of the heat-conducting fin 60 satisfies the relationship: 0.05 mm ≤ t ≤ 0.25 mm. This not only ensures that the heat-conducting fin 60 possesses good heat conduction and diffusion capabilities and mechanical rigidity but also prevents excessive thickness from increasing its weight, occupying too much space, and increasing thermal resistance.

[0069] In some embodiments, the cavity 101 has heat-conducting fins 60, and the heat-conducting fins 60 include a plurality of fins. Along the length direction of the housing component 10, the spacing h between two adjacent heat-conducting fins 60 is (e.g., ...). Figure 3 As shown, the following relationship is satisfied: 1.0mm≤h≤4.5mm. For example, h can be set to 1.0mm, 1.5mm, 2.0mm, 2.5mm, 3.0mm, 3.5mm, 4.0mm, 4.5mm, etc.

[0070] Specifically, when h is less than 1.0 mm, the spacing between two adjacent heat-conducting fins 60 is too small. Although this can improve the heat conduction efficiency, the heat-conducting fins 60 occupy a lot of space, which not only reduces the effective filling amount of the phase change heat storage heat exchange medium 50, but also increases the material cost and process cost. When h is greater than 4.5 mm, the spacing between two adjacent heat-conducting fins 60 is too large, which leads to a decrease in heat conduction efficiency.

[0071] For example, in this embodiment, the heat-conducting fins 60 can be configured as two, three, or more. Figure 3 The diagram shows the case when the heat-conducting fins 60 are set to twenty-one.

[0072] In some embodiments, a load-bearing plate 70 is provided inside the cavity 101, and the thickness t1 of the load-bearing plate 70 is such that, along the length direction of the housing component 10, the thickness t1 of the load-bearing plate 70 is (e.g., ...). Figure 8 As shown, the following relationship is satisfied: 2mm≤t1≤4mm. For example, t1 can be set to 2mm, 2.2mm, 2.4mm, 2.6mm, 2.8mm, 3mm, 3.2mm, 3.4mm, 3.6mm, 3.8mm, 4mm, etc.

[0073] Specifically, when t1 is less than 2mm, the thickness of the load-bearing plate 70 is too thin, causing it to bend and deform under the weight of the first pipe 20 and the second pipe 30, the fluid pressure, and the impact of the phase change heat storage medium 50. When t1 is greater than 4mm, the thickness of the load-bearing plate 70 is too thick, occupying too much space within the cavity 101. In other words, this embodiment ensures that the thickness t1 of the load-bearing plate 70 satisfies the relationship: 2mm≤t1≤4mm, thus enabling the load-bearing plate 70 to have sufficient load-bearing strength to stably support the spirally wound first pipe 20 and second pipe 30.

[0074] In some embodiments, the cavity 101 is further provided with heat-conducting fins 60, which include copper fins. Copper fins have excellent thermal conductivity, which can quickly diffuse the heat transferred by the first pipe 20 and the second pipe 30 to the surrounding phase change heat storage medium 50, or efficiently absorb the heat stored in the phase change heat storage medium 50 and transfer it to the first pipe 20 and the second pipe 30, avoiding heat accumulation in local areas due to insufficient thermal conductivity, and ensuring a more uniform temperature distribution in each sub-cavity 102 within the cavity 101.

[0075] In some embodiments, a load-bearing plate 70 is further provided inside the cavity 101, and the load-bearing plate 70 includes a stainless steel plate. Specifically, the stainless steel plate has high structural strength and can stably bear the load generated by the weight of the first pipeline 20 and the second pipeline 30 and the fluid pressure.

[0076] In some embodiments, the first conduit 20 includes a copper tube. The copper tube has excellent thermal conductivity, which enables rapid heat transfer between the first fluid in the first conduit 20 and the phase change heat storage medium 50 in the cavity 101.

[0077] In some embodiments, the second conduit 30 includes a copper tube. The copper tube has excellent thermal conductivity, which enables rapid heat transfer between the second fluid in the second conduit 30 and the phase change heat storage medium 50 in the cavity 101.

[0078] In some embodiments, the housing component 10 includes a stainless steel housing. The stainless steel housing has high structural strength and can withstand the pressure caused by the volume change when the phase change heat storage medium 50 undergoes a phase change.

[0079] In some embodiments, the outer surface of the housing component 10 is covered with an insulation layer 80, which includes a polyurethane layer. The polyurethane layer has good thermal insulation performance and can form a thermal insulation barrier on the outer surface of the housing component 10, thereby reducing the heat loss from the phase change heat storage and heat exchange medium 50 in the cavity 101 to the external environment.

[0080] In some embodiments, one of the first fluid and the second fluid is a refrigerant, and the other is water. That is, the first fluid can be a refrigerant and the second fluid can be water; or the first fluid can be water and the second fluid can be a refrigerant.

[0081] Specifically, when the high-temperature refrigerant flows in the first pipe 20 or the second pipe 30, it can quickly transfer heat to the phase change heat storage medium 50; while when water flows through the second pipe 30 or the first pipe 20, it can exchange heat with the phase change heat storage medium 50 to heat the water. The temperature difference between the two fluids complements the heat storage characteristics of the phase change medium, avoiding the problem of insufficient efficiency when relying solely on a single fluid to exchange heat with the phase change heat storage medium 50, thereby achieving real-time heat storage and real-time heat exchange.

[0082] Specifically, the working principle of the thermal storage and heat exchange device of this application is as follows: Assume the first fluid is refrigerant and the second fluid is water.

[0083] The charging process: The first fluid enters the first conveying section 23 through the first inlet 21 and flows along the first conveying section 23 to the first outlet 22. During this process, the first fluid comes into full contact with the phase change heat storage medium 50 through the first conveying section 23, thereby fully transferring heat to the phase change heat storage medium 50. Since the solid phase change heat storage medium 50 at the bottom of the cavity 101 completes phase change first, under the pressure of the un-phase-changed solid phase change heat storage medium 50 at the upper end, the phase change heat storage medium 50 at the bottom comes into close contact with the first conveying section 23 and the second conveying section 33, reducing thermal resistance. Significant heat transfer also occurs between the phase change heat storage medium 50 within the layer, further improving heat exchange efficiency. After the phase change heat storage medium 50 completely becomes liquid and the temperature stabilizes, the charging process is completed, thus realizing one charging cycle.

[0084] Insulation process: After the first fluid fully transfers heat to the phase change heat storage medium 50, the thermal energy is stored in the heat storage and heat exchange device. The insulation layer 80 covering the outer surface of the shell component 10 can effectively prevent heat loss, ensuring that the thermal energy transferred from the first fluid to the phase change heat storage medium 50 during off-peak hours is supplied for daily use during peak hours with almost no loss.

[0085] Heat release process: The second fluid enters the second conveying section 33 through the second inlet 31 and flows along the second conveying section 33 to the second outlet 32. During this process, the second fluid comes into full contact with the phase change thermal storage medium 50 through the second conveying section 33, thereby allowing the heat stored in the phase change thermal storage medium 50 to be fully transferred to the second fluid within the second conveying section 33. Since the liquid phase change thermal storage medium 50 at the bottom first completes the phase change from liquid to solid, similar to the heat charging process, there is also significant heat transfer between the phase change thermal storage mediums 50 within the layer, further improving the heat exchange efficiency. After the phase change thermal storage medium 50 completely becomes solid and the temperature stabilizes, the heat release process is completed, thus realizing one heat release cycle.

[0086] On the other hand, this application also provides a heat pump system that includes the aforementioned heat storage and heat exchange device. Therefore, this heat pump system includes all the technical effects of the aforementioned heat storage and heat exchange device. Since the technical effects of the heat storage and heat exchange device have already been described in detail above, they will not be repeated here.

[0087] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0088] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0089] The above are merely preferred embodiments of this application and are not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A heat storage and heat exchange device, characterized in that, include: The shell component (10) has a cavity (101) filled with a phase change heat storage and heat exchange medium (50). A first conduit (20) is at least partially disposed in the cavity (101) for at least conveying a first fluid; The second conduit (30) is at least partially disposed in the cavity (101) for at least conveying the second fluid; The first pipe (20) and the second pipe (30) are at least partially intertwined.

2. The heat storage and heat exchange device according to claim 1, characterized in that, The first pipe (20) located in the cavity (101) is arranged in a spiral shape to form a spiral gap (201), and the second pipe (30) located in the cavity (101) is arranged in a spiral shape and embedded in the spiral gap (201).

3. The heat storage and heat exchange device according to claim 1, characterized in that, The first pipe (20) located in the cavity (101) and the second pipe (30) located in the cavity (101) are spirally wound into a long strip structure (40), and the long strip structure (40) is arranged to bend back and forth in the cavity (101).

4. The heat storage and heat exchange device according to claim 3, characterized in that, Along the direction from the bottom to the top of the cavity (101), the elongated structure (40) is repeatedly bent into multiple layers, and in each layer, the elongated structure (40) is repeatedly bent along the length or width direction of the shell component (10).

5. The heat storage and heat exchange device according to claim 1, characterized in that, The phase change thermal storage heat exchange medium (50) covers the outer surfaces of the first pipeline (20) and the second pipeline (30); and / or, The phase change heat storage and heat exchange medium (50) has a predetermined gap with the top of the cavity (101); The cavity (101) is further provided with at least one load-bearing plate (70), and the first pipe (20) and the second pipe (30) are both installed on the load-bearing plate (70); and / or, The outer surface of the housing component (10) is covered with an insulation layer (80); and / or, The housing component (10) includes a bottom shell (11) and a cover (12), the bottom shell (11) having the cavity (101), and the cover (12) covering the bottom shell (11) to seal the cavity (101).

6. The heat storage and heat exchange device according to claim 1, characterized in that, The cavity (101) is also provided with a plurality of heat-conducting fins (60), which are spaced apart along the length of the shell component (10) to divide the cavity (101) into a plurality of sub-chambers (102). Each sub-chamber (102) contains the phase change heat storage and heat exchange medium (50), and the first pipe (20) and the second pipe (30) pass through the heat-conducting fins (60).

7. The heat storage and heat exchange device according to claim 6, characterized in that, The heat-conducting fins (60) are provided with through holes (61), and the first pipe (20) and the second pipe (30) are provided in the through holes (61). The cross-sectional area of ​​the through holes (61) is greater than the sum of the cross-sectional areas of the first pipe (20) and the second pipe (30).

8. The heat storage and heat exchange device according to claim 7, characterized in that, The radius of the through hole (61) is R, the distance between the geometric center of the first pipe (20) and the geometric center of the second pipe (30) is D, and the radius of the outer diameter of the first pipe (20) or the second pipe (30) is r. R, D and r satisfy the relationship: 2R≥D+2r.

9. The heat storage and heat exchange device according to claim 1, characterized in that, The first pipeline (20) includes a first inlet (21), a first outlet (22) and a first conveying section (23). The first inlet (21) and the first outlet (22) are both located outside the housing component (10). The first conveying section (23) is connected between the first inlet (21) and the first outlet (22) and is located inside the cavity (101). The second pipeline (30) includes a second inlet (31), a second outlet (32), and a second conveying section (33). The second inlet (31) and the second outlet (32) are both located outside the housing component (10). The second conveying section (33) is connected between the second inlet (31) and the second outlet (32) and is located inside the cavity (101). The first inlet (21), the first outlet (22), the second inlet (31) and the second outlet (32) are all located on the same side of the housing component (10), and the first inlet (21) and the second inlet (31) are both located near the bottom of the cavity (101), and the first outlet (22) and the second outlet (32) are both located near the top of the cavity (101).

10. The heat storage and heat exchange device according to any one of claims 1 to 9, characterized in that, The distance D between the geometric center of the first pipe (20) and the geometric center of the second pipe (30) satisfies the following relationship: 15mm ≤ D ≤ 16mm; and / or, The radius r of the outer diameter of the first pipe (20) satisfies the following relationship: 4mm ≤ r ≤ 5mm; and / or, The radius r of the outer diameter of the second pipe (30) satisfies the following relationship: 4mm ≤ r ≤ 5mm; and / or, Along the radial direction of the first conduit (20), the wall thickness d1 of the first conduit (20) satisfies the relationship: 0.2mm ≤ d1 ≤ 0.4mm; and / or, Along the radial direction of the second conduit (30), the wall thickness d2 of the second conduit (30) satisfies the relationship: 0.2mm ≤ d2 ≤ 0.4mm; and / or, The cavity (101) has heat-conducting fins (60), and the heat-conducting fins (60) have through holes (61). The radius R of the through holes (61) satisfies the following relationship: 10mm ≤ R ≤ 14mm; and / or, The through hole (61) has a center line (611), and the line connecting the geometric center of the first pipe (20) and the geometric center of the through hole (61) is a first connecting line (90). The angle θ between the first connecting line (90) and the center line (611) satisfies the following relationship: 40°≤θ≤50°; and / or, Along the length of the housing component (10), the winding length L of the first conduit (20) and the second conduit (30) after winding satisfies the following relationship: 450mm ≤ L ≤ 550mm; and / or, The torsion angle φ of the spiral winding of the first pipe (20) and the second pipe (30) satisfies the following relationship: 1700°≤φ≤1900°; and / or, The cavity (101) has heat-conducting fins (60) inside, and the thickness t of the heat-conducting fins (60) along the length direction of the shell component (10) satisfies the following relationship: 0.05mm ≤ t ≤ 0.25mm; and / or, The cavity (101) has heat-conducting fins (60), and the heat-conducting fins (60) include multiple fins. Along the length direction of the shell component (10), the distance h between two adjacent heat-conducting fins (60) satisfies the following relationship: 1.0 mm ≤ h ≤ 4.5 mm; and / or, The cavity (101) is provided with a load-bearing plate (70). Along the length of the shell component (10), the thickness t1 of the load-bearing plate (70) satisfies the following relationship: 2mm≤t1≤4mm.

11. The heat storage and heat exchange device according to any one of claims 1 to 9, characterized in that, The cavity (101) is further provided with heat-conducting fins (60), the heat-conducting fins (60) including copper fins; and / or, The cavity (101) is further provided with a load-bearing plate (70), the load-bearing plate (70) comprising a stainless steel plate; and / or, The first conduit (20) includes a copper pipe; and / or, The second conduit (30) includes a copper pipe; and / or, The housing component (10) includes a stainless steel housing; and / or, The outer surface of the housing component (10) is covered with an insulation layer (80), the insulation layer (80) comprising a polyurethane layer; and / or, One of the first fluid and the second fluid is a refrigerant, and the other is water.

12. A heat pump system, characterized in that, The heat pump system includes the heat storage and heat exchange device according to any one of claims 1 to 11.

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