Vapor chamber, heat dissipation assembly, and terminal apparatus

Abstract

A vapor chamber, divided into a heat source region and at least two condensing regions. The vapor chamber comprises a housing, a first capillary structure, and a second capillary structure. The second capillary structure is disposed overlapping the first capillary structure, and is located in the housing. The second capillary structure comprises a first capillary core and a second capillary core, a first gap being formed between the first capillary core and the housing, and a second gap being formed between the second capillary core and the housing. The first capillary core comprises a first hot end, the second capillary core comprises a second hot end, and the first hot end and the second hot end are located in the heat source region. The first hot end and the second hot end are spaced apart from each other to form a third gap, and the third gap places the first gap and the second gap in communication. When steam flowing in the first gap and the second gap flows to the heat source region, the steam is fully circulated by means of the communicating function of the third gap, facilitating intercommunication of the steam, reducing the flowing resistance of the steam, and facilitating steam distribution. The present application further provides a heat dissipation assembly and a terminal apparatus.

Description

Heat sink, heat dissipation components and terminal devices

[0001] Cross-references to related applications

[0002] This application claims to have been filed with the Chinese Patent Office on May 28, 2024, application number 202410681744.8, entitled "Heat Spreader, Heat Dissipation Assembly and Terminal Device", the entire contents of which are incorporated herein by reference. Technical Field

[0003] This application relates to the field of heat dissipation technology, and in particular to a heat dissipation plate, heat dissipation component and terminal device. Background Technology

[0004] Terminal devices typically include heat source elements and heat dissipation components. Heat source elements generate heat during operation, and heat dissipation components are used to dissipate the heat generated by the heat source elements. The faster the operating speed and the higher the operating power of the heat source elements, the more heat will be generated. If the heat generated by the heat source elements is not dissipated in time, it will affect the heat source elements or other components in the terminal device, or even damage the heat source elements.

[0005] Among them, heat dissipation components usually use heat pipes and fans in combination to achieve heat dissipation function. Due to the limitations of manufacturing process, the wall thickness of heat pipes usually exceeds 0.2mm, and the overall thickness of heat pipes needs to exceed 2.0mm to meet the heat dissipation requirements of terminal devices. In addition, the heat dissipation area of ​​heat pipes is related to their diameter, and the diameter of heat pipes affects heat dissipation performance.

[0006] With the trend towards thinner terminal device designs, it is difficult to reserve sufficient space for installing heat dissipation components. Therefore, thinner vapor chambers can be used instead of heat dissipation components. However, the capillary structure in existing vapor chambers typically results in high steam flow resistance and uneven steam distribution. Summary of the Invention

[0007] In view of this, it is necessary to provide a heat spreader that reduces steam flow resistance and improves the uniformity of steam distribution, a heat dissipation assembly including the heat spreader, and a terminal device to solve the above problems.

[0008] In a first aspect, this application provides a heat spreader plate divided into a heat source region and at least two condensation regions. The heat spreader plate includes a shell, a first capillary structure, and a second capillary structure. The second capillary structure is superimposed on the first capillary structure and located in the shell. The second capillary structure includes at least one first capillary core and at least one second capillary core. A first gap is formed between the first capillary core and the shell, and a second gap is formed between the second capillary core and the shell. The first capillary core includes a first hot end and a first cold end, and the second capillary core includes a second hot end and a second cold end. The first hot end and the second hot end are located in the heat source region, and the first cold end and the second cold end are located in different condensation regions. A third gap is formed between the first hot end and the second hot end, and the third gap connects the first gap and the second gap.

[0009] In the design of the above structure, a third gap is formed between the first and second hot ends, connecting the first and second gaps. When steam flowing through the first and second gaps reaches the heat source area, it can circulate fully through the connection of the third gap, which facilitates steam exchange between the first and second gaps, thereby reducing steam flow resistance and improving the heat dissipation power of the heat spreader. Secondly, the steam exchange between the first and second gaps also helps to balance the steam pressure in the first and second gaps, resulting in more uniform heat conduction.

[0010] In one possible embodiment of this application, the first hot end and the second hot end are arranged along a first direction, and the first cold end and the second cold end are arranged along a second direction. Along the first direction, the projections of the first hot end and the second hot end at least partially overlap, and the first direction and the second direction intersect.

[0011] The design of the above structure, in which the projections of the first hot end and the second hot end at least partially overlap, is beneficial for the first and second hot ends to cover the heat source area as much as possible along the second direction. This allows the condensed and recirculated coolant to reach the heat source area along the first and second capillary wicks and to spread out more evenly and quickly in the heat source area. This increases the area of ​​the heat source area that absorbs the heat conducted by the heat source element, thereby facilitating the rapid absorption of heat generated by the heat source element by the heat spreader. Furthermore, the recirculated coolant can reach the heat source area along the first and second capillary wicks, which is beneficial for the uniform distribution of coolant in the heat source area and helps prevent local dry burning of the heat spreader due to uneven coolant distribution.

[0012] In one possible embodiment of this application, the first hot end includes a first portion, and the second hot end includes a second portion; both the first portion and the second portion extend along a second direction.

[0013] The design of the above structure ensures that the third gap is unobstructed along the second direction, resulting in low flow resistance for steam in the third gap, which is beneficial for increasing the steam flow rate in the third gap.

[0014] In one possible embodiment of this application, the first hot end further includes a third portion, the third portion being connected to the end of the first portion away from the first cold end, and the third portion being bent relative to the first portion; and / or the second hot end further includes a fourth portion, the fourth portion being connected to the end of the second portion away from the second cold end, and the fourth portion being bent relative to the second portion.

[0015] The design of the above structure, with its relatively bent third and / or fourth parts, facilitates the extension of the first and / or second hot ends located in the heat source area in different directions, thereby enabling the liquid coolant to conduct heat from different directions.

[0016] In one possible embodiment of this application, the third portion bends toward the second portion; and / or the fourth portion bends toward the first portion.

[0017] The design of the above structure, with the third and fourth parts located between the first and second parts, can increase the maximum width of the third gap formed between the first and second hot ends, thereby increasing the area for steam exchange and facilitating steam flow in the third gap.

[0018] In one possible embodiment of this application, the third portion bends away from the second portion; and / or the fourth portion bends away from the first portion.

[0019] The design of the above structure ensures that the third gap is unobstructed along the second direction, resulting in low flow resistance for steam in the third gap, which is beneficial for increasing the steam flow rate in the third gap.

[0020] In one possible embodiment of this application, along the first direction, the width of the heat source area is W1, the distance between the first hot end and the second hot end is W2, the width of the first hot end is W3, and the width of the second hot end is W4, satisfying: 1 / 2≤W2 / W3≤3, 1 / 2≤W2 / W4≤3, W3 / W1≤1 / 3, W4 / W1≤1 / 3.

[0021] The design of the above structure allows for a certain width to be reserved for the third gap. When the width of the third gap is large, it is conducive to the flow of steam. When the width of the first hot end and the width of the second hot end are within a certain range, it is conducive to the rapid and uniform absorption of heat.

[0022] In one possible embodiment of this application, along the second direction, the length of the heat source region is L1, and the length of the first hot end and the second hot end that coincide in the projection along the first direction is L2, satisfying: 1 / 2≤L2 / L1≤1.

[0023] The design of the above structure allows the first and second hot ends to cover the length of the heat source region as much as possible along the second direction, so that the condensed and refluxed coolant can reach the heat source region along the first and second capillary cores, thereby absorbing heat quickly and evenly; and, while ensuring that heat is absorbed evenly and quickly, the overall length of the second capillary structure in the heat source region can be reduced.

[0024] In one possible embodiment of this application, the first hot end and the second hot end are arranged along a second direction, and the first cold end and the second cold end are arranged along the second direction, and the projections of the first hot end and the second hot end at least partially overlap along the second direction.

[0025] The design of the above structure, in which the projections of the first hot end and the second hot end at least partially overlap, is beneficial for the first and second hot ends to cover the heat source area as much as possible along the first direction. This allows the condensed and recirculated coolant to reach the heat source area along the first and second capillary wicks and to spread out more evenly and quickly in the heat source area. This increases the area of ​​the heat source area that absorbs the heat conducted by the heat source element, thereby facilitating the rapid absorption of heat generated by the heat source element by the heat spreader. Furthermore, the recirculated coolant can reach the heat source area along the first and second capillary wicks, which is beneficial for the uniform distribution of coolant in the heat source area and helps prevent local dry burning of the heat spreader due to uneven coolant distribution.

[0026] In one possible embodiment of this application, the first hot end includes a first portion and a third portion, the third portion and the first portion are connected at the ends opposite to the first cold end, the first portion extends along a second direction, and the third portion is bent relative to the first portion; and / or the second hot end includes a second portion and a fourth portion, the fourth portion and the second portion are connected at the ends opposite to the second cold end, the second portion extends along a second direction, and the fourth portion is bent relative to the second portion.

[0027] The design of the above structure, with its relatively bent third and / or fourth parts, facilitates the extension of the first and / or second hot ends located in the heat source area in different directions, thereby enabling the liquid coolant to conduct heat from different directions.

[0028] In one possible embodiment of this application, the third portion bends relative to the first portion along a first direction, and the first and second directions intersect; and / or the fourth portion bends relative to the first portion along a first direction, and the first and second directions intersect.

[0029] The design of the above structure is advantageous because the first hot end and / or the second hot end located in the heat source area extend in different directions, thereby facilitating the conduction of heat from different directions by the liquid coolant.

[0030] In one possible embodiment of this application, the first hot end further includes a fifth portion, the fifth portion and the third portion being connected at one end away from the first portion, the fifth portion extending away from the second hot end relative to the third portion; and / or the second hot end further includes a sixth portion, the sixth portion and the fourth portion being connected at one end away from the second portion, the sixth portion extending away from the first hot end relative to the fourth portion.

[0031] The design of the above structure is advantageous because the first hot end and / or the second hot end located in the heat source area extend in different directions, thereby facilitating the conduction of heat from different directions by the liquid coolant.

[0032] In one possible embodiment of this application, the first hot end includes a first portion and a third portion, the third portion and the first portion are connected at the ends opposite to the first cold end, the first portion extends along a second direction, and both ends of the third portion protrude relative to the first portion; and / or the second hot end includes a second portion and a fourth portion, the fourth portion and the second portion are connected at the ends opposite to the second cold end, the second portion extends along a second direction, and both ends of the fourth portion protrude relative to the second portion.

[0033] The design of the above structure is advantageous because the first hot end and / or the second hot end located in the heat source area extend in different directions, thereby facilitating the conduction of heat from different directions by the liquid coolant.

[0034] In one possible embodiment of this application, the permeability of the second capillary structure is greater than that of the first capillary structure.

[0035] The design of the above structure facilitates the return of liquid coolant mainly through the second capillary structure, thereby promoting the circulation of coolant in the heat exchanger.

[0036] In one possible embodiment of this application, the housing includes a first surface and a second surface, which are disposed opposite to each other. A first capillary structure is disposed on the first surface, and a second capillary structure is disposed on the second surface, with the second capillary structure located on the surface of the first capillary structure.

[0037] Secondly, this application provides a heat dissipation assembly, which includes a heat dissipation plate, and the heat dissipation plate further includes a fan and / or fins. The fins are disposed on the surface of the housing located in the condensation zone, and the fan is used to generate airflow toward the fins.

[0038] The design of the above structure, including the heat dissipation components of the heat spreader, has the properties of low steam flow resistance and uniform steam distribution.

[0039] Thirdly, this application provides a terminal device, which includes: a heat source element and a heat spreader or heat dissipation assembly. The heat source element is disposed in the heat source area of ​​the heat spreader and is disposed on the side of the housing that is sequentially opposite to the second capillary structure and the first capillary structure.

[0040] The design of the above structure, including the terminal device of the heat spreader, has the performance of low steam flow resistance and uniform steam distribution. Attached Figure Description

[0041] Figure 1A is a schematic diagram of the structure of the terminal device provided in the embodiment of this application.

[0042] Figure 1B is a top view of the heat source element provided in the embodiment of this application disposed on the heat dissipation assembly.

[0043] Figure 2 is a schematic diagram of the overall structure of the heat spreader provided in the embodiment of this application.

[0044] Figure 3 is an exploded view of the heat spreader shown in Figure 2 along one direction.

[0045] Figure 4 is an exploded view of the heat spreader shown in Figure 2 from another direction.

[0046] Figure 5 is a schematic cross-sectional view of the heat spreader shown in Figure 2 along the AA direction.

[0047] Figure 6 is a top view of the first and second capillary structures in the heat spreader shown in Figure 2.

[0048] Figure 7 is a top view of the first and second capillary structures in a heat spreader provided by related technologies.

[0049] Figure 8 is a top view of a first capillary structure and a second capillary structure provided in some embodiments of this application.

[0050] Figure 9 is a top view of a first capillary structure and a second capillary structure provided in some embodiments of this application.

[0051] Figure 10 is a top view of a first capillary structure and a second capillary structure provided in some other embodiments of this application.

[0052] Figure 11 is a top view of a first capillary structure and a second capillary structure provided in some other embodiments of this application.

[0053] Figure 12 is a top view of a first capillary structure and a second capillary structure provided in some other embodiments of this application.

[0054] Figure 13 is a top view of a first capillary structure and a second capillary structure provided in some other embodiments of this application.

[0055] Figure 14 is a simulation test diagram of steam flow on the heat spreader provided in the embodiment.

[0056] Figure 15 shows a simulation test diagram of steam flow on the heat spreader provided as a comparative example.

[0057] Explanation of main component symbols Detailed Implementation

[0058] To better understand the above-mentioned objectives, features, and advantages of this application, the application will be described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. Many specific details are set forth in the following description to provide a thorough understanding of this application; the described embodiments are merely some, not all, of the embodiments described in this application.

[0059] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the scope of this application. The term "and / or" as used herein describes an association between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A alone, A and B simultaneously, and B alone.

[0060] In the various embodiments of this application, for ease of description and not limitation, the term "connection" used in the patent application specification and claims is not limited to physical or mechanical connections, whether direct or indirect. Terms such as "upper," "lower," "above," "below," "left," and "right" are used only to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship also changes accordingly.

[0061] Please refer to Figure 1A, which is a schematic diagram of the structure of the terminal device 200 provided in an embodiment of this application. The terminal device 200 shown in Figure 1A is a laptop computer. In other embodiments, the terminal device 200 may also include, but is not limited to, a desktop computer, a tablet computer, a mobile phone, a charger, a camera, etc.

[0062] Please refer to Figure 1B, which is a top view of the heat source element 226 disposed on the heat dissipation assembly 228 according to an embodiment of this application. The terminal device 200 includes a heat source element 226 and a heat dissipation assembly 228. The heat source element 226 generates heat during operation, and the heat dissipation assembly 228 is used to dissipate the heat generated by the heat source element 226. The heat source element 226 may include, but is not limited to, a chip, a central processing unit (CPU), a graphics processing unit (GPU), a wireless module, a battery, etc.

[0063] The terminal device 200 shown in Figure 1A may include a first body 210 and a second body 220, which are rotatably connected. The terminal device 200 can be in an open or folded state. The first body 210 may include a first housing 212 and a display screen 214, with the first housing 212 located on one side of the display screen 214 and surrounding its edge. The second body 220 may include a second housing 222, a keyboard 224, a heat source element 226, and a heat dissipation assembly 228, with the second housing 222 located on one side of the keyboard 224 and surrounding its edge. The heat dissipation assembly 228 and the heat source element 226 are located between the second housing 222 and the keyboard 224. When the terminal device 200 is in the folded state, the display screen 214 and the keyboard 224 are located on the inside, and the first housing 212 and the second housing 222 are located on the outside.

[0064] The heat dissipation assembly 228 may include a heat spreader 100, a fan 2281, and fins 2283. Both the heat source element 226 and the fins 2283 are located on the surface of the heat spreader 100. The heat spreader 100 and the heat source element 226 are connected (directly or indirectly). The heat spreader 100 is used to quickly conduct away the heat generated by the heat source element 226, so that the heat source element 226 can be maintained at a suitable operating temperature. The temperature of the area of ​​the heat spreader 100 where the heat source element 226 is located is higher than the temperature where the fins 2283 are located. The fan 2281 enables airflow inside the terminal device 200 for rapid heat dissipation. It is understood that in other embodiments, the fan 2281 and / or the fins 2283 may be omitted depending on actual needs and the specific terminal device 200. The connection methods between the heat source element 226 and the heat spreader 100 include, but are not limited to, bonding, screwing, and snap-fitting.

[0065] In the same terminal device 200, there can be one or more heat source elements 226 depending on the number of heat source elements 226. When there are multiple heat source elements 226, multiple heat source elements 226 can share one heat spreader 100, or multiple heat spreaders 100 can be set. The specific number of heat source elements 226 and heat spreaders 100 is not limited and can be flexibly adjusted according to the hardware form, component layout, and usage scenario of the terminal device 200.

[0066] In this embodiment, the terminal device 200 may further include a heat sink 2285 and thermally conductive adhesive (not shown). Both the heat sink 2285 and the thermally conductive adhesive are disposed between the heat source element 226 and the heat spreader 100. The heat sink 2285 is disposed on the surface of the heat spreader 100, and the thermally conductive adhesive is used to bond the heat source element 226 and the heat sink 2285. Along the direction in which the heat source element 226 and the heat spreader 100 are stacked (defined as the third direction Z), the projection of the heat source element 226 lies within the projection of the heat sink 2285. The heat sink 2285 is used to disperse and conduct the heat generated by the heat source element 226 to the heat spreader 100, preventing the heat generated by the relatively small heat source element 226 from becoming too concentrated. The larger area of ​​the heat sink 2285 increases the heat conduction area, thereby increasing the heat dissipation effect.

[0067] Figure 2 is a schematic diagram of the overall structure of the heat spreader 100 provided in this embodiment. The heat spreader 100 can be divided into a heat source area I and at least two condensation areas II. When the terminal device 200 does not include the heat sink 2285, the heat source area I is the projection area of ​​the heat source element 226 on the heat spreader 100 along the third direction Z; when the terminal device 200 includes the heat sink 2285, the heat source area I is the projection area of ​​the heat sink 2285 on the heat spreader 100 along the third direction Z.

[0068] In the embodiment shown in Figure 2, the heat spreader 100 includes a heat source area I and two condensation areas II, with the heat source area I located between the two condensation areas II. The specific arrangement of the heat source area I and the two condensation areas II can be flexibly designed according to the layout of other components in the terminal device 200 and the heat dissipation effect required by the heat spreader 100. The heat source area I is used to connect with the heat source element 226, and the heat source element 226 and the heat source area I are stacked. The condensation areas II extend outward relative to the heat source element 226 and the heat source area I. The heat generated by the heat source element 226 is conducted to the heat source area I, and then to the condensation areas II, where it is dissipated. The heat conducted to the condensation areas II can be further dissipated quickly through the action of the fins 2283 and the fan 2281. It can be understood that when the heat source element 226 dissipates heat and conducts it to the heat spreader 100, the temperature of the condensation area II is lower than the temperature of the heat source area I.

[0069] Please refer to Figures 3, 4, 5 and 6 together. Figure 3 is an exploded view of the heat spreader 100 shown in Figure 2 along one direction. Figure 4 is an exploded view of the heat spreader 100 shown in Figure 2 along another direction. Figure 5 is a cross-sectional schematic diagram of the heat spreader 100 shown in Figure 2 along the AA direction. Figure 6 is a top view schematic diagram of the first capillary structure 50 and the second capillary structure 60 in the heat spreader 100 shown in Figure 2. For ease of reference, other components in the heat spreader 100 are omitted in Figure 6.

[0070] The heat spreader 100 may include a housing 10, a first capillary structure 50, a second capillary structure 60, coolant (not shown), and a support column 70. The housing 10 may be formed by a first housing 30 and a second housing 40, which are sealed to each other to form a sealed receiving cavity 47. The first capillary structure 50, the second capillary structure 60, the coolant, and the support column 70 are all housed within the receiving cavity 47. The pressure in the receiving cavity 47 may be negative, i.e., less than atmospheric pressure, or even close to a vacuum, to lower the boiling point of the coolant and facilitate a phase change at a lower temperature.

[0071] The heat spreader 100 is generally flat, as are the first housing 30 and the second housing 40. The thickness of the first housing 30 or the second housing 40 can be less than 0.1 mm, and the overall thickness of the heat spreader 100 can be less than 1 mm, which helps reduce the overall thickness of the terminal device 200. Furthermore, the heat dissipation area of ​​the heat spreader 100 can cover most of the heat-generating area of ​​the heat source element 226, facilitating the rapid dissipation of heat generated by the heat source element 226.

[0072] The first housing 30 includes a first surface 31, and the second housing 40 includes a second surface 41. The first surface 31 and the second surface 41 are disposed opposite to each other, with the first surface 31 facing the second housing 40 and the second surface 41 facing the first housing 30. The second housing 40 also includes a first side surface 43 and a second side surface 45, which are disposed on opposite sides of the second surface 41. The side of the first side surface 43 and the second side surface 45 facing away from the second surface 41 is connected to the first surface 31. The first side surface 43, the second side surface 45, the first surface 31, and the second surface 41 together form a receiving cavity 47.

[0073] The first capillary structure 50 is fixed to the first surface 31, and the second capillary structure 60 is fixed to the second surface 41. The second capillary structure 60 is stacked on top of the first capillary structure 50 along the third direction Z. That is, the first shell 30, the first capillary structure 50, the second capillary structure 60, and the second shell 40 are stacked along the third direction Z, which helps to reduce the overall thickness of the heat spreader 100. The heat source element 226 is located on the side of the second shell 40 away from the first shell 30.

[0074] Multiple support columns 70 are provided, positioned between the second housing 40 and the first capillary structure 50. Each end of the support column 70 connects to both the second housing 40 and the first capillary structure 50. The end of the support column 70 facing away from the first capillary structure 50 can be fixed to the second surface 41. The support column 70 can be integrally formed with the second housing 40, and the support column 70 and the second capillary structure 60 are spaced apart. The support column 70 serves to provide support and prevent the first housing 30 or the second housing 40 from collapsing. The installation of the support column 70 does not increase the thickness of the heat spreader 100. In other embodiments, the fixing method of the support column 70 is not limited; it can be integrally formed with the first housing 30.

[0075] When the heat spreader 100 is not heated, the coolant can be adsorbed by the first capillary structure 50 and the second capillary structure 60. The coolant can be water, ethanol, etc. When the heat spreader 100 is heated, the coolant absorbs heat and evaporates, forming vapor that moves in the receiving cavity 47. When the vapor comes into contact with the condensation zone II, which has a lower temperature than the heat source zone I, the vapor can condense and form liquid coolant. During the condensation process, the vapor releases heat. At the same time, the liquid coolant can flow in the first capillary structure 50 and the second capillary structure 60 and flow back to the heat source zone I to repeat the evaporation and condensation cycle. The first capillary structure 50 has a large capillary force, which is beneficial to the flow and distribution of the liquid coolant in the first capillary structure 50. The second capillary structure 60 has a large permeability, which is greater than that of the first capillary structure 50. This is beneficial to the liquid coolant mainly flowing back through the second capillary structure 60, thereby promoting the circulation of the coolant in the heat spreader 100.

[0076] The first capillary structure 50 may include, but is not limited to, copper mesh capillary, sintered copper powder capillary, or foamed copper capillary. In some embodiments, when the first capillary structure 50 is a copper mesh capillary, the mesh size of the copper mesh capillary can range from 100 to 400 mesh; when the first capillary structure 50 is a sintered copper powder capillary, the mesh size of the sintered copper powder capillary can range from 60 to 200 mesh, and the particle size of the copper powder before sintering can range from 50 μm to 200 μm; when the first capillary structure 50 is a foamed copper capillary, the permeability of the foamed copper capillary can be greater than 2 × 10⁻⁶. -10 m 2 It is understood that, in other embodiments, the specific structure and parameters of the first capillary structure 50 can be adjusted according to the specific type of terminal device 200 and heat dissipation requirements.

[0077] The second capillary structure 60 may include, but is not limited to, printed copper powder capillary, braided copper wire, copper mesh capillary, and foamed copper capillary. In some embodiments, when the second capillary structure 60 is a printed copper powder capillary, the mesh size of the printed copper powder capillary can range from 60 to 200 mesh, and the particle size of the copper powder before sintering can range from 50 μm to 200 μm; when the second capillary structure 60 is a braided copper wire, the wire diameter can be 0.03 mm, 0.04 mm, 0.05 mm, 0.06 mm, etc., the number of braided strands of a single copper wire can be selected as 6 to 15, the number of braided strands can be 12, 16, 20, 24, etc., and the number of braided layers of the copper wire can be 1 to 4 layers; when the second capillary structure 60 is a copper mesh capillary, the mesh size of the copper mesh capillary can range from 100 to 400 mesh; when the second capillary structure 60 is a foamed copper capillary, the permeability of the foamed copper capillary can be greater than 2 × 10⁻⁶. -10 m 2 It is understood that in other embodiments, the specific structure and parameters of the second capillary structure 60 can be adjusted according to the specific type of terminal device 200 and heat dissipation requirements. Specifically, the capillary force and permeability of the first capillary structure 50 and the second capillary structure 60 can be adjusted by modifying factors such as the capillary pore size and porosity of the capillary structure.

[0078] Referring to Figure 6, the second capillary structure 60 includes at least one first capillary wick 61 and at least one second capillary wick 63. The first capillary wick 61 includes a first hot end 613 and a first cold end 615, and the second capillary wick 63 includes a second hot end 633 and a second cold end 635. The first hot end 613 and the second hot end 633 are located in the heat source region I, and the first cold end 615 and the second cold end 635 are located in different condensation regions II.

[0079] A first gap 65 is formed between the first capillary wick 61 and the first side surface 43, and a second gap 67 is formed between the second capillary wick 63 and the second side surface 45. Both the first gap 65 and the second gap 67 serve as steam channels to facilitate the flow of steam.

[0080] A third gap 69 is formed between the first hot end 613 and the second hot end 633, and the third gap 69 connects the first gap 65 and the second gap 67. When the steam flowing in the first gap 65 and the second gap 67 flows to the heat source area I, it can flow fully through the connection of the third gap 69, which is conducive to realizing the steam interconnection in the first gap 65 and the second gap 67, thereby reducing the steam flow resistance and improving the heat dissipation power of the heat spreader 100. Secondly, the steam interconnection in the first gap 65 and the second gap 67 is also conducive to balancing the steam pressure in the first gap 65 and the second gap 67, making the heat conduction more uniform.

[0081] Please refer to Figure 7, which is a top view of the first capillary structure 50' and the second capillary structure 60' in the heat spreader 100' provided in the related technology. The first capillary structure 50' in the heat spreader 100' has the same structure as the first capillary structure 50. The difference from the heat spreader 100 is that the second capillary structure 60' in the heat spreader 100' is an integral structure. That is, the second capillary structure 60' located in the heat source area I does not have a third gap 69. This is equivalent to the first gap 65' and the second gap 67' being separated by the second capillary structure 60'. The steam in the first gap 65' and the second gap 67' is difficult to communicate with each other, so the steam is difficult to distribute quickly and evenly, and the steam flow resistance is large. At the same time, it leads to uneven distribution of the return coolant, resulting in the phenomenon of local dry burning of the heat spreader 100'.

[0082] Referring again to Figure 6, in this embodiment, the first hot end 613 and the second hot end 633 are arranged along the first direction X, and the first cold end 615 and the second cold end 635 are arranged along the second direction Y. The first cold end 615 and the second cold end 635 are located on both sides of the heat source region I. Along the first direction X, the projections of the first hot end 613 and the second hot end 633 at least partially overlap, that is, the projections of the first hot end 613 and the second hot end 633 can completely overlap or partially overlap. In this embodiment, the projections of the first hot end 613 and the second hot end 633 partially overlap. The projections of the first hot end 613 and the second hot end 633 at least partially overlap, which is beneficial for the first hot end 613 and the second hot end 633 to cover the heat source area I as much as possible along the second direction Y. This allows the condensed and recirculated coolant to reach the heat source area I along the first capillary wick 61 and the second capillary wick 63, and to spread out more evenly and quickly in the heat source area I. This is beneficial for increasing the area of ​​the heat source area I that absorbs the heat conducted by the heat source element 226, and thus for the heat spreader 100 to quickly absorb the heat generated by the heat source element 226. Furthermore, the recirculated coolant can reach the heat source area I along the first capillary wick 61 and the second capillary wick 63, which is beneficial for the uniform distribution of coolant in the heat source area I, and thus helps to prevent the phenomenon of local dry burning of the heat spreader 100 due to uneven distribution of coolant.

[0083] In this embodiment, the first direction X, the second direction Y, and the third direction Z all intersect. In this embodiment, the first direction X, the second direction Y, and the third direction Z are all perpendicular to each other. In other embodiments, the first direction X, the second direction Y, and the third direction Z may not be perpendicular to each other, as long as the first direction X, the second direction Y, and the third direction Z are not coplanar.

[0084] In other embodiments, when the number of condensing zones II is greater than two, each condensing zone II is provided with at least one first cold end 615 or at least one second cold end 635. The number and relative positions of the condensing zones II can be set according to factors such as the structural design and space size of the terminal device 200.

[0085] In some embodiments, the length of the heat source region I along the second direction Y is defined as L1, and the length of the first hot end 613 and the second hot end 633 projected onto the first direction X along the same length is defined as L2, satisfying: 1 / 2 ≤ L2 / L1 ≤ 1. When 1 / 2 ≤ L2 / L1, the first hot end 613 and the second hot end 633 can cover the length L1 of the heat source region I along the second direction Y as much as possible, so that the condensed and returned coolant can reach the heat source region I along the first capillary wick 61 and the second capillary wick 63, and thus absorb heat evenly as quickly as possible; when L2 / L1 ≤ 1, under the premise of ensuring that heat is absorbed evenly and quickly, the overall length of the second capillary structure 60 in the heat source region I can be reduced, and there is no need to set the first hot end 613 and the second hot end 633 too long. Furthermore, if L2 is too long, the first hot end 613 or the second hot end 633 may obstruct the flow of steam in the third gap 69.

[0086] Let W1 be the width of the heat source region I along the first direction X, W2 be the distance between the first hot end 613 and the second hot end 633, W3 be the width of the first hot end 613, and W4 be the width of the second hot end 633. Then 1 / 2 ≤ W2 / W3 ≤ 3, 1 / 2 ≤ W2 / W4 ≤ 3, W3 / W1 ≤ 1 / 3, and W4 / W1 ≤ 1 / 3. The distance W2 between the first hot end 613 and the second hot end 633 is the width of the third gap 69 along the first direction X. Limiting 1 / 2 ≤ W2 / W3 ≤ 3 and 1 / 2 ≤ W2 / W4 ≤ 3 helps to reserve a certain width for the third gap 69. A larger width of the third gap 69 facilitates steam flow. When the width W3 of the first hot end 613 and the width W4 of the second hot end 633 are within a certain range, it helps to quickly and evenly absorb heat. Therefore, limiting the relationship between width W1, distance W2, width W3, and the width W4 helps to achieve a balance between steam flow and uniform heat absorption. When the shape of the heat source region I is irregular, both length L1 and width H1 are calculated using their maximum values.

[0087] In the second capillary structure 60 shown in Figure 6, the first hot end 613 includes a first portion 6131, and the second hot end 633 includes a second portion 6332. Both the first portion 6131 and the second portion 6332 extend along the second direction Y, and the extension directions of the first portion 6131 and the second portion 6332 are opposite. The first portion 6131 is the first hot end 613, and the second portion 6332 is the second hot end 633. The third gap 69 located between the first hot end 613 and the second hot end 633 connects the first gap 65 and the second gap 67 along the second direction Y.

[0088] Please refer to Figures 8 and 9, which are top views of the first capillary structure 50 and the second capillary structure 60 provided in some embodiments of this application, respectively. Referring to Figure 8, unlike the embodiment shown in Figure 6, in the embodiment shown in Figure 8, the first hot end 613a of the second capillary structure 60 includes a first portion 6131a and a third portion 6133a. The third portion 6133a is connected to the end of the first portion 6131a away from the first cold end 615, and the third portion 6133a is bent relative to the first portion 6131a. The second hot end 633a of the second capillary structure 60 includes a second portion 6332a and a fourth portion 6334a. The fourth portion 6334a and the second portion 6332a are connected to the end of the second cold end 635, and the fourth portion 6334a is bent relative to the second portion 6332a. It is understood that in other embodiments, the third portion 6133a may be bent relative to the first portion 6131a, and the fourth portion 6334a and the second portion 6332a may extend in the same direction; or the third portion 6133a and the first portion 6131a may extend in the same direction, and the fourth portion 6334a may be bent relative to the third portion 6133a. That is, the third portion 6133a may be bent relative to the first portion 6131a; and / or the fourth portion 6334a may be bent relative to the second portion 6332a. The provision of relatively bent third portions 6133a and / or fourth portions 6334a facilitates the extension of the first hot end 613a and / or the second hot end 633a in the heat source region I in different directions, thereby enabling the liquid coolant to conduct heat from different directions.

[0089] The bending direction of the third part 6133a and / or the fourth part 6334a can be along the first direction X, or along a direction that intersects both the first direction X and the second direction Y. In the embodiment shown in FIG8, the third part 6133a bends relative to the first part 6131a along the first direction X, and the third part 6133a bends toward the second part 6332a; the fourth part 6334a bends relative to the second part 6332a along the first direction X, and the fourth part 6334a bends toward the first part 6131a. That is, the third part 6133a and the fourth part 6334a are located between the first part 6131a and the second part 6332a, which can increase the maximum width of the third gap 69a formed between the first hot end 613a and the second hot end 633a, thereby increasing the area for steam interconnection and facilitating the flow of steam in the third gap 69a.

[0090] Please refer to Figure 9. Unlike the embodiment shown in Figure 8, in the embodiment shown in Figure 9, the third portion 6133b of the first hot end 613b is bent away from the second portion 6332b; the fourth portion 6334b of the second hot end 633b is bent away from the first portion 6131b. That is, the third portion 6133b and the fourth portion 6334b are located on opposite sides of the first portion 6131b and the second portion 6332b. Therefore, the third gap 69b formed between the first hot end 613b and the second hot end 633b is unobstructed along the second direction Y, meaning the flow resistance of steam in the third gap 69b is small, which is beneficial for increasing the steam flow rate in the third gap 69b.

[0091] Please refer to Figures 10, 11, 12, and 13, which are top views of the first capillary structure 50 and the second capillary structure 60 provided in other embodiments of this application, respectively. Referring to Figure 10, unlike the embodiment shown in Figure 6, in the embodiment shown in Figure 10, the first hot end 613c and the second hot end 633c are arranged along the second direction Y, and the first cold end 615 and the second cold end 635 are arranged along the second direction Y. Along the second direction Y, the projections of the first hot end 613c and the second hot end 633c at least partially overlap. In the embodiment shown in Figure 10, along the second direction Y, the projections of the first hot end 613c and the second hot end 633c completely overlap. The projections of the first hot end 613c and the second hot end 633c at least partially overlap, which is beneficial for the first hot end 613c and the second hot end 633c to cover the heat source region I as much as possible along the first direction X, so that the condensed and recirculated coolant can reach the heat source region I along the first capillary wick 61 and the second capillary wick 63, thereby absorbing heat quickly and evenly. The embodiment shown in Figure 10 is applicable to cases where the width of the heat source region I along the first direction X is relatively narrow.

[0092] The first hot end 613c includes a first part 6131c, and the second hot end 633c includes a second part 6332c. Both the first part 6131c and the second part 6332c extend along the second direction Y, and the extension directions of the first part 6131c and the second part 6332c are opposite. The first part 6131c is the first hot end 613c, and the second part 6332c is the second hot end 633c. The third gap 69c located between the first hot end 613c and the second hot end 633c connects the first gap 65 and the second gap 67 along the first direction X.

[0093] Please refer to Figure 11. Unlike the embodiment shown in Figure 10, in the embodiment shown in Figure 11, the first hot end 613d includes a first portion 6131d and a third portion 6133d. The third portion 6133d and the first portion 6131d are connected at the end opposite to the first cold end 615. The first portion 6131d extends along the second direction Y, and the third portion 6133d is bent relative to the first portion 6131d. And / or the second hot end 633d includes a second portion 6332d and a fourth portion 6334d. The fourth portion 6334d and the second portion 6332d are connected at the end opposite to the second cold end 635. The second portion 6332d extends along the second direction Y, and the fourth portion 6334d is bent relative to the second portion 6332d. In other embodiments, the third portion 6133d may be bent relative to the first portion 6131d, and the fourth portion 6334d and the second portion 6332d may extend in the same direction; or the third portion 6133d and the first portion 6131d may extend in the same direction, and the fourth portion 6334d may be bent relative to the third portion 6133d. That is, the third portion 6133d may be bent relative to the first portion 6131d; and / or the fourth portion 6334d may be bent relative to the second portion 6332d. The provision of relatively bent third portions 6133d and / or fourth portions 6334d facilitates the extension of the first hot end 613d and / or the second hot end 633d in the heat source region I in different directions, thereby enabling the liquid coolant to conduct heat from different directions.

[0094] The bending direction of the third part 6133d and / or the fourth part 6334d can be along the first direction X, or along a direction that intersects both the first direction X and the second direction Y. In this embodiment, the third part 6133d bends relative to the first part 6131d along the first direction X, and the fourth part 6334d bends relative to the first part 6131d along the first direction X. The first direction X intersects the second direction Y, and the third part 6133d and the fourth part 6334d are located between the first part 6131d and the second part 6332d. Compared with the embodiments shown in FIG. 6, FIG. 8 or FIG. 9, the direction in which the third gap 69d connects the first gap 65 and the second gap 67 in the embodiment shown in FIG. 11 changes, and a more suitable structure of the heat spreader 100 can be selected according to the actual shape of the heat source element 226.

[0095] Please refer to Figure 12. Unlike the embodiment shown in Figure 11, in the embodiment shown in Figure 12, the first hot end 613e includes a first portion 6131e, a third portion 6133e, and a fifth portion 6135e. The fifth portion 6135e and the third portion 6133e are connected at the ends opposite to the first portion 6131e, and the fifth portion 6135e extends relative to the third portion 6133e away from the second hot end 633e. The second hot end 633e includes a second portion 6332e, a fourth portion 6334e, and a sixth portion 6336e. The sixth portion 6336e and the fourth portion 6334e are connected at the ends opposite to the second portion 6332e, and the sixth portion 6336e extends relative to the fourth portion 6334e away from the first hot end 613e. It can be understood that in other embodiments, the fifth portion 6135e may be bent relative to the third portion 6133e; or the sixth portion 6336e may be bent relative to the fourth portion 6334e. The arrangement of relatively bent third and fifth portions 6133e and / or relatively bent fourth and sixth portions 6336e facilitates the extension of the first hot end 613e and / or the second hot end 633e in the heat source region I in different directions, thereby enabling the liquid coolant to conduct heat from different directions. The third gap 69e, which connects the first gap 65 and the second gap 67, is located between the third portion 6133e and the fourth portion 6334e, and the third gap 69e connects the first gap 65 and the third gap 67 along the second direction Y.

[0096] Please refer to Figure 13. Unlike the embodiment shown in Figure 12, in the embodiment shown in Figure 13, the first hot end 613f includes a first part 6131f and a third part 6133f. The third part 6133f and the first part 6131f are connected at the end opposite to the first cold end 615. The first part 6131f extends along the second direction Y, and both ends of the third part 6133f protrude relative to the first part 6131f. And / or the second hot end 633f includes a second part 6332f and a fourth part 6334f. The fourth part 6334f and the second part 6332f are connected at the end opposite to the second cold end 635. The second part 6332f extends along the second direction Y, and both ends of the fourth part 6334f protrude relative to the second part 6332f.

[0097] The protrusion direction of the third portion 6133f and / or the fourth portion 6334f can be along the first direction X, or along a direction that intersects both the first direction X and the second direction Y. In this embodiment, the third portion 6133f protrudes relative to the first portion 6131f along the first direction X, and the fourth portion 6334f protrudes relative to the second portion 6332f along the first direction X. The third gap 69f connects the first gap 65 and the second gap 67 along the second direction Y.

[0098] The following performance tests are conducted using specific embodiments and comparative examples of the heat spreader 100.

[0099] The steam flow in the heat spreader 100' (comparative example) provided by related technologies and the heat spreader 100 provided in the embodiments of this application were simulated and tested. The heating element (not shown) was brought into contact with the heat spreader 100' and the heat spreader 100 respectively, and the power consumption of the heating element was set to 30W. The steam pressure in different regions of the heat spreader 100' and the heat spreader 100 was tested respectively.

[0100] Please refer to Figures 14 and 15. Figure 14 is a simulation test diagram of steam flow in the heat spreader 100 provided in the embodiment, and Figure 15 is a simulation test diagram of steam flow in the heat spreader 100' provided in the comparative example. According to the test results, the steam flow pressure drop in heat source region I and condensation region II of heat spreader 100' is approximately 664 Pa; the steam flow pressure drop in heat source region I and condensation region II of heat spreader 100 is approximately 621 Pa. This corresponds to a steam flow pressure drop of 43 Pa less than that of heat spreader 100' when the power consumption of the heating element is 30 W, representing a reduction of approximately 7%. A smaller steam flow pressure drop in heat source region I and condensation region II indicates a more uniform steam distribution.

[0101] The heating element is brought into contact with the heat spreader 100' and the heat spreader 100 respectively. Different power consumption P of the heating element is set, and after stabilizing for a certain period of time, the temperature T of the heating element on the heat spreader 100' and the heat spreader 100 is measured. j Temperature T of heat source region I 热 The temperature T of the first cold end is 615. 冷1 The temperature T of the second cold end is 635. 冷1 And calculate T 热 -T 冷1 T 热 -T 冷2 And thermal resistance, where the formula for calculating thermal resistance R is R = (T j -T0) / P, where T0 is the ambient temperature during the test, T0=28℃, and the test results and calculation results are shown in Table 1.

[0102] Table 1

[0103] The results in Table 1 show that when the power consumption of the heating element is 35W, the temperature T of the heating element connected to the heat spreader 100 is... j Compared to the temperature T of the heating element connected to the heat spreader 100' jThe temperature is reduced by 0.43℃, meaning that after both the heat spreader 100' and the heat spreader 100 have been working for a period of time, the heat spreader 100 can more effectively reduce the temperature T of the heating element. j .

[0104] Temperature T of heating element j Approaching 100℃, or the temperature difference between heat source zone I and condensation zone II is greater than 5℃ (i.e., T). 热 -T 冷1 Or T 热 -T 冷 At temperatures above 5°C, this is typically the upper limit for testing the heat dissipation performance of a vapor chamber 100. 热 -T 冷1 Or T 热 -T 冷 A temperature difference greater than 5°C indicates an excessively large temperature difference between heat source zone I and condensation zone II, suggesting untimely coolant return and a risk of dry burning. Table 1 shows that the test limits for heat spreader 100' and heat spreader 100 are 35W and 50W respectively, meaning that heat spreader 100 has a performance improvement of approximately 10W-15W in heat dissipation power consumption compared to heat spreader 100'. Furthermore, based on thermal resistance calculations, when the power consumption of the heating element is 35W, the thermal resistance of heat spreader 100 decreases by 0.01°C / W.

[0105] The heat dissipation plate 100' and the heat dissipation plate 100 are assembled with the fan 2281 and the fins 2283 to form a heat dissipation assembly 228. Then, the heat-generating element is brought into contact with the heat dissipation assembly 228 of the comparative example and the embodiment. Different power consumption P of the heat-generating element is set respectively, and after stabilizing for a certain period of time, the same test as the above test is performed. The test results and calculation results are shown in Table 2.

[0106] Table 2

[0107] As can be seen from the test results in Table 2, when the heat dissipation plate 100 is assembled into the heat dissipation component 228, the heat dissipation component 228 provided in the embodiment is most suitable for a heat-generating element with a power consumption of 45W, and the heat dissipation component 228 provided in the comparative example is most suitable for a heat-generating element with a power consumption of 35W. Through the calculation of thermal resistance, for a heat-generating element with a power consumption of 35W, the thermal resistance of the heat dissipation component 228 provided in the embodiment can be reduced by 0.38℃ / W, and for a heat-generating element with a power consumption of 40W, the thermal resistance of the heat dissipation component 228 provided in the embodiment can be reduced by 0.35℃ / W.

[0108] The heat dissipation component 228 provided in the embodiment and the heat dissipation component provided in the comparative example are respectively assembled into the terminal device 200. The heat dissipation component 228 is connected to the heat source element 226 in the terminal device 200. After the terminal device 200 runs for the same amount of time, the temperature of the heat source element 226 is tested to be 82°C and 85°C respectively. That is, after the improvement of the heat spreader 100 in the embodiment of this application, the temperature of the heat source element 226 can be reduced by 3°C.

[0109] The test results above verify that, compared to the heat spreader 100' provided in the comparative example, the heat spreader 100 provided in this embodiment has a third gap 69 formed between the first hot end 613 and the second hot end 633. The third gap 69 connects the first gap 65 and the second gap 67, allowing steam to communicate between the first gap 65 and the second gap 67 through the connection of the third gap 69. This helps to reduce the flow resistance of steam and improve the heat dissipation power of the heat spreader 100. Secondly, it also helps to balance the steam pressure in the first gap 65 and the second gap 67, making the heat conduction more uniform. In addition, the projections of the first hot end 613 and the second hot end 633 overlap, which helps the coolant in the heat source area I to spread more evenly and quickly, thus helping the heat spreader 100 to quickly absorb the heat generated by the heat source element 226. Furthermore, the returning coolant can reach the heat source area I along the first capillary 61 and the second capillary 63, which is beneficial for the uniform distribution of steam in the heat source area I.

[0110] The above embodiments are only used to illustrate the technical solutions of this application and are not intended to limit it. Although this application has been described in detail with reference to the above preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions to the technical solutions of this application should not depart from the spirit and scope of the technical solutions of this application.

Claims

1. A heat spreader, characterized in that, The heat spreader is divided into a heat source zone and at least two condensation zones, and includes: case; First capillary structure; and A second capillary structure is superimposed on the first capillary structure and located in the housing. The second capillary structure includes at least one first capillary core and at least one second capillary core. A first gap is formed between the first capillary core and the housing, and a second gap is formed between the second capillary core and the housing. The first capillary core includes a first hot end and a first cold end, and the second capillary core includes a second hot end and a second cold end. The first hot end and the second hot end are located in the heat source region, and the first cold end and the second cold end are located in different condensation regions. A third gap is formed between the first hot end and the second hot end, and the third gap connects the first gap and the second gap.

2. The heat spreader according to claim 1, characterized in that, The first hot end and the second hot end are arranged along a first direction, and the first cold end and the second cold end are arranged along a second direction. Along the first direction, the projections of the first hot end and the second hot end at least partially overlap, and the first direction and the second direction intersect.

3. The heat spreader according to claim 2, characterized in that, The first hot end includes a first portion, and the second hot end includes a second portion; both the first portion and the second portion extend along the second direction.

4. The heat spreader according to claim 3, characterized in that, The first hot end further includes a third part, which is connected to the end of the first part away from the first cold end, and the third part is bent relative to the first part; and / or The second hot end also includes a fourth part, which is connected to the end of the second part away from the second cold end, and the fourth part is bent relative to the second part.

5. The heat spreader according to claim 4, characterized in that, The third portion bends toward the second portion; and / or The fourth part bends toward the first part.

6. The heat spreader according to claim 4, characterized in that, The third part bends away from the second part; and / or The fourth part bends away from the first part.

7. The heat spreader according to claim 3, characterized in that, Along the first direction, the width of the heat source area is W1, the distance between the first hot end and the second hot end is W2, the width of the first hot end is W3, and the width of the second hot end is W4, satisfying: 1 / 2≤W2 / W3≤3, 1 / 2≤W2 / W4≤3, W3 / W1≤1 / 3, W4 / W1≤1 / 3.

8. The heat spreader according to claim 3, characterized in that, Along the second direction, the length of the heat source region is L1, and the length of the first hot end and the second hot end that coincide along the first direction is L2, satisfying: 1 / 2≤L2 / L1≤1.

9. The heat spreader according to claim 1, characterized in that, The first hot end and the second hot end are arranged along a second direction, and the first cold end and the second cold end are arranged along the second direction. Along the second direction, the projections of the first hot end and the second hot end at least partially overlap.

10. The heat spreader according to claim 9, characterized in that, The first hot end includes a first part and a third part, the third part and the end of the first part opposite to the first cold end are connected, the first part extends along the second direction, and the third part is bent relative to the first part; and / or The second hot end includes a second part and a fourth part, the fourth part and the second part being connected at the end opposite to the second cold end, the second part extending along the second direction, and the fourth part being bent relative to the second part.

11. The heat spreader according to claim 10, characterized in that, The third portion bends relative to the first portion along a first direction, and the first direction intersects with the second direction; and / or The fourth part bends relative to the first part along a first direction, and the first direction intersects with the second direction.

12. The heat spreader according to claim 10 or 11, characterized in that, The first hot end further includes a fifth portion, which is connected to the end of the third portion away from the first portion, and the fifth portion extends away from the second hot end relative to the third portion; and / or The second hot end also includes a sixth portion, which is connected to the end of the fourth portion away from the second portion, and the sixth portion extends away from the first hot end relative to the fourth portion.

13. The heat spreader according to claim 9, characterized in that, The first hot end includes a first part and a third part, the third part and the end of the first part opposite to the first cold end are connected, the first part extends along the second direction, and both ends of the third part protrude relative to the first part; And / or the second hot end includes a second portion and a fourth portion, the fourth portion and the second portion being connected at one end away from the second cold end, the second portion extending along the second direction, and both ends of the fourth portion protruding relative to the second portion.

14. The heat spreader according to any one of claims 1-13, characterized in that, The permeability of the second capillary structure is greater than that of the first capillary structure.

15. The heat spreader according to any one of claims 1-14, characterized in that, The housing includes a first surface and a second surface, which are disposed opposite to each other. A first capillary structure is disposed on the first surface, and a second capillary structure is disposed on the second surface, with the second capillary structure located on the surface of the first capillary structure.

16. A heat dissipation component, characterized in that, The heat dissipation assembly includes a heat spreader as described in any one of claims 1-15, the heat spreader further includes a fan and / or fins, the fins are disposed on the surface of the housing located in the condensation zone, and the fan is used to generate airflow toward the fins.

17. A terminal device, characterized in that, The terminal device includes: Heat source elements; and The heat dissipation plate according to any one of claims 1-15 or the heat dissipation assembly according to claim 16, wherein the heat source element is disposed in the heat source area of ​​the heat dissipation plate and is disposed on the side of the housing that is sequentially opposite to the second capillary structure and the first capillary structure.

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