Constant heat transfer power multi-channel heat sink and control method thereof

Abstract

The present application relates to the technical field of heat sink, in particular to a constant heat exchange power multi-channel heat sink and a control method thereof. The heat sink comprises hot flow channels and cold flow channels; the hot flow channels are arranged at intervals; hot fluid flows through the hot flow channels in turn by turning back; the cold flow channels are arranged at intervals; cold fluid flows through the cold flow channels in turn by turning back; the cold flow channels and the hot flow channels conduct heat alternately; the heat exchange area of the cold flow channels and the hot flow channels gradually increases along the flow direction of the cold fluid or the hot fluid. Thus, the problem that the heat dissipation power of the heat sink gradually decreases and cannot fully meet the high heat dissipation requirement of airborne equipment and the high power-to-weight ratio requirement in the aviation field is solved.

Description

Technical Field

[0001] This invention relates to the field of radiator technology, and more specifically, to a multi-channel radiator with constant heat exchange power and its control method. Background Technology

[0002] Current airborne high-power equipment operates for short periods and generates large amounts of waste heat instantaneously. This means that thermal management systems must not only cope with high-power heat loads but also mitigate the thermal shock caused by instantaneous peak heat loads, posing a significant challenge to the design of airborne equipment thermal management systems. High-power cooling equipment carried to meet the peak heat dissipation requirements of airborne equipment adds substantial extra weight during operational breaks. In the aerospace field, radiators, as core devices for energy transfer and conversion, directly affect heat storage and exchange efficiency through their structural design. Currently, most commercially available phase change thermal storage radiators employ relatively simple single-channel or dual-channel structures to achieve heat dissipation. These structures use independent and parallel fluid channels, allowing hot and cold fluids to flow within their respective channels, with the channel walls serving as the heat exchange medium to achieve heat transfer between the hot and cold fluids.

[0003] However, in actual heat exchange processes, the hot and cold fluids continuously exchange heat along the flow direction within the channel, causing the temperature difference between the hot and cold sides to gradually decrease as the flow distance increases. This affects the stability and efficiency of the overall heat exchange performance of the radiator. Summary of the Invention

[0004] To address the problem that the heat dissipation power of radiators is gradually decreasing and cannot fully meet the high heat dissipation requirements of airborne equipment and the technical requirements of high power-to-weight ratio in the aerospace field, this invention provides a multi-channel radiator with constant heat exchange power and its control method.

[0005] In a first aspect, this application provides a constant heat exchange power multi-channel radiator, the constant heat exchange power multi-channel radiator comprising:

[0006] A heat flow channel is provided at intervals; the hot fluid flows through the multiple heat flow channels in sequence by means of a folding back.

[0007] The system includes multiple cold flow channels spaced at intervals; cold fluid flows sequentially through these channels via a reversal mechanism; the multiple cold flow channels and multiple hot flow channels alternately conduct heat; and the heat exchange area between the cold flow channels and the hot flow channels gradually increases along the flow direction of the cold fluid or the hot fluid.

[0008] In some embodiments, both the hot flow channel and the cold flow channel are cylindrical; multiple hot flow channels and multiple cold flow channels are coaxially arranged; the hot flow channels and the cold flow channels are alternately nested; the cold fluid flows through multiple cold flow channels in sequence with gradually increasing diameter; the hot fluid flows through multiple hot flow channels in sequence with gradually increasing diameter; heat transfer occurs between adjacent cold flow channels and hot flow channels.

[0009] In some embodiments, the axial length of the cold flow channel is proportional to its diameter; the axial length of the hot flow channel is proportional to its diameter; and each hot flow channel corresponds to a cold flow channel with the same axial length.

[0010] In some embodiments, among the plurality of cold flow channels, the cold flow channel with a smaller diameter is located at the axial midpoint of the cold flow channel with a larger diameter;

[0011] Of the plurality of heat flow channels, the heat flow channel with the smaller diameter is located at the axial midpoint of the heat flow channel with the larger diameter.

[0012] In some embodiments, the constant heat exchange power multi-channel radiator further includes a phase change heat storage channel; the phase change heat storage channel is used to store phase change materials; the phase change heat storage channel is cylindrical; multiple phase change heat storage channels are coaxially arranged; the cold flow channel, the hot flow channel and the phase change heat storage channel are nested alternately in sequence.

[0013] In some embodiments, the constant heat exchange power multi-channel radiator further includes multiple partitions; the partitions are cylindrical; the cold flow channel, the hot flow channel, and the phase change heat storage channel are separated and heat transferred by the multiple partitions;

[0014] The structural dimensions of the radiator are calculated using the following formula:

[0015] W H =K HP ×2π(R) P +0.5ΔR P )×L×(T H -T P )+K HC ×2π(R) C +0.5ΔR C )×L×(T H -T C );

[0016] ;

[0017] ;

[0018] The structural dimensions include the radius of the phase change heat storage channel, the radius of the cold flow channel, and the axial length of the constant heat exchange power multi-channel radiator;

[0019] W H K represents the instantaneous heat release power of the heat fluid. HP R is the heat transfer coefficient from the heat flow channel to the phase change heat storage channel. P ΔR is the radius of the phase change heat storage channel; P R is the radial thickness of the phase change heat storage channel; C The radius of the cold flow channel is ΔR. C L is the radial thickness of the cold flow channel; T is the axial length of the constant heat exchange power multi-channel radiator; H T represents the instantaneous temperature of the thermal fluid. P T is the instantaneous temperature of the phase change material. C K represents the instantaneous temperature of the cold fluid. HC The heat transfer coefficient is the coefficient of heat transfer from the hot flow channel to the cold flow channel. The convective heat transfer coefficient of the hot fluid is... The convective heat transfer coefficient of the cold fluid is... The thermal conductivity of the partition is given. The thermal conductivity of the phase change material is given. The thickness of the partition is [missing information]. The radial thickness of the phase change heat storage channel is given.

[0020] In some embodiments, the cross-section of the cold flow channel is rectangular; the cross-sectional width of the plurality of cold flow channels is equal; and the cross-sectional length of the plurality of cold flow channels increases sequentially along the flow direction of the cold fluid.

[0021] The heat flow channel has a rectangular cross-section; the cross-sectional widths of the multiple heat flow channels are equal; and the cross-sectional lengths of the multiple heat flow channels increase sequentially along the flow direction of the heat fluid.

[0022] Secondly, this application provides a control method for a constant heat exchange power multi-channel radiator, applied to the constant heat exchange power multi-channel radiator as described in any one of the first aspects, the control method for the constant heat exchange power multi-channel radiator comprising:

[0023] In response to a heat dissipation command, the heat fluid controlling the heat load flows sequentially through multiple heat flow channels in order of increasing heat exchange area.

[0024] In response to the heat dissipation command, the cold fluid is controlled to flow sequentially through multiple cold flow channels in order of increasing heat exchange area;

[0025] Obtain the flow rate of the hot fluid within the heat flow channel;

[0026] The flow rate of the cold fluid in the cold flow channel is adjusted according to the flow rate of the hot fluid in the hot flow channel; the flow rate of the hot fluid in the hot flow channel is positively correlated with the flow rate of the cold fluid in the cold flow channel.

[0027] In some embodiments, the heat dissipation parameters of the constant heat exchange power multi-channel radiator are obtained; the heat dissipation parameters include the heat dissipation power density of the cold fluid;

[0028] Based on the heat dissipation parameters, the order and number of the cold fluid flowing through the multiple cold flow channels are adjusted, and the order and number of the hot fluid flowing through the multiple hot flow channels are adjusted, so as to change the increase gradient of the heat exchange area after each return of the cold fluid and the hot fluid; the increase gradient of the heat exchange area is positively correlated with the heat dissipation power density.

[0029] In some embodiments, the heat dissipation parameters further include the heat dissipation power requirement of the heat load; the increasing gradient of the heat exchange area is negatively correlated with the heat dissipation power requirement.

[0030] In some embodiments, the heat dissipation parameters further include the pump source pressures of the cold fluid and the hot fluid; the increasing gradient of the heat exchange area is negatively correlated with the pump source pressure.

[0031] To address the problem that the heat dissipation power of radiators is gradually decreasing and can no longer fully meet the high heat dissipation requirements of airborne equipment and the high power-to-weight ratio technical requirements of the aviation field, this invention has the following advantages:

[0032] By alternating the conduction of heat through multiple cold flow channels and multiple hot flow channels, and by gradually increasing the heat exchange area of ​​the cold flow channels and hot flow channels along the flow direction of the cold or hot fluid, the heat exchange area is inversely proportional to the temperature difference. This allows for targeted control of the heat exchange characteristics of the radiator, thereby enabling the heat exchange power of the entire radiator to reach a state of near constancy along the flow direction. This solves the problem in existing technologies where the heat dissipation power of radiators gradually decreases, making it difficult to fully meet the high heat dissipation requirements of airborne equipment and the high power-to-weight ratio technical requirements of the aviation field. Attached Figure Description

[0033] Figure 1 A schematic diagram of a constant heat exchange power multichannel radiator according to one embodiment is shown;

[0034] Figure 2 It shows Figure 1 Top view of a multi-channel radiator with constant heat exchange power;

[0035] Figure 3 A simplified diagram of the multi-channel flow direction in a multi-channel radiator with constant heat exchange power is shown.

[0036] Figure 4 A simplified diagram of a multi-channel radiator with constant heat exchange power and cylindrical multi-channels is shown.

[0037] Figure 5 A simplified diagram of a rectangular multichannel radiator with constant heat exchange power is shown.

[0038] Figure 6 A flowchart illustrating a method for manufacturing a constant heat exchange power multichannel radiator according to one embodiment is shown.

[0039] Reference numerals: radiator 10; cold flow channel 11; hot flow channel 12; phase change heat storage channel 13; partition 14. Detailed Implementation

[0040] The present disclosure will now be discussed with reference to several exemplary embodiments. It should be understood that these embodiments are discussed only to enable those skilled in the art to better understand and thus implement the present disclosure, and are not intended to imply any limitation on the scope of the disclosure.

[0041] As used herein, the term "comprising" and its variations are to be interpreted as open-ended terms meaning "including but not limited to". The term "based on" is to be interpreted as "at least partially based on". The terms "one embodiment" and "an embodiment" are to be interpreted as "at least one embodiment". The term "another embodiment" is to be interpreted as "at least one other embodiment". The terms "upper", "lower", "left", "right", "front", "rear", "top", "bottom", "inner", "outer", "vertical", "horizontal", "lateral", "longitudinal", etc., indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. These terms are primarily for the purpose of better describing this application and its embodiments and are not intended to limit the indicated devices, elements, or components to having a specific orientation or being constructed and operated in a specific orientation. Furthermore, some of the above terms may be used to indicate other meanings besides orientations or positional relationships; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in this application according to the specific circumstances. In addition, the terms "installed", "set up", "equipped with", "connected", and "linked" should be interpreted broadly. For example, it can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or an internal connection between two devices, elements, or components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances. Furthermore, the terms "first," "second," etc., are mainly used to distinguish different devices, elements, or components (the specific types and structures may be the same or different), and are not used to indicate or imply the relative importance or quantity of the indicated devices, elements, or components. Unless otherwise stated, "a plurality of" means two or more.

[0042] As a core device for energy transfer and conversion, the structural design of radiators directly affects their heat storage and exchange efficiency. Currently, most commercially available phase change thermal energy storage radiators employ relatively simple single-channel or dual-channel structures to achieve heat dissipation. These structures use independent, parallel fluid channels, allowing hot and cold fluids to flow within their respective channels, with the channel walls serving as the heat exchange medium. However, in actual heat exchange, the continuous heat exchange between the hot and cold fluids along the flow direction within the channels causes the temperature difference between the hot and cold sides to gradually decrease with increasing flow distance. This affects the stability and efficiency of the overall heat exchange performance of the radiator.

[0043] Example 1:

[0044] In this embodiment, to solve the above problems, this application provides a constant heat exchange power multi-channel radiator 10, such as... Figure 1 , Figure 2 As shown, the constant heat exchange power multi-channel radiator 10 includes a hot flow channel 12 and a cold flow channel 11.

[0045] Multiple hot flow channels 12 are spaced apart, and the hot fluid flows through multiple hot flow channels 12 sequentially through a zigzag pattern. Multiple cold flow channels 11 are spaced apart, and the cold fluid flows through multiple cold flow channels 11 sequentially through a zigzag pattern. The multiple cold flow channels 11 and multiple hot flow channels 12 alternately conduct heat, which can increase the overall heat exchange contact range and improve the basic heat exchange efficiency.

[0046] Figure 3 A simplified schematic diagram shows the flow of hot fluid in hot flow channel 12 and cold fluid in cold flow channel 11. When the cold and hot fluids first come into contact, the temperature difference between them is large, resulting in a high heat exchange power. However, as the temperature difference gradually decreases after heat exchange, the heat exchange power also decreases, meaning the heat exchange capacity gradually weakens along the flow direction. Therefore, this application gradually increases the heat exchange area of ​​cold flow channel 11 and hot flow channel 12 along the flow direction of the cold or hot fluid. This matches the gradual temperature change of the hot and cold fluids during flow, and by increasing the heat exchange area, the heat exchange power remains constant, thereby achieving dynamic adaptation of the heat exchange process, ensuring its stability, and meeting the heat dissipation requirements of airborne equipment during operation.

[0047] Furthermore, such as Figure 2 As shown, both the hot flow channel 12 and the cold flow channel 11 are cylindrical. The cylindrical structure provides good structural stability, facilitates uniform flow of hot and cold fluids, and reduces flow resistance. Multiple hot flow channels 12 and multiple cold flow channels 11 are coaxially arranged, with the hot flow channels 12 and cold flow channels 11 alternately nested to ensure uniform heat exchange distance between adjacent channels, thus improving heat exchange uniformity. The cold fluid flows through multiple cold flow channels 11 in a gradually increasing diameter order, while the hot fluid flows through multiple hot flow channels 12 in a gradually increasing diameter order. This allows for smoother pressure changes during fluid flow, and the contact area between the hot and cold fluids gradually increases with the flow direction. Simultaneously, the heat transfer between adjacent cold flow channels 11 and hot flow channels 12 further optimizes the heat exchange path, ensuring a constant heat exchange power of the radiator. The cylindrical radiator 10, while satisfying the gradually changing heat exchange area, also has a relatively regular shape, facilitating standardized size and shape design, reducing costs, and improving versatility.

[0048] Furthermore, such as Figure 4As shown, the axial length of the cold flow channel 11 is proportional to its diameter, and the axial length of the hot flow channel 12 is also proportional to its diameter. When the cold and hot fluids first come into contact, the temperature difference between them is large. By shortening the axial length, the heat exchange power is prevented from decreasing too quickly. As the temperature difference gradually decreases after heat exchange, the rate of heat exchange power reduction slows down, and the axial length increases accordingly, thereby increasing the heat exchange area between the hot and cold fluids and ensuring that the heat exchange power remains relatively constant along the radial flow direction. Each hot flow channel 12 corresponds to a cold flow channel 11 of the same axial length, ensuring that each set of cold flow channels 11 and hot flow channels 12 has symmetrical heat exchange conditions. This allows for uniform heat exchange, reducing local overheating or insufficient heat exchange, thereby improving the stability of the heat exchange performance of the radiator 10 and helping to meet the heat dissipation requirements of airborne equipment.

[0049] Furthermore, such as Figure 4 As shown, among the multiple cold flow channels 11, the smaller diameter cold flow channel 11 is located at the axial center of the larger diameter cold flow channel 11. Similarly, among the multiple hot flow channels 12, the smaller diameter hot flow channel 12 is located at the axial center of the larger diameter hot flow channel 12. Since the hot and cold fluids need to make multiple turns during flow, placing the shorter axially long cold flow channel 11 at the axial center of the larger diameter cold flow channel 11 ensures that the difference in turn path length and angle during each turn is smaller, minimizing significant fluctuations in flow resistance and facilitating standardized design.

[0050] Furthermore, such as Figure 2 As shown, the constant heat exchange power multi-channel radiator 10 also includes a phase change heat storage channel 13. The phase change heat storage channel 13 is used to store phase change materials. The phase change heat storage channel 13 utilizes the phase change of the phase change material to store and release heat. When the heat load power fluctuates, the phase change material can absorb or release heat, helping to maintain the stability of the heat exchange power. The phase change heat storage channel 13 is cylindrical. The cylindrical structure and coaxial arrangement facilitate installation with the cold flow channel 11 and the hot flow channel 12. Multiple phase change heat storage channels 13 are coaxially arranged, with the cold flow channel 11, hot flow channel 12, and phase change heat storage channel 13 arranged alternately and nested, thereby maximizing the contact area between the phase change heat storage channel 13 and the cold flow channel 11 and hot flow channel 12 respectively, improving heat transfer efficiency, and enabling the radiator 10 to meet the heat dissipation requirements of airborne equipment.

[0051] Furthermore, the constant heat exchange power multi-channel radiator 10 also includes multiple baffles 14. The baffles 14 are cylindrical, and the cold flow channel 11, hot flow channel 12, and phase change heat storage channel 13 are separated and heat transferred through the multiple baffles 14. The cylindrical baffles 14 effectively separate different types of channels, preventing fluid mixing, and also possess good thermal conductivity, ensuring smooth heat transfer between channels. The radial thickness of the baffles 14 should be as thin as possible to reduce thermal resistance.

[0052] The structural dimensions of the heat sink 10 are calculated using the following formula:

[0053] W H =K HP ×2π(R) P +0.5ΔR P )×L×(T H -T P )+K HC ×2π(R) C +0.5ΔR C )×L×(T H -T C );

[0054] ;

[0055] ;

[0056] The structural dimensions include the radius of the phase change heat storage channel 13, the radius of the cold flow channel 11, and the axial length of the constant heat exchange power multi-channel radiator 10.

[0057] W H K represents the instantaneous heat release power of the hot fluid. HP R is the heat transfer coefficient from heat flow channel 12 to phase change heat storage channel 13; P The radius of phase change heat storage channel 13 is ΔR. P R represents the radial thickness of the phase change heat storage channel 13. C The radius of the cold flow channel 11; ΔR C L is the radial thickness of the cold flow channel 11; L is the axial length of the constant heat exchange power multi-channel radiator 10; T H T represents the instantaneous temperature of the hot fluid. P T represents the instantaneous temperature of the phase change material. C K represents the instantaneous temperature of the cold fluid. HC The heat transfer coefficient is given from the hot flow channel 12 to the cold flow channel 11. The convective heat transfer coefficient of the hot fluid is denoted as . The convective heat transfer coefficient of the cold fluid is... The thermal conductivity of partition 14 is... The thermal conductivity of the phase change material is... The thickness of partition 14, The radial thickness of phase change heat storage channel 13. To ensure K... HP K HC ΔR P ΔR C Assuming L remains constant, according to T H T P and T C Thus, the heat exchange temperature difference, T, is obtained. H -T P and T H -T C Secondly, to ensure that the heat dissipation power of the heat load always exceeds the heat dissipation requirements of the airborne equipment, the minimum radius of the phase change heat storage channel 13 and the radius of the cold flow channel 11 can be obtained according to the aforementioned heat transfer power formula. Each channel is designed in this way, resulting in the detailed dimensions of the final radiator 10. This makes the radiator 10 structural design more scientific and targeted. Through this precise design, the heat transfer power of the radiator 10 can be kept constant or increased or decreased to meet the heat dissipation requirements of the airborne equipment during operation.

[0058] Furthermore, such as Figure 5 As shown, the cross-section of the cold flow channel 11 is rectangular, the cross-sectional width of the multiple cold flow channels 11 is equal, and the cross-sectional length of the multiple cold flow channels 11 increases sequentially along the flow direction of the cold fluid.

[0059] The hot flow channel 12 has a rectangular cross-section, and multiple hot flow channels 12 have equal cross-sectional widths. The cross-sectional lengths of the multiple hot flow channels 12 increase sequentially along the flow direction of the hot fluid. The cross-sectional lengths of the hot flow channel 12 and the cold flow channel 11 increase sequentially along the flow direction of the cold or hot fluid, resulting in a gradual increase in the heat exchange area. This ensures that the heat changes during the flow of the cold and hot fluids are matched, guaranteeing efficient heat exchange throughout the entire process of temperature changes in the hot and cold fluids, thereby meeting the heat dissipation requirements of airborne equipment.

[0060] Example 2:

[0061] In this embodiment, this application provides a method for manufacturing a constant heat transfer power multi-channel radiator 10, applied to the constant heat transfer power multi-channel radiator 10 of Embodiment 1, such as... Figure 6 As shown, the constant heat exchange power multi-channel radiator 10 includes steps S10 to S40.

[0062] Step S10: In response to the heat dissipation command, the heat fluid of the heat load is controlled to flow through multiple heat flow channels 12 in order of increasing heat exchange area, so that the heat flow channel 12 with smaller heat exchange area gradually transitions to the larger channel, adapting to the gradual change of heat fluid temperature and improving the adequacy of heat exchange.

[0063] Step S20: In response to the heat dissipation command, the cold fluid is controlled to flow through multiple cold flow channels 11 in order of increasing heat exchange area, so that the cold flow channel 11 with smaller heat exchange area is matched with the hot flow channel 12, and gradually transitions to the larger channel, adapting to the process of gradual change of cold fluid temperature and improving the adequacy of heat exchange.

[0064] Step S30: Obtain the flow rate of the hot fluid in the heat flow channel 12.

[0065] Step S40: Adjust the flow rate of the cold fluid in the cold flow channel 11 according to the flow rate of the hot fluid in the hot flow channel 12. The flow rate of the hot fluid in the hot flow channel 12 is positively correlated with the flow rate of the cold fluid in the cold flow channel 11, so as to achieve dynamic matching of the flow rates of the cold fluid and the hot fluid, avoid insufficient heat exchange or energy waste caused by flow mismatch, ensure stable heat exchange power, and thus meet the heat dissipation requirements of the airborne equipment.

[0066] Furthermore, the manufacturing method of the constant heat exchange power multi-channel radiator 10 also includes steps S50 and S60. The manufacturing method of the constant heat exchange power multi-channel radiator 10 sequentially executes steps S10, S20, S30, S40, S50, and S60. Steps S50 and S60 will be described in detail below:

[0067] Step S50: Obtain the heat dissipation parameters of the constant heat exchange power multi-channel radiator 10, including the heat dissipation power density of the cold fluid, and keep track of the real-time heat exchange conditions of the radiator 10.

[0068] Step S60: Based on the heat dissipation parameters, adjust the order and number of cold fluid flowing through multiple cold flow channels 11, and adjust the order and number of hot fluid flowing through multiple hot flow channels 12 to change the gradient of heat exchange area increase after each return of the cold and hot fluids. The gradient of heat exchange area increase is positively correlated with the heat dissipation power density. The heat dissipation power density is closely related to the rate of heat exchange power reduction. When the heat dissipation power density of the cold fluid is large, the heat exchange power density decreases faster along the flow direction. In this embodiment, by increasing the gradient of heat exchange area increase, the rate of change of heat exchange area is positively correlated with the heat exchange temperature difference, thereby achieving a design that makes the heat exchange power tend to be constant.

[0069] Furthermore, the heat dissipation parameters also include the heat dissipation power requirement of the heat load, and the increase gradient of the heat exchange area is negatively correlated with the heat dissipation power requirement. When the heat load heat dissipation power requirement is high, the increase gradient of the heat exchange area is reduced, so that the overall heat exchange area of ​​the cold fluid and hot fluid in the radiator 10 is larger, thereby achieving sufficient heat dissipation. When the heat dissipation power requirement is low, some cold fluid channels or hot fluid channels can be skipped to increase the increase gradient of the heat exchange area. This skipping flow method can greatly alleviate the flow resistance in the backflow process and help extend the service life of the driving source such as the cooling pump matched with the radiator 10.

[0070] Furthermore, the heat dissipation parameters also include the pump source pressures of the cold and hot fluids; the increase gradient of the heat exchange area is negatively correlated with the pump source pressure. Based on the pump source pressures of the cold and hot fluids, the control method can be more comprehensively adapted to the operating conditions of the radiator 10. The increase gradient of the heat exchange area is negatively correlated with the pump source pressure. When the pump source pressure is high, the fluid flow momentum is sufficient, and a smaller increase gradient of the heat exchange area is enough to ensure smooth fluid flow in each channel and achieve efficient heat exchange. When the pump source pressure is low, a larger increase gradient of the heat exchange area can reduce fluid flow resistance, ensuring that the fluid can flow smoothly through each channel to complete heat exchange, avoiding heat exchange interruption due to insufficient pressure, ensuring the stable operation of the radiator 10's heat exchange function, and meeting the heat dissipation requirements of airborne equipment.

[0071] If the pump source pressure of the hot or cold fluid is insufficient to overcome the resistance loss caused by the flow along the channel, i.e., the pump source pressure is less than the total flow resistance, a bouncy flow measure can be adopted. However, in this case, the heat exchange area is also reduced by a factor of two. The total flow resistance consists of the resistance of the cold fluid in the cold flow channel 11 and the resistance of the hot fluid in the hot flow channel 12.

[0072] When the pump source pressure is greater than the total flow resistance and the total heat dissipation power is greater than or equal to the heat dissipation demand, skipping flow is not performed. When the pump source pressure is less than or equal to the total flow resistance but less than twice the pump source pressure and the total heat dissipation power is greater than or equal to twice the heat dissipation demand, one flow channel is skipped during the reversal. Since the heat dissipation power is much greater than the demand, one flow channel can be skipped during the reversal to reduce the flow resistance of the hot and cold fluids, ensuring that the pump source pressure is sufficient to deliver the cold and hot fluids to the end of the corresponding channels while also ensuring the heat exchange quality of the radiator 10. When twice the pump source pressure is less than or equal to the total flow resistance but less than three times the pump source pressure and the total heat dissipation power is greater than or equal to three times the heat dissipation demand, two flow channels are skipped during the reversal. When n times the pump source pressure is less than or equal to the total flow resistance but less than n+1 times the pump source pressure and the total heat dissipation power is greater than or equal to n+1 times the heat dissipation demand, n flow channels are skipped during the reversal.

[0073] Those skilled in the art will understand that the above embodiments are specific examples of implementing this disclosure, and in practical applications, various changes can be made in form and detail without departing from the scope of this disclosure.

Claims

1. A multi-channel radiator with constant heat exchange power, characterized in that, The constant heat exchange power multi-channel radiator includes: A heat flow channel is provided at intervals; the hot fluid flows through the multiple heat flow channels in sequence by means of a folding back. The system includes multiple cold flow channels spaced at intervals; cold fluid flows sequentially through multiple cold flow channels via a zigzag process; the multiple cold flow channels and multiple hot flow channels alternately conduct heat; the heat exchange area between the cold flow channels and the hot flow channels gradually increases along the flow direction of the cold fluid or the hot fluid. Both the hot flow channel and the cold flow channel are cylindrical; multiple hot flow channels and multiple cold flow channels are coaxially arranged; the hot flow channels and the cold flow channels are alternately nested; the cold fluid flows through multiple cold flow channels in order of gradually increasing diameter; the hot fluid flows through multiple hot flow channels in order of gradually increasing diameter; heat transfer occurs between adjacent cold flow channels and hot flow channels.

2. The constant heat exchange power multi-channel radiator according to claim 1, characterized in that, The axial length of the cold flow channel is proportional to its diameter; the axial length of the hot flow channel is proportional to its diameter; each hot flow channel corresponds to a cold flow channel with the same axial length.

3. A constant heat exchange power multi-channel radiator according to claim 2, characterized in that, Of the plurality of cold flow channels, the cold flow channel with the smaller diameter is located at the axial center of the cold flow channel with the larger diameter; Of the plurality of heat flow channels, the heat flow channel with the smaller diameter is located at the axial midpoint of the heat flow channel with the larger diameter.

4. A constant heat exchange power multi-channel radiator according to claim 1, characterized in that, The constant heat exchange power multi-channel radiator also includes a phase change heat storage channel; the phase change heat storage channel is used to store phase change materials; the phase change heat storage channel is cylindrical; multiple phase change heat storage channels are coaxially arranged; the cold flow channel, the hot flow channel and the phase change heat storage channel are nested alternately in sequence.

5. A constant heat exchange power multi-channel radiator according to claim 4, characterized in that, The constant heat exchange power multi-channel radiator also includes multiple partitions; the partitions are cylindrical; the cold flow channel, the hot flow channel, and the phase change heat storage channel are separated and heat transferred by the multiple partitions; The structural dimensions of the radiator are calculated using the following formula: W H =K HP ×2π(R P +0.5ΔR P )×L×(T H -T P )+K HC ×2π(R C +0.5ΔR C )×L×(T H -T C ); ； ； The structural dimensions include the radius of the phase change heat storage channel, the radius of the cold flow channel, and the axial length of the constant heat exchange power multi-channel radiator; W H K represents the instantaneous heat release power of the heat fluid. HP R is the heat transfer coefficient from the heat flow channel to the phase change heat storage channel. P ΔR is the radius of the phase change heat storage channel; P R is the radial thickness of the phase change heat storage channel; C The radius of the cold flow channel is ΔR. C L is the radial thickness of the cold flow channel; T is the axial length of the constant heat exchange power multi-channel radiator; H T represents the instantaneous temperature of the thermal fluid. P T is the instantaneous temperature of the phase change material. C K represents the instantaneous temperature of the cold fluid. HC The heat transfer coefficient is the coefficient of heat transfer from the hot flow channel to the cold flow channel. The convective heat transfer coefficient of the hot fluid is... The convective heat transfer coefficient of the cold fluid is... The thermal conductivity of the partition is given. The thermal conductivity of the phase change material is given. The thickness of the partition is [missing information]. The radial thickness of the phase change heat storage channel is given.

6. A control method for a multi-channel radiator with constant heat exchange power, applied to the multi-channel radiator with constant heat exchange power as described in any one of claims 1-5, characterized in that, The control method includes: In response to a heat dissipation command, the heat fluid controlling the heat load flows sequentially through multiple heat flow channels in order of increasing heat exchange area. In response to the heat dissipation command, the cold fluid is controlled to flow sequentially through multiple cold flow channels in order of increasing heat exchange area; Obtain the flow rate of the hot fluid within the heat flow channel; The flow rate of the cold fluid in the cold flow channel is adjusted according to the flow rate of the hot fluid in the hot flow channel; the flow rate of the hot fluid in the hot flow channel is positively correlated with the flow rate of the cold fluid in the cold flow channel.

7. The control method for a multi-channel radiator with constant heat exchange power according to claim 6, characterized in that, The control method further includes: Obtain the heat dissipation parameters of the constant heat exchange power multi-channel radiator; the heat dissipation parameters include the heat dissipation power density of the cold fluid; Based on the heat dissipation parameters, the order and number of the cold fluid flowing through the multiple cold flow channels are adjusted, and the order and number of the hot fluid flowing through the multiple hot flow channels are adjusted, so as to change the increase gradient of the heat exchange area after each return of the cold fluid and the hot fluid; the increase gradient of the heat exchange area is positively correlated with the heat dissipation power density.

8. The control method for a multi-channel radiator with constant heat exchange power according to claim 7, characterized in that, The heat dissipation parameters also include the heat dissipation power requirement of the heat load; the increasing gradient of the heat exchange area is negatively correlated with the heat dissipation power requirement.

9. The control method for a multi-channel radiator with constant heat exchange power according to claim 7, characterized in that, The heat dissipation parameters also include the pump source pressures of the cold fluid and the hot fluid; the increase gradient of the heat exchange area is negatively correlated with the pump source pressure.

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