Three-dimensional heat sink device

Abstract

This invention relates to a three-dimensional heat-absorbing device for absorbing heat transferred from an external heat source, thereby suppressing a temperature rise in the heat source. The three-dimensional heat-absorbing device includes: an airtight component defining the appearance of the device; a first space interconnected within the airtight component in a three-dimensional grid structure; and a second space forming a space not occupied by the first space within the internal space of the airtight component. One of the first and second spaces forms a channel for vaporizing a working fluid, and a core for absorbing liquefied working fluid is disposed along the inner surface of the channel. The other of the first and second spaces is filled with the core. The shape of the channel formed in one of the first and second spaces is defined by the core filled in the other space, and a phase-change working fluid can pass through the boundary between the first and second spaces.

Description

[0001] This invention is a divisional application of the invention application with application number 201580084499.1, entitled "Three-dimensional heat absorption device", filed on November 12, 2015. Technical Field

[0002] This invention relates to a heat-absorbing device that absorbs heat transferred from an external heat source to suppress the temperature rise of the heat source. Background Technology

[0003] Typically, in various products including electronic components (e.g., semiconductors), the heat generated during operation needs to be effectively dissipated to the outside to avoid performance degradation. Among related technologies, heat pipes are widely known as a highly effective means of transferring heat generated by a heat source to other locations. Amir Faghri's paper discloses the operating principles and development status of such heat pipes (Amir Faghri, Review and Advances in Heat Pipe Science and Technology, ASME Journal of HeatTransfer, Vol. 134, pp. 123001-1-18, 2012).

[0004] Figure 1 The structure of a conventional heat pipe is shown. Figure 1 A is a longitudinal sectional view of the heat pipe. Figure 1 B is a cross-sectional view of the heat pipe. Figure 1 The linear heat pipe 1 includes a long, cylindrical, hermetically sealed container 11 and a porous core 14 formed on the inner wall of the hermetically sealed container 11. The core 14 is immersed in a liquefied working fluid, and a channel 12 through which the gaseous working fluid, undergoing a phase change due to heat, passes is formed inside the core 14. The internal space of the hermetically sealed container 11 is longitudinally divided from the left side of the figure into an evaporation section A, an insulation section B, and a condensation section C. The working fluid evaporates in the core 14 of the evaporation section A to absorb heat through heat transferred from an external heat source (not shown). As a result, the pressure in the channel 12 increases, causing the gaseous working fluid to move to the condensation section. The gaseous working fluid reaching the opposite condensation section condenses into a liquid working fluid to release heat, is drawn into the core 14 in the condensation section, and then flows back to the evaporation section A along the core 14 by capillary action. The heat generated by the external heat source can be effectively absorbed and transferred through a cyclic process including the evaporation, condensation, and movement of the working fluid.

[0005] Meanwhile, flat heat pipes that utilize the heat transfer principle of such linear heat pipes are also known. For example, Figure 2A shows an example of a flat heat pipe used as the core, because the gap between the upper and lower surfaces of the middle member 24 is smaller than that between the lower member 21 (Novel Concepts, Inc. http: / / www.novelconceptsinc.com / ). Figure 2 B shows an example where the channel for the working fluid is an open, flat heat pipe (Celsia Inc. http: / / celsiainc.com / vapor-chamber-one-piece-design / ). Figure 2 A and Figure 2 The flat heat pipe of type B is an example designed for cooling products that transfer small amounts of heat (e.g., electronic components), and its thickness can be as thin as 1 mm. Figure 2 Like B, Figure 2 C illustrates an example of a flat heat pipe used when a large amount of heat transfer is required, such as in the jet deflector of a jet aircraft, like... Figure 2 Similar to B, the channels for the working fluid are opened (DT Queheillalt, G. Carbajal, GP Peterson, HNG Wadley, International Journal of Heat and Mass Transfer, Vol. 51, pp. 312-326, 2008). Such flat heat pipes, applied beneath the plate, are also referred to as radiators in the sense that the heat applied is transferred throughout the entire area.

[0006] Figure 1 and Figure 2 The conventional linear or flat heat pipes shown have various advantages: they have a simple structure, can operate even under small temperature gradients, have a fast response speed, and the heating and cooling units can be separated from each other, or their functions can be switched. Therefore, linear or flat heat pipes have been widely used in various fields.

[0007] However, with respect to traditional linear or flat heat pipes, due to their low calorie transfer capacity and lack of consideration for heat storage beyond simple heat transfer, a separate forced cooling device (e.g., a fan) is necessary to maintain functionality when excess heat is absorbed. This separate forced cooling device requires additional energy consumption and generates noise, and the external volume of the heat pipe is excessively increased to achieve adequate natural cooling without forced cooling. Furthermore, the limited heat transfer direction of linear or flat heat pipes restricts the design of products incorporating them. Therefore, despite the aforementioned advantages of traditional linear or flat heat pipes, their application range is limited.

[0008] Meanwhile, in recent years, so-called phase change materials (PCMs) (e.g., ice packs), which absorb or release a large amount of latent heat during the phase transition between the solid and liquid phases, have attracted attention as heat storage devices. However, since such PCMs typically have low thermal conductivity, it has been learned that more efficient heat storage performance can be achieved compared to products used simultaneously filled in porous metal structures with high thermal conductivity (KJKang, Progress in Materials Science, Vol. 69, pp. 213-307, 2015). Heat storage devices based on such PCMs are also excellent heat absorption devices. Even when heat is applied from the outside, the temperature does not rise as long as the phase transition from solid to liquid continues. However, when the phase transition is complete, the heat storage performance is lost due to latent heat, thus lacking performance retention characteristics as a heat absorption device. Summary of the Invention

[0009] Technical issues

[0010] The present invention provides a heat-absorbing device with a compact and robust structure, which has a high heat transfer rate and high heat capacity, and therefore can operate at a constant rate.

[0011] Technical solution

[0012] The inventors of this invention have discovered that in developing a heat-absorbing device that can operate at a constant rate and has a compact structure without the need for conventional forced cooling, it is necessary to provide heat storage performance while increasing the heat transfer rate. Therefore, the inventors of this invention have expanded or diversified the heat transfer system of the device in three dimensions, imparting heat storage performance to a portion of the diversified heat transfer system as needed, and embodying these aspects, thereby obtaining the present invention. The understanding of the above-mentioned problems and the subject matter of the invention based on this understanding will be described below.

[0013] (1) The three-dimensional heat absorption device may include an airtight component defining the appearance of the three-dimensional heat absorption device, a first space connected in a three-dimensional grid structure inside the airtight component, and a second space forming a space not occupied by the first space in the internal space of the airtight component, wherein at least one of the first space and the second space forms a channel for working fluid vapor, and a core for absorbing liquefied working fluid is provided along the inner surface of the channel.

[0014] (2) At least one of the first space and the second space may be filled with a core, and the phase change working fluid may move in the boundary between the first space and the second space.

[0015] (3) The boundary between the first space and the second space can be formed by walls.

[0016] (4) The core can be disposed on the inner surface of the wall of the first space and the second space, and the first space and the second space can form a channel for working fluid vapor.

[0017] (5) The working fluid can be a homogeneous material or a heterogeneous material.

[0018] (6) The core can be disposed on the inner surface of the wall of either the first space or the second space to form a channel for working fluid vapor.

[0019] (7) The interior of the space in the first space and the second space that does not form a channel for working fluid vapor can be filled with phase change material.

[0020] (8) The three-dimensional heat absorption device may also include a porous heat transfer component impregnated in a phase change material.

[0021] (9) The porous heat transfer component can be any of foam metal, grid metal and braided metal.

[0022] (10) A solid heat dissipation component may be installed in the space where no channel for working fluid vapor is formed in the first space and the second space.

[0023] (11) The heat dissipation component can be any of porous metal, solid metal and cooling plate.

[0024] (12) The core can be any of the following: metal mesh, felt, fiber and permeable porous solid.

[0025] (13) The working fluid can be any of water, ammonia, ethanol, helium, argon, nitrogen, lead, silver and lithium.

[0026] (14) The phase change material can be any one of paraffin, silicic acid and hydrated salt.

[0027] (15) The boundary between the first space and the second space can be a plane or a curved surface.

[0028] Effect

[0029] In the three-dimensional heat-absorbing device according to the invention, the internal heat transfer system is three-dimensionally extended and diversified, thereby improving the heat transfer rate. Furthermore, heat storage capacity is provided in a portion of the heat transfer system, allowing the heat-absorbing device to operate at a constant rate through natural cooling alone, typically without a separate forced cooling device, while suppressing temperature rise. Moreover, this improved heat transfer rate and / or heat storage capacity allows for the compact design of devices with suppressed energy consumption and noise generation. Additionally, in the three-dimensional heat-absorbing device according to the invention, the heat transfer channels are three-dimensionally connected, improving durability against external forces. Furthermore, the unrestricted operating direction allows for free design of systems including this heat-absorbing device. Attached Figure Description

[0030] Figure 1 The structure of a linear heat pipe according to related technologies is shown;

[0031] Figure 2 An example of a flat heat pipe according to the relevant technology is shown; and

[0032] Figures 3 to 6 The structure of a three-dimensional heat-absorbing device according to different embodiments of the present invention is shown. Detailed Implementation

[0033] The invention will be described in detail below by way of embodiments. Prior to this, the terms and words used in this specification and the appended claims should not be construed as limited to their general or literal meaning, but rather as meanings and concepts consistent with the technical spirit of the invention, based on the inventor's ability to appropriately define the concepts of the terms to best describe the principles of their invention. Therefore, the construction of the embodiments described in this specification corresponds only to the most preferred embodiments of the invention and does not represent all the technical spirit of the invention. Therefore, it should be understood that various equivalents and modifications may exist at the time of this invention. Also, in the drawings, the same parts or equivalents may be represented by the same reference numerals. Furthermore, throughout the specification, when a particular part is written as "comprising" a particular component, this means that the particular part does not exclude other components, but may also include other components, unless otherwise described.

[0034] Figure 3 A heat-absorbing device 10 according to a first embodiment of the present invention is shown.

[0035] Figure 3 A shows the two-dimensional structure of the heat absorption device 10. (See diagram for example.) Figure 3As shown in Figure A, the heat-absorbing device 10 includes an airtight member 110 defining the appearance of the device, and the internal space of the airtight member 110 is divided into a first space 120 and a second space 130. That is, the second space 130 is formed by the space in the internal space of the airtight member 110 that is not occupied by the first space 120. In this embodiment, the first space 120 forms a channel for the working fluid vapor, and the interior of the second space 130 is filled with a porous material for absorbing the liquefied working fluid to form a core 140. The shape of the airtight member 110 is not particularly limited and can be appropriately determined according to the system in which the heat-absorbing device 10 is applied. In this figure, the shape of the airtight member 110 is arbitrarily represented as the blank space of the core 140 to define the boundary between the exterior and interior of the device.

[0036] In this case, the airtight component 110 is not particularly limited as long as it is impermeable and has a predetermined thermal conductivity. The working fluid is not particularly limited as long as it is a material that can evaporate and condense according to the operating temperature and pressure of the heat-absorbing device 10. All liquids (e.g., water, ammonia, and ethanol), gases (e.g., helium, argon, and nitrogen), and solids (e.g., lead, silver, and lithium) can be used at room temperature and atmospheric pressure. For example, even if the material is solid at room temperature and atmospheric pressure, it can be used as the working fluid if it is liquid or gaseous at the operating temperature and pressure of the heat-absorbing device 10. The core 140 is formed of a porous material (e.g., metal mesh, felt, fiber, and permeable porous solid) so that the liquefied working fluid can move via capillary action. The internal pressure of the airtight component 110 can be maintained below atmospheric pressure, allowing evaporation and liquefaction to occur at a predetermined temperature.

[0037] Figure 3 B is a perspective view showing the first space 120. In this case, the first spaces 120 are connected to each other in a three-dimensional grid structure, and the second space 130 is reflected through... Figure 3 The empty spaces of B are connected to each other. However, Figure 3 The object shown in B represents the shape of a channel in the first space 120 in three dimensions, which serves as a pathway for the vapor phase working fluid. This shape of the channel is defined by a core 140 filled in the second space 130, but this does not mean that the boundary between the first space 120 and the second space 130 is formed by a single wall. Therefore, in this embodiment, the phase change working fluid can pass through the boundary between the first space 120 and the second space 130.

[0038] Although the three-dimensional grid shape of the first space 120 is hexagonal as in this embodiment, and therefore the channel has a straight shape, the invention is not limited thereto. For example, the boundary between the first space 120 and the second space 130 can be constructed to have a flat or curved shape, the shape of the channel serving as a passage for the working fluid can be constructed to have a straight or curved shape, and the cross-section of the channel can vary depending on the position.

[0039] Figure 3 C is a conceptual diagram of the operation of the heat-absorbing device 100. A predetermined first space 120 is filled with a gaseous working fluid, and a liquefied working fluid is absorbed into the core 140 of a second space 130. When heat is transferred from an external heat source (not shown) to the external local area D of the heat-absorbing device 10, the liquefied working fluid immersed in the core 140 of the second space 130 absorbs heat and transforms into a gaseous working fluid. This gaseous working fluid moves further away from the heat source along the channels of the first space 120 due to increased vapor pressure. The gaseous working fluid, moving away from the heat source, releases heat to the outside, is transformed back into a liquefied working fluid, and is again absorbed into the core 140. The absorbed liquefied working fluid flows back into the core 140 near the heat source via capillary action. The heat generated by the external heat source can be effectively absorbed and transferred through a cyclical process involving the evaporation, condensation, and movement of the working fluid.

[0040] according to Figure 3The heat-absorbing device 10 of the embodiment has the same basic heat transfer principle as the heat pipe according to the related art, but has the following advantages. First, since the volume of the core 140 formed of permeable porous material in the three-dimensionally extended heat transfer system is much larger than that of the heat pipe according to the related art, the amount of working fluid is also increased. As the amount of working fluid with high specific heat increases, the heat capacity of the entire heat-absorbing device 10 increases, so that the temperature rise of the heat-absorbing device 10 itself may be significantly delayed compared with the heat energy absorbed by the external heat source, and heat can be absorbed by the external heat source at a constant rate even without an independent forced cooling device. Second, the core 140, which fills the second space 130 to isolate the first space 120, is formed of permeable porous material, and can therefore be used to resist external forces to support the device 10 and to absorb and store liquefied working fluid. That is, the core 140 occupies the internal space of the airtight member 110 except for the first space 120 that forms the channel for working fluid vaporization, and can therefore also be used as a lightweight structural material for supporting loads. Third, while linear or flat heat pipes according to related technologies are one-dimensional or two-dimensional heat pipes, the heat-absorbing device 10 according to this embodiment is a three-dimensional heat pipe. When heat is applied from an external heat source to a portion of the hermetic member 110, the phase-change working fluid vapor near the heat source moves through multiple adjacent channels, and the condensed working fluid on the opposite side moves towards the heat source from the entire space formed by the permeable porous material through capillary action. Therefore, heat transfer occurs rapidly, and the heat-absorbing device 10 can operate using the same heat transfer mechanism regardless of the location and orientation of the heat source applied to the hermetic member 110.

[0041] Figure 4 The structure of a heat-absorbing device 20 according to a second embodiment of the present invention is shown.

[0042] Figure 4 A shows the two-dimensional structure of the heat absorption device 20. (As shown in Figure A) Figure 4 As shown in Figure A, similar to the first embodiment, the heat absorption device 20 includes an airtight member 210, and the internal space of the airtight member 210 is divided into a first space 220 and a second space 230. Furthermore, in this embodiment, the shape and material of the airtight member 210, the type of working fluid, and the materials of the cores 240a and 240b can be the same as those according to the first embodiment.

[0043] In this embodiment, unlike the first embodiment, the boundary between the first space 220 and the second space 230 is formed by a wall 280, and cores 240a and 240b are disposed on the inner surface of the wall 280, so that the first space 220 and the second space 230 independently form channels for the working fluid vapor. In this case, unlike the first embodiment, since the boundary between the first space 220 and the second space 230 is formed by the wall 280, it is impossible to move the phase change working fluid. The working fluid operating in the first space 220 and the second space 230 can be a homogeneous material or a heterogeneous material.

[0044] Figure 4 B is a perspective view showing the first space 220. In this case, the first space 220 is connected by a three-dimensional grid structure, and the second space 230 is reflected through... Figure 4 The structural blank spaces of B are interconnected. The three-dimensional grid structure forming the first space 220 is a hollow thin-film structure, and such a thin film constitutes the walls 280 of the first space 220 and the second space 230. In this embodiment, for example, the surface of the hollow thin-film structure can be composed of triple periodically minimal surfaces (TPMS) (S. Hyde et al., The Language of Shape, Elsevier, Danvers, MA, USA 1996), and Figure 4 Figure B shows three types of TPMS, such as the P surface, the D surface, and the G surface. The TPMS consists of smooth, continuous surfaces that do not intersect each other and have an average curvature of 0 (regardless of position), and the first space 220 and the second space 230 divided by the TPMS have similar shapes.

[0045] However, in this embodiment, although the three-dimensional grid shape of the first space 220 has a grid shape with TPMS, and therefore the channel has a curved shape, the invention is not limited thereto. For example, even in this embodiment, the channel for the working fluid vapor of the first space 220 can also be made according to the first embodiment. Figure 3 The straight lines shown in B constitute this. In this case, the shape of the three-dimensional thin film structure forming the first space 220 is similar to... Figure 3 The shape of the channels in B is the same. In addition, the boundary between the first space 220 and the second space 230 can be constructed to have a flat or curved shape, the shape of the channel serving as a passage for the working fluid can be constructed to have a straight or curved shape, and the cross-section of the channel can vary depending on the position.

[0046] Meanwhile, such hollow thin-film structures can be manufactured by methods involving the fabrication of a template, the formation of the thin film, and the removal of the template from within the thin film. This is a recently disclosed method relating to the fabrication of hollow thin-film structures. The template can be fabricated by using photolithography to cure a thermosetting resin or by using a wire-woven porous truss structure. There are no particular limitations on the material, as long as it is permeable and has a predetermined thermal conductivity similar to that of the airtight component 210. For example, metals can be advantageously used here.

[0047] according to Figure 4 In this embodiment, heat transfer of the heat-absorbing device 20 occurs through independent channels in the first space 220 and the second space 230. That is, when heat is transferred from an external heat source to a portion of the exterior of the heat-absorbing device 20, the liquefied working fluid impregnated in the cores 240a and 240b of the first and second spaces 220 absorbs heat and thus transforms into a gaseous working fluid. The gaseous working fluid moves along the first and second spaces 220 and 230 further away from the heat source due to increased vapor pressure. The gaseous working fluid, moving away from the heat source, releases heat to the outside, is transformed into a liquefied working fluid, and is again absorbed in the cores 240a and 240b. The absorbed liquefied working fluid moves along the channels of the first and second spaces 220 and 230 towards the cores 240a and 240b, closer to the heat source, through capillary action. The heat generated by the external heat source can be effectively absorbed and transferred through a cyclical process involving the evaporation, condensation, and movement of the working fluid. In this case, as described above, the working fluid in the first space 220 and the second space 230 can be a homogeneous material or a heterogeneous material.

[0048] according to Figure 4The heat-absorbing device 20 of this embodiment utilizes the same basic heat transfer principle as the heat pipe according to related technologies, but has the following advantages. First, the three-dimensional first space 220 and the three-dimensional second space 230 are used as independent channels for the working fluid, which increases the heat transfer rate and the amount of heat transfer. Furthermore, when the working fluids in the first space 220 and the second space 230 are different, multiple heat transfer mechanisms with different heat transfer temperature ranges can be simultaneously implemented in one heat-absorbing device 20. Second, similar to the first embodiment, since the volume of the cores 240a and 240b formed of permeable porous material in the three-dimensional extended heat transfer system is much larger than that of the heat pipe according to related technologies, the amount of working fluid also increases. As the amount of working fluid with a high specific heat increases, the heat capacity of the entire heat-absorbing device 20 increases, which can significantly delay the temperature rise of the heat-absorbing device 20 itself compared to the heat energy absorbed by the external heat source, and even without an independent forced cooling device, heat can be absorbed by the external heat source at a constant rate. Third, the membrane wall 280, which serves as the boundary separating the first space 220 and the second space 230, itself constitutes an ideal lightweight structure capable of supporting external loads. For example, hollow truss structures with kagome, octet, or pyramidal lattice structures exhibit superior strength compared to weight (HNG Wadley, Phil. Trans. R. Soc. A. Vol. 364, pp. 31-68, 2006). Furthermore, it has been reported that structures with... Figure 4 The TPMS-shaped thin-film structure shown in B also has strength equal to that of a hollow truss structure (SCHan, JWLee, K. Kang, Advanced Materials, Vol. 27, pp. 5506-5511, 2015). Therefore, since the first space 220 and the second space 230 are separated by the thin-film wall 280, the heat-absorbing device 20 can be supported against external forces. Fourth, similar to the first embodiment, the heat-absorbing device 20 operates as a three-dimensional heat pipe, so the same heat transfer mechanism can be used regardless of the position and direction of the heat applied to the airtight member 110.

[0049] Figure 5 The structure of the heat absorption device 30 according to a third embodiment of the present invention is shown.

[0050] Figure 5 A shows the two-dimensional structure of the heat absorption device 30. (See diagram for example.) Figure 5As shown in Figure A, similar to the first embodiment, the heat-absorbing device 30 includes an airtight member 310, and its internal space is divided into a first space 320 and a second space 330. Furthermore, similar to the first embodiment, the shape and material of the airtight member 310, the type of working fluid, and the material of the core 340 can be used identically. Furthermore, similar to the second embodiment, since the boundary between the first space 320 and the second space 330 is formed by a thin film wall 380, it is impossible for the phase-change working fluid to move. Furthermore, the three-dimensional hollow thin film structure forming the first space 320, its manufacturing method, and the material of the thin film can be the same as those according to the second embodiment. Although... Figure 5 A shows a first space 320 having a grid shape with TPMS, and thus the channel having a curved shape, but the invention is not limited thereto.

[0051] In this embodiment, unlike the second embodiment, since the core 340 is only disposed on the inner surface of the wall 380 of the first space 320, only the first space 320 forms a channel for the working fluid vapor, and the second space 330 is filled with, for example, PCM 350 with a large latent heat of fusion, such as paraffin, lauric acid, and hydrated salts. In this case, immediate heat transfer from an external heat source occurs through the channel formed by the first space 320, and this immediate heat transfer is the same as the heat transfer through the working fluid in the first embodiment. The PCM 350 filled in the second space 330 serves as a heat storage device that gradually absorbs heat from the outside while changing from a solid phase to a liquid phase.

[0052] Figure 5 B illustrates a modification to the third embodiment. Figure 5 In B, the second space 330 also includes a porous heat transfer component 360 with high thermal conductivity and formed of metal. The porous heat transfer component 360 can be formed of a permeable porous metal (e.g., foam metal, grid metal, and braided metal) (KJ Kang, “Wire-woven cellular metals: the present and future”, Progress in Materials Science, Vol. 69, pp. 213-307, 2015) and impregnated in PCM 360. Such a porous heat transfer component 360 promotes a higher heat transfer rate to the PCM 360, which has low thermal conductivity, thereby improving the heat storage performance of the heat absorption device 30.

[0053] Compared with heat storage devices based on heat pipes or PCMs according to relevant technologies, according to Figure 5The heat-absorbing device 30 of the embodiment has the following advantages: First, heat transfer from the PCM 350 in the first space 320 to the second space 330 occurs immediately through the wall 380 with a wide surface area via the three-dimensional channel of the first space 320, thereby improving the responsiveness to heat absorption by the PCM. Second, when the melting temperature of the PCM 350 in the second space 330 is within the operating temperature range for immediate heat transfer of the first space 210, the working fluid in the first space 320 is completely dried even when unexpectedly high heat energy is applied from the outside due to the high latent heat of fusion of the PCM 350 in the second space 330 surrounding the first space 320, significantly reducing the possibility of loss of heat transfer function. Simultaneously, when the melting temperature of the PCM 350 in the second space 330 is outside the operating temperature range for heat transfer of the first space 320, the first space 320 and the second space 330 can operate independently. Third, since the PCM 350 of the second space 330 itself has a high specific heat, even when heat transfer occurs in the first space 320 according to the heat pipe principle, the temperature of the entire heat-absorbing device 30 rises slowly, and heat absorption can even occur at a constant rate without an independent forced cooling device. Fourth, similar to the second embodiment, the thin film wall 380, which serves as the boundary separating the first space 320 and the second space 330, itself constitutes an ideal lightweight structure that can support external loads, and can therefore be used to support the heat-absorbing device 30 according to external forces. Fifth, similar to the first embodiment, the heat-absorbing device 30 operates as a three-dimensional heat pipe, so the same heat transfer mechanism can be used to operate regardless of the position and direction of the heat applied to the airtight member 310. Sixth, similar to the first embodiment, since a three-dimensionally extended heat transfer system is provided, the heat transfer rate may be increased, and the heat capacity of the device may be increased.

[0054] Figure 6 The structure of a heat-absorbing device 40 according to a fourth embodiment of the present invention is shown.

[0055] Figure 6 A and Figure 6 B illustrates the two-dimensional and three-dimensional structures of the heat absorption device 40. For example... Figure 6 As shown in Figure A, similar to the first embodiment, the heat-absorbing device 40 includes an airtight member 410, and the internal space of the airtight member 410 is divided into a first space 420 and a second space 430. Furthermore, similar to the first embodiment, the shape and material of the airtight member 410, the type of working fluid, and the material of the core 440 can be used identically. Furthermore, similar to the second embodiment, since the boundary between the first space 420 and the second space 430 is formed by a thin film wall 480, it is impossible for the phase change working fluid to move. Furthermore, the three-dimensional hollow thin film structure forming the first space 420, its manufacturing method, and the material of the thin film can be the same as those according to the second embodiment. Although... Figure 6 A shows that the shape of the passage in the first space 420 has the same shape as... Figure 3 B is similar to hexagonal grid shapes and linear shapes, but the invention is not limited thereto.

[0056] In this embodiment, similar to the third embodiment, since the core 440 is provided only on the inner surface of the wall 480 of the first space 420, only the first space 420 forms a channel for the working fluid vapor. However, unlike the third embodiment, the second space 430 can be as follows: Figure 6 A and Figure 6 As shown in Figure B, it has a heat dissipation component 470 (e.g., a cooling fin), or it can be as follows: Figure 6 The space shown in section C is completely empty. Besides the cooling fins, the heat dissipation member 470 can also be formed of porous or solid metal, and thus can fill all or part of the second space 430. In this case, immediate heat transfer occurs in the first space 420 using the same principle as a heat pipe, and conductive, radiative, and convective heat transfer occurs in the second space 430 using the heat dissipation member 470 or the empty space. When the volume of the second space 430 is larger than the volume of the first space 420, the heat transfer mechanism in the second space 430 can be advantageously used.

[0057] Compared with heat pipes based on related technologies, according to Figure 6 The heat transfer device 40 of the embodiment has the following advantages: First, when the volume of the second space 430 is larger than the volume of the first space 420, conductive heat transfer, radiative heat transfer, and convective heat transfer are initiated by the second space 430 itself or the heat dissipation member 470, so that heat absorption can be carried out at a constant rate even without an independent forced cooling device. Second, in particular, when the heat dissipation member 470 filling the second space 430 is completely filled with a non-porous (solid) material (e.g., metal), the first space 420 can be simply formed by drilling holes in the non-porous material block, so that the heat absorption device 40 can be easily manufactured, the structural strength can be improved, and the heat absorption device 40 has the high heat capacity of the non-porous material, so that heat absorption can be carried out at a constant rate even without an independent forced cooling device. Third, even when the second space 430 is empty or the heat dissipation member 470 is not completely filled, similar to the second embodiment, the thin film wall 480, which serves as the wall separating the first space 420 and the second space 430, itself constitutes an ideal lightweight structure capable of supporting external loads, and can therefore be used to support the heat-absorbing device 40 according to external forces. Fourth, similar to the first embodiment, the heat-absorbing device 20 operates as a three-dimensional heat pipe, so the same heat transfer mechanism can be used regardless of the location and direction of the heat applied to the airtight member 410. Fifth, similar to the first embodiment, due to the provision of a three-dimensionally extended heat transfer system, the heat transfer rate may be increased, and the heat capacity of the device may be increased.

[0058] As described above, in the three-dimensional heat-absorbing device according to the invention, the internal heat transfer system is three-dimensionally extended and diversified, thereby improving the heat transfer rate. Furthermore, heat storage capacity is provided in a portion of the heat transfer system, allowing the heat-absorbing device to operate at a constant rate through natural cooling alone, typically without a separate forced cooling device and while suppressing temperature rise. Moreover, this improved heat transfer rate and / or heat storage capacity allows for the compact design of devices with suppressed energy consumption and noise generation. Furthermore, in the three-dimensional heat-absorbing device according to the invention, since the heat transfer channels are three-dimensionally connected, the operating direction is unrestricted, allowing for free design of systems including this heat-absorbing device.

[0059] The above description relates to detailed embodiments of the present invention. These embodiments should not be construed as limiting the scope of the invention as described. Furthermore, it should be understood that various changes and modifications can be derived by those skilled in the art without departing from the spirit of the invention. For example, in the above embodiments, the actions performed by the first space and the second space can be interchanged. Moreover, although described in the embodiments, the working fluid and phase change material filled in the heat-absorbing device can be appropriately selected and used according to the operating temperature and operating pressure range. Therefore, it should be understood that all modifications and variations correspond to the scope of the invention as disclosed in the appended claims or their equivalents.

Claims

1. A three-dimensional heat absorption device, comprising: An airtight component that defines the appearance of a three-dimensional heat absorption device; The first space within the airtight component is interconnected by a three-dimensional grid structure; as well as A second space is formed within the internal space of the airtight component, which is not occupied by the first space. In this configuration, one of the first and second spaces forms a channel for the working fluid vapor, and a core for absorbing the liquefied working fluid is disposed along the inner surface of the channel. The other of the first and second spaces is filled with the core. The shape of the channel formed in one of the first and second spaces is defined by the core filled in the other of the first and second spaces, and the phase change working fluid can pass through the boundary between the first and second spaces.

2. The three-dimensional heat sink device of claim 1, wherein, The core can be any of the following: metal mesh, felt, fiber, and permeable porous solid.

3. The three-dimensional heat sink device of claim 1, wherein, The working fluid can be any one of water, ammonia, ethanol, helium, argon, nitrogen, lead, silver, and lithium.

4. The three-dimensional heat sink of claim 1, wherein, The boundary between the first space and the second space is a plane or a curved surface.

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