A refrigerant phase change heater and direct cooling system
By incorporating heating elements and toothed protrusions on the outer wall of the refrigerant pipe, the problem of insufficient heating circuit in the direct cooling solution at low temperatures is solved, achieving miniaturization and safety of the refrigerant phase change heater, and improving battery stability and lifespan.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- WUXI CONOWEI NEW ENERGY TECHNOLOGY CO LTD
- Filing Date
- 2025-06-10
- Publication Date
- 2026-05-26
AI Technical Summary
The direct cooling solution lacks a suitable heating circuit in low-temperature environments, which affects battery performance. Furthermore, existing heaters are bulky, have high wiring risks, and the refrigerant lubricating oil is prone to deterioration, affecting system safety and efficiency.
A refrigerant phase change heater is designed. By setting heating elements and toothed protrusions on the outer wall of the refrigerant pipe, the phase change heating of the refrigerant is achieved, avoiding direct contact between the heating elements and the refrigerant. By adopting a reasonable pipe diameter difference and interface design, the stability and safety of refrigerant flow are ensured.
It enables flexible adaptation to small units, avoids refrigerant and lubricant deterioration, reduces the risk of high-pressure leakage, improves the stable operation of batteries within a suitable temperature range, and enhances battery performance and lifespan.
Smart Images
Figure CN224288351U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of heat exchange equipment technology, and in particular to a refrigerant phase change heater and a direct cooling system. Background Technology
[0002] With the continuous development of new energy technologies, containerized energy storage systems are increasingly widely used in new energy, photovoltaic, and power station fields due to their advantages such as small footprint and convenient installation and transportation, and are highly favored by the new energy photovoltaic industry. For dedicated containerized energy storage systems, direct cooling solutions offer rapid cooling. In direct cooling systems, the refrigerant directly enters the battery cold plate to cool the battery. Compared to traditional indirect cooling methods, such as heat exchange through a coolant loop, direct cooling reduces intermediate heat transfer steps. The refrigerant is in direct contact with the battery, quickly removing the heat generated by the battery and achieving rapid cooling.
[0003] However, the direct cooling solution also has a significant problem: the lack of a suitable heating circuit. In low-temperature environments, battery performance is severely affected, such as increased internal resistance and reduced charge / discharge efficiency. In such cases, heating the battery is necessary to maintain its normal operating performance.
[0004] In direct-cooling systems, although liquid refrigerant heaters can be used to heat the refrigerant into a gas to heat the battery, these heaters are bulky and cannot be used in small units. Furthermore, direct contact between the heating rod and the refrigerant can lead to overheating and deterioration of the lubricating oil in the refrigerant. Additionally, the wiring for the heating rod must be routed from inside the unit, posing a risk of high-pressure refrigerant leaking into the environment along the wiring. Finally, as the refrigerant flows through the heater, the hydraulic diameter of the pipe changes significantly, resulting in high resistance and affecting overall system efficiency. Utility Model Content
[0005] This invention provides a refrigerant phase change heater and a direct cooling system, which solves the problem of the lack of a suitable heating circuit in existing energy storage battery packs by setting a heating component attached to the outer wall of the refrigerant pipe.
[0006] In a first aspect, this utility model provides a phase change refrigerant phase change heater, including: a refrigerant pipe, including a heating section and interfaces located at both ends of the heating section along the extending direction of the heating section;
[0007] Heating elements are evenly distributed on the outer wall of the heating section.
[0008] Optionally, the inner wall of the heating section is provided with a plurality of tooth-shaped protrusions evenly arranged along the circumference, the tooth-shaped protrusions extending along the extension direction of the heating section.
[0009] Optionally, the inner diameter of the interface is greater than or equal to the inner diameter of the heating section, and the absolute value of the difference between the inner diameter of the heating section and the inner diameter of the interface is less than a first threshold.
[0010] Optional, the heating element includes:
[0011] At least one heating element is provided, and the heating elements are evenly arranged along the outer wall of the heating section; the heating elements are used to heat the refrigerant in the heating section.
[0012] The structural component has its inner wall fitted into the heating section and is used to fix the heating element.
[0013] Optionally, the inner diameter of the heating section is 10-30mm, and the outer wall of the structural component has a square cross-section on the first plane; the first plane is perpendicular to the extension direction of the heating section.
[0014] Optionally, the inner diameter of the heating section is 25-50mm, and the outer wall of the structural component has a hexagonal cross-section on the first plane; the first plane is perpendicular to the extension direction of the heating section.
[0015] Optionally, the inner diameter of the heating section is 40-100mm, and the outer wall of the structural component has a circular cross-section on the first plane; the first plane is perpendicular to the extension direction of the heating section.
[0016] Optionally, the inner wall opening of the interface is provided with a flared bevel.
[0017] Optionally, the angle between the flared bevel and the outer wall of the interface is 30°.
[0018] Secondly, this utility model embodiment also provides a direct cooling system, which includes the refrigerant phase change heater mentioned in the first aspect.
[0019] This utility model provides a refrigerant phase change heater, comprising: a refrigerant pipe including a heating section and interfaces located at both ends of the heating section along its extension direction; and heating elements uniformly disposed on the outer wall of the heating section. Compared to liquid fluorine heaters, the refrigerant phase change heater provided by this utility model has a compact structure, avoiding the disadvantage of large size that prevents its application in small units, and can flexibly adapt to various specifications of direct cooling systems. Because the heating elements are disposed on the outer wall of the heating section, direct contact between the heating components and the refrigerant is avoided, eliminating the risk of overheating and deterioration of the lubricating oil in the refrigerant, and ensuring the stability and service life of the refrigerant. Simultaneously, its wiring method eliminates the need to extend it from inside the unit, reducing the risk of high-pressure refrigerant leakage into the environment along the wires, improving system safety, ensuring stable battery operation within a suitable temperature range, and improving battery performance and service life. Attached Figure Description
[0020] Figure 1 A schematic diagram of the structure of a refrigerant phase change heater provided in an embodiment of this utility model;
[0021] Figure 2A schematic diagram of the cross-section of the heating section of a refrigerant phase change heater in the first plane, provided for an embodiment of this utility model;
[0022] Figure 3 A schematic diagram of an interface provided for an embodiment of this utility model;
[0023] Figure 4 A structural schematic diagram of a cross-section of an interface on a first plane is provided for an embodiment of this utility model;
[0024] Figures 5-7 A schematic diagram of the cross-section of a refrigerant phase change heater in a first plane, provided for an embodiment of this utility model;
[0025] Figures 8-10 A schematic diagram of the cross-section of another refrigerant phase change heater provided in an embodiment of this utility model;
[0026] In the diagram: 100, refrigerant pipe; 101, heating section; 102, interface; 103, flared bevel; 200, heating element; 201, heating plate; 202, structural component. Detailed Implementation
[0027] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, not the entire structure.
[0028] Figure 1 This is a schematic diagram of the structure of a refrigerant phase change heater provided in an embodiment of the present invention. Figure 2 This is a schematic diagram of the cross-section of the heating section of a refrigerant phase change heater in the first plane, provided by an embodiment of the present invention. Figure 3 This is a schematic diagram of an interface provided in an embodiment of the present invention. The first plane is perpendicular to the extending direction of the heating section 101.
[0029] Specifically, such as Figures 1-3 As shown, the refrigerant phase change heater includes: a refrigerant pipe 100, including a heating section 101 and interfaces 102 located at both ends of the heating section 101 along the extending direction of the heating section 101;
[0030] Heating elements 200 are evenly distributed on the outer wall of heating section 101.
[0031] Specifically, during the battery pack heating process, the refrigerant in the refrigerant pipe 100 flows into the heating section 101 through an interface 102 at one end. The heating element 2001, located on the outer wall of the heating section 101, transfers heat to the liquid refrigerant inside the pipe by raising the pipe wall temperature. As heat is continuously input, the liquid refrigerant absorbs heat, and its temperature gradually rises. When the temperature reaches the boiling point of the refrigerant, the liquid refrigerant transforms into a gaseous state. The transformed gaseous refrigerant then flows out of the heating section 101 and is delivered to the battery through the interface 102 at the other end. In low-temperature environments, the gaseous refrigerant can efficiently release heat to the battery, providing the necessary heating for the battery, thereby ensuring stable operation of the battery within a suitable temperature range and improving battery performance and lifespan.
[0032] This utility model provides a refrigerant phase change heater, comprising: a refrigerant pipe including a heating section and interfaces located at both ends of the heating section along its extension direction; and heating elements uniformly disposed on the outer wall of the heating section. Compared to liquid fluorine heaters, the refrigerant phase change heater provided by this utility model has a compact structure, avoiding the disadvantage of large size that prevents its application in small units, and can flexibly adapt to various specifications of direct cooling systems. Because the heating elements are disposed on the outer wall of the heating section, direct contact between the heating components and the refrigerant is avoided, eliminating the risk of overheating and deterioration of the lubricating oil in the refrigerant, and ensuring the stability and service life of the refrigerant. Simultaneously, its wiring method eliminates the need to extend it from inside the unit, reducing the risk of high-pressure refrigerant leakage into the environment along the wires, improving system safety, ensuring stable battery operation within a suitable temperature range, and improving battery performance and service life.
[0033] Continue to refer to Figure 2 In an optional embodiment, the interior of the heating section 101 is provided with a plurality of tooth-shaped protrusions evenly arranged along the circumference, the tooth-shaped protrusions extending along the extension direction of the heating section 101.
[0034] Specifically, by setting toothed protrusions that are evenly distributed along the circumference and extend along the direction of the heating section 101, the contact area between the inner wall of the heating section 101 and the refrigerant is increased. In addition, the toothed protrusions strengthen the structural strength of the pipe body and reduce the probability of accidents such as pipe wall rupture due to excessive pressure.
[0035] In actual operation, the toothed protrusions create turbulence in the flowing refrigerant, thereby promoting greater mixing and friction within the refrigerant and accelerating the heat transfer process from the pipe wall to the refrigerant. Simultaneously, the toothed protrusions divide the flow channel into multiple regions, resulting in a more uniform refrigerant distribution within the pipe, preventing localized overheating or undercooling, further ensuring the stability and consistency of the refrigerant phase change process, and improving the overall performance and reliability of the refrigerant phase change heater.
[0036] Figure 4 A schematic diagram of the cross-section of an interface on a first plane is provided for an embodiment of this utility model, as shown below. Figure 4 As shown, in an optional embodiment, the inner diameter of the interface 102 is greater than or equal to the inner diameter of the heating section 101, and the absolute value of the difference between the inner diameters of the heating section 101 and the interface 102 is less than a first threshold.
[0037] The first threshold can be understood as the maximum allowable range of the difference between the inner diameter of the heating section 101 and the inner diameter of the interface 102. When it exceeds this range, it may lead to strong turbulence, vortices, and energy loss. For example, the magnitude of the first threshold is selected based on turbulence suppression conditions, pressure loss economic adjustment, and fluid continuity conditions, combined with the specific pipe diameter.
[0038] Specifically, the inner diameter of interface 102 is slightly larger than or equal to the inner diameter of heating section 101. Considering the thickness of the refrigerant pipe wall, when the refrigerant flows into the heating section from the interface, the inner diameter of the pipe increases slightly, and the slightly wider inner diameter will correspondingly reduce the flow velocity. This change in flow velocity helps the refrigerant to better absorb heat in the heating section, promoting the stable progress of the phase change process. At the same time, controlling the absolute value of the difference between the inner diameter of heating section 101 and interface 102 to be less than a first threshold can prevent the pipe diameter change from being too drastic. If the pipe diameter change is too large, the refrigerant will generate strong turbulence and vortices when flowing through this point, resulting in a significant increase in local resistance, consuming more energy, and thus sacrificing the overall efficiency of the machine.
[0039] This embodiment of the utility model, by reasonably setting the pipe diameter difference, makes the change in refrigerant flow rate more gradual, reduces unnecessary energy loss, ensures the smooth flow of refrigerant in the pipe, and thus avoids the problem of sacrificing the efficiency of the whole machine due to significant changes in the hydraulic diameter of the pipe and high resistance, thereby realizing the efficient and stable operation of the refrigerant phase change heater.
[0040] In an optional embodiment, the heating element 200 includes:
[0041] At least one heating element 201 is provided, and the heating elements 201 are evenly arranged along the outer wall of the heating section 101; the heating elements 201 are used to heat the refrigerant in the heating section 101.
[0042] Structural component 202, the inner wall of structural component 202 is in contact with heating section 101, and structural component 202 is used to fix heating element 201.
[0043] Specifically, the heating elements 201 are evenly arranged along the outer wall of the heating section 101 to ensure the uniformity of heating. When the heating elements 201 are powered on, the heat they generate can be transferred to the pipe wall of the heating section 101 in a relatively even manner, thereby making the refrigerant inside the pipe evenly heated and ensuring that the refrigerant rises steadily in the heating section 101 and successfully completes the phase change process.
[0044] The structural component 202 is tightly fitted to the heating section 101. On the one hand, it fixes the heating element 201 to the outer wall of the heating section 101, preventing the heating element 201 from shifting or falling off during refrigerant flow and system operation, and avoiding interference or damage from external environmental factors, thus extending the service life of the heating element 201. On the other hand, the structural component 202 can be made of heat-conducting materials such as aluminum to assist in heat conduction, allowing the heat generated by the heating element 201 to be transferred to the heating section 101 more efficiently, thereby improving the overall working efficiency of the heating element 200.
[0045] Figures 5-7 A schematic diagram of the cross-section of a refrigerant phase change heater in a first plane, provided for an embodiment of this utility model; Figures 8-10 This is a schematic diagram of the cross-section of a refrigerant phase change heater in a first plane, provided as an embodiment of the present invention. (Reference) Figures 5-7 This utility model embodiment provides three structural components 202 with different sizes and numbers of heating elements 201 arranged according to the inner diameter of the heating section 101, which can be adapted to direct cooling systems with different power requirements. (Reference) Figures 8-10 When the refrigerant flow rate is limited by the inner diameter of the pipe, this embodiment of the invention also provides a corresponding solution. Figures 5-7 Three types of toothed protrusion versions; on the one hand, the toothed protrusion strengthens the structural strength of the refrigerant pipe 100, making the pipe less prone to bursting; on the other hand, the thickness of the toothed protrusion can be reduced, and the depth relative to the center of symmetry of the refrigerant pipe 100 can be increased, acting as heat-conducting fins, increasing the heat exchange area and heat exchange efficiency of the refrigerant in the profile pipe.
[0046] refer to Figure 5 and Figure 8 In an optional embodiment, the inner diameter of the heating section 101 is 10-30 mm, and the outer wall of the structural member 202 has a square cross-section on the first plane; the first plane is perpendicular to the extension direction of the heating section 101.
[0047] Specifically, when the inner diameter of the heating section 101 is 10-30mm, the outer wall of the adapting structural component 202 has a square cross-section on the first plane perpendicular to the extension direction of the heating section 101. Under this design, a small number of relatively large heating elements 201 are evenly distributed inside the structural component 202 to meet the heating requirements of a smaller power for this inner diameter.
[0048] For example, if the direct cooling system is applied to a small energy storage battery pack, the battery heat generation rate is relatively low, and the heating power requirement is not high. In this case, the square outer wall design of structural component 202 can provide a more compact spatial layout, saving installation space. At the same time, if the environment in which the small energy storage battery pack is used is relatively cold, toothed protrusions can be provided inside the heating section 101 to increase the heat exchange area of the refrigerant in the pipe while enhancing the structural strength of the refrigerant pipe 100, ensuring that the refrigerant can fully absorb heat within the limited pipe diameter and achieve efficient phase change.
[0049] refer to Figure 6 and Figure 9 In an optional embodiment, when the inner diameter of the heating section 101 is 25-50mm, the outer wall of the structural member 202 has a hexagonal cross-section in the first plane; the first plane is perpendicular to the extension direction of the heating section 101.
[0050] Specifically, when the inner diameter of the heating section 101 is 25-50mm, the outer wall of the structural component 202 has a hexagonal cross-section on the first plane. For this inner diameter range, the number of heating elements 201 equipped in the structural component 202 is increased while their size is reduced to accommodate direct cooling systems with medium power requirements.
[0051] For example, when a direct cooling system is used in a medium-sized distributed energy storage device, the battery pack is large and the heat generation is complex, requiring a more stable and moderately powerful heating method. The hexagonal structural component 202 accommodates heating elements 201 with a larger total area and a more uniform distribution, ensuring that the refrigerant can be heated evenly and efficiently inside the pipe.
[0052] refer to Figure 7 and Figure 10 In an optional embodiment, the inner diameter of the heating section 101 is 40-100mm, and the outer wall of the structural member 202 has a circular cross-section on the first plane; the first plane is perpendicular to the extension direction of the heating section 101.
[0053] Specifically, when the inner diameter of the heating section 101 is 40-100mm, the cross-section of the outer wall of the structural component 202 on the first plane is circular. In this scenario, the structural component 202 has the largest number of heating elements 201, the smallest single element area, and the largest total heating area, which is used to meet the needs of high-power direct cooling systems.
[0054] For example, in the direct cooling system of a large-scale centralized energy storage power station, the battery pack is relatively large, requiring higher refrigerant heating power. The circular structural component 202's outer wall design can better distribute internal pressure, ensuring structural reliability. The ring-shaped heating elements 201 enable the refrigerant to quickly and uniformly absorb heat within the large-diameter pipe, completing an efficient phase change, ensuring the stable and efficient operation of the large-scale direct cooling system, and providing precise and stable temperature regulation for the battery.
[0055] Continue to refer to Figure 3 In an optional embodiment, the inner wall opening of the interface 102 is provided with a flared bevel 103.
[0056] Specifically, by providing a flared bevel 103 at the opening on the inner wall of interface 102, the flared bevel 103 provides better adaptability for the connection between interface 102 and external pipelines. During actual installation, construction personnel can more easily align the external pipeline with interface 102, and the guiding effect of the flared bevel 103 makes the pipeline connection more efficient.
[0057] In one specific embodiment, the included angle α between the flared bevel 103 and the outer wall of the interface 102 is 30°.
[0058] For example, sealing materials such as rubber sealing rings can also be installed at the external pipe position corresponding to the flared bevel 103. When the external pipe is connected to the interface 102, the flared bevel 103 can make the sealing material fit more tightly against the connection, enhance the sealing effect, ensure the stable and reliable refrigerant circulation of the direct cooling system, and improve the operational safety and stability of the entire system.
[0059] like Figure 1 As shown, this embodiment of the present invention also provides a direct cooling system, including a refrigerant phase change heater as described in the above embodiments. Since this direct cooling system includes the refrigerant phase change heater of any of the above embodiments, it possesses the same or corresponding beneficial effects as those described in the above embodiments, which will not be repeated here.
[0060] Note that the above description is merely a preferred embodiment of the present invention and the technical principles employed. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein, and various obvious changes, readjustments, combinations, and substitutions can be made without departing from the scope of protection of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments. Many other equivalent embodiments may be included without departing from the concept of the present invention, and the scope of the present invention is determined by the scope of the appended claims.
Claims
1. A phase-change refrigerant heater, characterized by comprising: include: The refrigerant pipe (100) includes a heating section (101) and interfaces (102) located at both ends of the heating section (101) along the extending direction of the heating section (101); Heating elements (200) are uniformly disposed on the outer wall of the heating section (101).
2. The phase-change refrigerant heater according to claim 1, wherein The inner wall of the heating section (101) is provided with a plurality of tooth-shaped protrusions evenly arranged along the circumference, and the tooth-shaped protrusions extend along the extension direction of the heating section (101).
3. The refrigerant phase change heater according to claim 1, characterized in that, The inner diameter of the interface (102) is greater than or equal to the inner diameter of the heating section (101), and the absolute value of the difference between the inner diameter of the heating section (101) and the inner diameter of the interface (102) is less than a first threshold.
4. The refrigerant phase change heater according to claim 1, characterized in that, The heating element (200) includes: At least one heating element (201) is provided, the heating element (201) being evenly arranged along the outer wall of the heating section (101); the heating element (201) is used to heat the refrigerant in the heating section (101); The structural component (202) has its inner wall in contact with the heating section (101) and is used to fix the heating element (201).
5. The refrigerant phase change heater according to claim 4, characterized in that, The inner diameter of the heating section (101) is 10-30 mm, and the outer wall of the structural member (202) has a square cross-section on the first plane; the first plane is perpendicular to the extension direction of the heating section (101).
6. The refrigerant phase change heater according to claim 4, characterized in that, The inner diameter of the heating section (101) is 25-50 mm, and the outer wall of the structural member (202) has a hexagonal cross-section on the first plane; the first plane is perpendicular to the extension direction of the heating section (101).
7. The refrigerant phase change heater according to claim 4, characterized in that, The inner diameter of the heating section (101) is 40-100mm, and the outer wall of the structural component (202) has a circular cross-section on the first plane; the first plane is perpendicular to the extension direction of the heating section (101).
8. The refrigerant phase change heater according to claim 1, characterized in that, The inner wall opening of the interface (102) is provided with a flared bevel (103).
9. The refrigerant phase change heater according to claim 8, characterized in that, The angle between the flared bevel (103) and the outer wall of the interface (102) is 30°.
10. A direct cooling system, characterized in that, Includes a refrigerant phase change heater as described in any one of claims 1-9.