Sheet-type heat pipe

Abstract

The present invention provides a sheet-shaped heat pipe that, when there are multiple objects to be cooled (heat sources), makes it difficult for heat from one object to be transferred to other objects. [Solution] The sheet-shaped heat pipe 1 according to the present invention forms an internal space S between a heat dissipation plate 2 and a heat receiving plate 3, and a capillary structure and a working fluid are sealed in the internal space S. The heat receiving plate 3 has a housing portion 11 that protrudes in the opposite direction from the heat dissipation plate 2, and the bottom portion 12 of the housing portion 11 has a plurality of heat receiving portions, at least one of the plurality of heat receiving portions is a first concave heat receiving portion 14 formed in a concave shape, and the capillary structure is arranged in the bottom portion 12 and the first concave heat receiving portion 14.

Description

Technical Field

[0001] The present invention relates to a sheet-shaped heat pipe that is mounted on a device having a heat source, receives heat from the heat source, and cools the heat source by heat transportation.

Background Art

[0002] A vapor chamber for cooling electronic components, which are heat-generating bodies such as semiconductor elements mounted on electric and electronic devices, has been proposed (for example, see Patent Document 1).

[0003] Patent Document 1 describes that heat transportation of two heat-generating bodies (100-1, 100-2) is performed and cooled by a heat transportation body (1) which is a single vapor chamber. The heat transportation body (1) includes a container (10) in which a cavity (13) is formed inside and which is thermally connected to the heat-generating bodies (100-1, 100-2), a working fluid enclosed in the cavity (13), a wick structure (14) provided in the cavity (13) through which the liquid-phase working fluid (L) flows, and a vapor flow path (15) provided in the cavity (13) through which the gas-phase working fluid (G) flows. And two heat-generating bodies (100-1, 100-2) are thermally connected to the second surface (22) of the other plate-like body (12) of the container (10).

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] In the case of the heat transporter (1) described in Patent Document 1, if the heat-generating element (100-1) is considerably hotter than the heat-generating element (100-2), the heat from the heat-generating element (100-1) may be conducted to the heat-generating element (100-2) via the liquid-phase working fluid (L) flowing through the second surface (22) and the wick structure (14), hindering the cooling of the heat-generating element (100-2), and there is a risk that the heat-generating element (100-2) will not be sufficiently cooled.

[0006] Therefore, the present invention aims to solve the above problems and provide a sheet-shaped heat pipe that makes it difficult for heat from one cooling target to be conducted to other cooling targets when there are multiple cooling targets (heat sources). [Means for solving the problem]

[0007] The sheet-shaped heat pipe of the present invention is a sheet-shaped heat pipe having an internal space formed between a first plate and a second plate, wherein a capillary structure and a working fluid are sealed in the internal space, the second plate has a housing portion that protrudes in the direction opposite to the first plate, the bottom surface of the housing portion has a plurality of heat receiving portions, at least one of the plurality of heat receiving portions is a first concave heat receiving portion formed in a concave shape, and the capillary structure is disposed between the bottom surface and the first concave heat receiving portion. [Effects of the Invention]

[0008] According to the present invention, when cooling multiple objects to be cooled (heat sources) with a single sheet-shaped heat pipe, it is possible to make it difficult for heat from one object to be cooled to be conducted to other objects to be cooled. [Brief explanation of the drawing]

[0009] [Figure 1] This is an upper perspective view of a sheet-like heat pipe according to the first embodiment of the present invention. [Figure 2] This is a lower perspective view of the sheet-like heat pipe of the same embodiment. [Figure 3] This is an exploded perspective view of the sheet-shaped heat pipe of the same embodiment. [Figure 4] This is a cross-sectional view AA in Figure 1. [Figure 5] This is a lower perspective view of a sheet-like heat pipe according to a second embodiment of the present invention. [Figure 6] This is a longitudinal cross-sectional view of the sheet-shaped heat pipe of the same embodiment. [Figure 7] This is a lower perspective view of a sheet-like heat pipe according to a third embodiment of the present invention. [Figure 8] This is a longitudinal cross-sectional view of the sheet-shaped heat pipe of the same embodiment. [Figure 9] This is a longitudinal cross-sectional view of a sheet-like heat pipe according to a fourth embodiment of the present invention. [Figure 10] This is a longitudinal cross-sectional view of a sheet-shaped heat pipe according to a fifth embodiment of the present invention. [Figure 11] This is a longitudinal cross-sectional view of a sheet-like heat pipe according to the sixth embodiment of the present invention. [Modes for carrying out the invention]

[0010] The following describes preferred embodiments of the present invention, using a sheet-type heat pipe (hereinafter referred to as "SHP") mounted on various devices (not shown) as an example. Not all of the configurations described below are essential requirements of the present invention.

[0011] Figures 1 to 4 show an SHP1 in the first embodiment of the present invention. The SHP1 is composed of a heat dissipation plate 2 as a first plate, a heat receiving plate 3 as a second plate, a first capillary structure 4, a second capillary structure 5, and a third capillary structure 6 as capillary structures housed in the heat receiving plate 3, and a working fluid (not shown). In this embodiment, the heat dissipation plate 2 and the heat receiving plate 3 are made of austenitic stainless steel, but they may also be made of an alloy mainly composed of titanium or copper.

[0012] As shown in FIGS. 1 and 4, the heat dissipation plate 2 is formed in a substantially rectangular thin plate shape, and has a flat portion 7 formed flat and a plurality of support portions 8 protruding in the direction of the heat receiving plate 3. The flat portion 7 and the support portions 8 of the heat dissipation plate 2 are integrally formed by drawing. Note that the heat dissipation plate 2 may be formed by etching.

[0013] The support portions 8 are formed in a hemispherical shape and are in contact with the first capillary structure 4. The plurality of support portions 8 in the present embodiment are arranged in an oblique lattice shape, but may be arranged in a regular triangular lattice shape, a square lattice shape, a rectangular lattice shape, a rectangular lattice shape, etc., or in an irregular arrangement as long as the first capillary structure 4 can be prevented from floating or being displaced.

[0014] Although not shown, a heat sink or the like, which is a radiator, may be brought into thermal contact with the flat portion 7 or the support portions 8 of the heat dissipation plate 2 in order to enhance the heat dissipation effect.

[0015] As shown in FIGS. 2 to 4, the heat receiving plate 3 is formed in a thin plate shape, and has an outer peripheral portion 10 that joins with the outer peripheral portion 9 of the heat dissipation plate 2, and a housing portion 11 that protrudes in a direction opposite to the heat dissipation plate 2. The housing portion 11 integrally has a bottom surface portion 12, an inclined wall portion 13 that connects the outer peripheral portion 10 and the bottom surface portion 12, and a plurality (two in the present embodiment) of heat receiving portions recessed in the bottom surface portion 12, namely, a first concave heat receiving portion 14 and a second concave heat receiving portion 15. The heat receiving plate 3 of the present embodiment is formed by drawing.

[0016] The bottom portion 16 of the first concave heat receiving portion 14 is in thermal contact with a heat source P1, which is a cooling target of various devices on which the SHP1 is mounted, and the bottom portion 17 of the second concave heat receiving portion 15 is in thermal contact with a heat source P2, which is a cooling target of various devices on which the SHP1 is mounted. The first concave heat receiving portion 14 and the heat source P1, and the second concave heat receiving portion 15 and the heat source P2 may be in thermal contact via a heat conductor (not shown) having a high thermal conductivity without direct contact.

[0017] The first concave heat receiving part 14 and the second concave heat receiving part 15 are formed in a substantially rectangular shape (rounded rectangular shape) in a plan view. The first concave heat receiving part 14 and the second concave heat receiving part 15 of this embodiment have the same shape. Note that the first concave heat receiving part 14 and the second concave heat receiving part 15 may have other polygonal shapes, circular shapes, or irregular shapes in a plan view according to the shapes of the heat sources P1 and P2.

[0018] The outer peripheral part 9 of the heat dissipation plate 2 and the outer peripheral part 10 of the heat receiving plate 3 are joined by a method such as diffusion bonding, laser welding, or brazing, and an internal space S is formed. In the internal space S, a first capillary structure 4, a second capillary structure 5, a third capillary structure 6, and a working fluid are accommodated (enclosed), and the inside of the internal space S is evacuated from the nozzle part 18.

[0019] The first capillary structure 4, the second capillary structure 5, and the third capillary structure 6 have a capillary structure with fine gaps evenly distributed throughout in order to generate a strong capillary force on the liquid-phase working fluid. Examples include metal fiber wicks, metal fiber sintered wicks, metal powder sintered wicks, metal fiber felts, metal fiber sintered felts, metal powder sintered filters, powder sintered plates, flat mesh bodies formed by arranging metal wires vertically and horizontally and weaving them, flat metal foils (not shown) having fine grooves intersecting vertically and horizontally on the surface to generate capillary force and holes arranged at equal intervals at appropriate positions of the grooves, non-woven fabrics (not shown), etc. Note that since the size of the gaps can be changed by changing the thickness and length of the metal fibers, various types of metal fiber wicks can be adopted. The same applies to metal fiber sintered wicks, metal powder sintered wicks, metal fiber felts, metal fiber sintered felts, metal powder sintered filters, powder sintered plates, mesh bodies, metal foils, and non-woven fabrics.

[0020] The first capillary structure 4 of this embodiment is a flat mesh body formed by arranging metal wires vertically and horizontally and weaving them, and is formed substantially the same as the shape of the bottom surface part 12 of the heat receiving plate 3 in a plan view. However, other outer shapes may be used as long as they can generate a capillary force that allows the liquid-phase working fluid to flow.

[0021] The first capillary structure 4 is housed in the housing section 11 while resting on the bottom surface 12 of the heat receiving plate 3.

[0022] The second capillary structure 5 in this embodiment is a sintered felt of stainless steel fibers and is housed in the first concave heat receiving section 14. The third capillary structure 6 in this embodiment is housed in the second concave heat receiving section 15. The upper surfaces of the second capillary structure 5 and the third capillary structure 6 are flush with the bottom surface 12 and are in contact with the first capillary structure 4. The second capillary structure 5 is formed to be substantially the same as the internal shape of the first concave heat receiving section 14, and the third capillary structure 6 is formed to be substantially the same as the internal shape of the second concave heat receiving section 15. In this embodiment, the fine gaps between the second capillary structure 5 and the third capillary structure 6 are, on average, narrower than the fine gaps between the first capillary structure 4. However, the volume of the gaps per unit volume is larger for the second capillary structure 5 and the third capillary structure 6 than for the first capillary structure 4. Therefore, the amount of liquid-phase working fluid that can be held per unit volume (holding rate) is greater for the second capillary structure 5 and the third capillary structure 6 than for the first capillary structure 4.

[0023] In this embodiment, the second capillary structure 5 and the third capillary structure 6 are made of different types of sintered metal fibers, and the second capillary structure 5 has a greater capacity to hold liquid-phase working fluid per unit volume (retention rate) than the third capillary structure 6. That is, the relationship of the retention rates of liquid-phase working fluid is first capillary structure 4 < second capillary structure 5 < third capillary structure 6. However, the relationship of the retention rates of liquid-phase working fluid does not necessarily have to be first capillary structure 4 < second capillary structure 5 < third capillary structure 6, and can be appropriately changed depending on the temperatures of the heat sources P1, P2, and P3.

[0024] The internal space S contains more working fluid than the first capillary structure 4, the second capillary structure 5, and the third capillary structure 6 can hold when the working fluid is entirely in the liquid phase, and when the working fluid is entirely in the liquid phase, the first concave heat receiving section 14 and the second concave heat receiving section 15 are filled with liquid working fluid. Because the second capillary structure 5 can hold more liquid working fluid than the third capillary structure 6, the total amount of liquid working fluid in the first concave heat receiving section 14 is greater than the total amount of liquid working fluid in the second concave heat receiving section 15.

[0025] The support column 8 of the heat dissipation plate 2 and the first capillary structure 4, the heat receiving plate 3 and the first capillary structure 4, the heat receiving plate 3 and the second capillary structure 5, the heat receiving plate 3 and the third capillary structure 6, the first capillary structure 4 and the second capillary structure 5, and the first capillary structure 4 and the third capillary structure 6 are in contact with each other, but they may also be joined by methods such as diffusion bonding, laser welding, or brazing.

[0026] When heat sources P1 and P2 are below a predetermined temperature (low temperature), the working fluid is in the liquid phase and is sufficiently held in the gaps of the first capillary structure 4, the gaps of the second capillary structure 5, the gaps of the third capillary structure 6, the first concave heat receiving section 14, and the second concave heat receiving section 15. However, when heat sources P1 and P2 reach temperatures above a predetermined temperature (high temperature), the working fluid absorbs heat and vaporizes, increasing the amount of gaseous working fluid, while the amount of liquid working fluid decreases. Since the amount of liquid working fluid held in the first concave heat receiving section 14 is greater than the amount of liquid working fluid held in the second concave heat receiving section 15, even when the amount of liquid working fluid decreases, liquid working fluid is always held in the first concave heat receiving section 14.

[0027] Here, we will explain the heat transport of the working fluid in the internal space S of the SHP1. Here, we will explain the case where the heat source P1 is at a lower temperature than the heat source P2. By bringing the first concave heat receiving section 14, which holds a large amount of liquid-phase working fluid, into thermal contact with the lower-temperature heat source P1, and the second concave heat receiving section 15, which holds a smaller amount of liquid-phase working fluid, into thermal contact with the higher-temperature heat source P2, it becomes more difficult for heat from the heat source P2 to be conducted to the heat source P1.

[0028] The liquid-phase working fluid is held in the gaps between the first capillary structure 4, the second capillary structure 5, and the third capillary structure 6, and also fills the first concave heat receiving section 14 and the second concave heat receiving section 15. When the temperature of heat sources P1 and P2 rises, the liquid-phase working fluid receives heat through the heat receiving plate 3 (bottom 16, 17) and becomes a gaseous working fluid, which then moves to the heat dissipation plate 2 side. At this time, even if heat from heat source P2 is conducted to the first concave heat receiving section 14 side via the bottom surface 12 or the gaseous working fluid, the liquid-phase working fluid is held within the first concave heat receiving section 14, so the heat from heat source P2 is received by this liquid-phase working fluid and is extremely difficult to transfer to heat source P1. The gaseous working fluid comes into thermal contact with the heat dissipation plate 2, causing the heat dissipation plate 2 to absorb heat from the working fluid, which is then released from the heat dissipation plate 2 to the outside of the SHP1. As the temperature of the gaseous working fluid decreases, it condenses into a liquid phase and moves towards the heat receiving plate 3, where it is held by the first capillary structure 4. If the liquid phase working fluid contained in the first concave heat receiving section 14 and the second concave heat receiving section 15 continues to absorb heat from heat sources P1 and P2, the capillary force of the first capillary structure 4, the second capillary structure 5, and the third capillary structure 6 causes the liquid phase working fluid held in the first capillary structure 4 to move to the second capillary structure 5 and the third capillary structure 6, where it is held inside the first capillary structure 4, the first concave heat receiving section 14, and the second concave heat receiving section 15. In this way, heat is transported within the SHP1 by the working fluid, and the heat sources P1 and P2 are cooled, thereby mitigating the temperature rise of the equipment.

[0029] The SHP1 has a flat heat receiving section 19 formed flatly on its bottom surface 12, and not only the first concave heat receiving section 14 and the second concave heat receiving section 15, but also the flat heat receiving section 19 on the bottom surface 12 can come into thermal contact with the heat source P3 to be cooled, and the heat source P3 can be cooled by heat transport inside the SHP1.

[0030] In this embodiment, the first capillary structure 4, the second capillary structure 5, and the third capillary structure 6 are all different types of capillary structures. However, they may all be the same type of capillary structure, and their retention rates for the liquid phase working fluid may all be the same. In that case, the first capillary structure 4, the second capillary structure 5, and the third capillary structure 6 may be formed as a single unit. Alternatively, the first capillary structure 4 and the second capillary structure 5 may be the same type of capillary structure to have the same retention rate for the liquid phase working fluid, while the third capillary structure 6 may be a different type of capillary structure to have a different retention rate for the liquid phase working fluid. In that case, the first capillary structure 4 and the second capillary structure 5 may be formed as a single unit. Alternatively, the first capillary structure 4 and the third capillary structure 6 may be made of the same type of capillary structure to have the same retention rate of the liquid phase working fluid, while the second capillary structure 5 may be made of a different type of capillary structure to have a different retention rate of the liquid phase working fluid. In that case, the first capillary structure 4 and the third capillary structure 6 may be formed as a single unit.

[0031] As described above, the SHP1 of this embodiment is a sheet-shaped heat pipe 1 having an internal space S formed between a heat dissipation plate 2 and a heat receiving plate 3, the internal space S containing a capillary structure and a working fluid, the heat receiving plate 3 having a housing portion 11 that protrudes in the opposite direction to the heat dissipation plate 2, the bottom portion 12 of the housing portion 11 having a plurality of heat receiving portions, at least one of the plurality of heat receiving portions being a first concave heat receiving portion 14 formed in a concave shape, and the capillary structure is arranged in the bottom portion 12 and the first concave heat receiving portion 14. By bringing the first concave heat receiving section 14, which has a large capacity to hold liquid-phase working fluid, into thermal contact with a low-temperature heat source P1, and the second concave heat receiving section 15, which has a small capacity to hold liquid-phase working fluid, into thermal contact with a high-temperature heat source P2, even if the temperatures of heat sources P1, P2, and P3 rise, it is possible to make it difficult for heat from heat sources P2 and P3 to be conducted to heat source P1 by the liquid-phase working fluid within the first concave heat receiving section 14.

[0032] Furthermore, the SHP1 of this embodiment has a second concave heat receiving section 15 in which a plurality of heat receiving sections are formed in a concave shape, and a third capillary structure 6 is disposed in the second concave heat receiving section 15, and the fluid retention rate of at least one of the second capillary structure 5 disposed in the first concave heat receiving section 14 and the third capillary structure 6 disposed in the second concave heat receiving section 15 may be equivalent to the fluid retention rate of the first capillary structure 4 disposed in the bottom section 12. In that case, the liquid phase fluid can be uniformly held in the first capillary structure 4 and at least one of the second capillary structure 5 and the third capillary structure 6.

[0033] Furthermore, in this embodiment, the working fluid retention rates of the first capillary structure 4 located on the bottom surface 12, the second capillary structure 5 located on the first concave heat receiving section 14, and the third capillary structure 6 located on the second concave heat receiving section 15 are all different. Therefore, when the temperatures of the heat sources P1, P2, and P3 to be cooled are all different, it is possible to select a capillary structure with an appropriate working fluid retention rate according to the temperature.

[0034] Furthermore, the SHP1 of this embodiment has a structure in which multiple heat receiving sections are in thermal contact with different heat sources P1, P2, and P3, and when the temperatures of heat sources P1 and P2 are different, the second concave heat receiving section 15, which has a small capacity to hold working fluid, is in thermal contact with the heat source P2, which has a higher temperature, and the first concave heat receiving section 14, which has a large capacity to hold working fluid, is in thermal contact with the heat source P1, which has a lower temperature. As a result, even if the temperatures of heat sources P1, P2, and P3 rise, liquid-phase working fluid tends to remain in the first concave heat receiving section 14, and the liquid-phase working fluid in the first concave heat receiving section 14 makes it difficult for heat from heat source P2 to be conducted to heat sources P1 and P3.

[0035] Furthermore, in this embodiment of the SHP1, the fluid retention rate of the working fluid in the first capillary structure 4 located on the bottom surface 12, the fluid retention rate of the second capillary structure 5 located on the first concave heat receiving section 14, and the fluid retention rate of the third capillary structure 6 located on the second concave heat receiving section 15 may all be the same. In that case, the liquid phase working fluid held in the first capillary structure 4, the second capillary structure 5, and the third capillary structure 6 can be made uniform.

[0036] Furthermore, in this embodiment, the SHP1 has a first capillary structure 4 disposed on the bottom surface 12 which is a mesh body made of woven metal wires, and a second capillary structure 5 and a third capillary structure 6 disposed on the first concave heat receiving section 14 and the second concave heat receiving section 15 which are made of sintered fiber felt made of sintered metal fibers. Since sintered fiber felt has a higher retention rate of liquid-phase working fluid than mesh body, it is possible to easily move the liquid-phase working fluid from the first capillary structure 4 to the second capillary structure 5 and the third capillary structure 6. As a result, it is possible to easily store liquid-phase working fluid in the first concave heat receiving section 14 and the second concave heat receiving section 15.

[0037] Furthermore, in this embodiment, the SHP1 is a flat heat receiving section 19 in which at least one of the multiple heat receiving sections is formed flat. Therefore, the heat source P3 can be cooled by bringing it into thermal contact with the flat heat receiving section 19, which is not formed in a concave shape.

[0038] Figures 5 and 6 show the SHP1A in the second embodiment of the present invention. Here, the differences from the first embodiment will be explained, and the explanation of the common points with the first embodiment will be omitted. This embodiment uses a heat receiving plate 3A in which the area of ​​the first concave heat receiving section 14A in plan view is formed to be larger than that of the second concave heat receiving section 15. The depth of the first concave heat receiving section 14A and the depth of the second concave heat receiving section 15 are the same, but since the area of ​​the first concave heat receiving section 14A in plan view is larger than that of the second concave heat receiving section 15, the volume of the first concave heat receiving section 14A is larger than that of the second concave heat receiving section 15. Therefore, the amount of liquid-phase working fluid that can be stored is greater in the first concave heat receiving section 14A than in the second concave heat receiving section 15.

[0039] In this embodiment, a second capillary structure 5A and a third capillary structure 6A of the same type are housed in the first concave heat receiving section 14A and the second concave heat receiving section 15, but the volume of the second capillary structure 5A housed in the first concave heat receiving section 14A is larger than the volume of the third capillary structure 6A housed in the second concave heat receiving section 15. Therefore, the total amount of liquid-phase working fluid that can be held is greater for the second capillary structure 5A than for the third capillary structure 6A.

[0040] Since the bottom 16A of the first concave heat receiving portion 14A has a larger area than the bottom 16 of the first concave heat receiving portion 14 in the first embodiment, it becomes possible to have thermal contact with a heat source (not shown) that has a larger contact area than the heat source P1.

[0041] In this embodiment as well, as the temperatures of heat sources P1, P2, and P3 rise, the liquid-phase working fluid receives heat through the heat receiving plate 3A (bottom 16A, 17, flat heat receiving section 19) and becomes a gaseous working fluid, which then moves to the heat dissipation plate 2 side. At this time, even if the heat from heat source P2 is conducted to the first concave heat receiving section 14A side via the bottom 12 or the gaseous working fluid, the liquid-phase working fluid is retained within the first concave heat receiving section 14A. Therefore, the heat from heat sources P2 and P3 is received by this liquid-phase working fluid, and it is extremely difficult for heat to be transferred to heat source P1. The gaseous working fluid comes into thermal contact with the heat dissipation plate 2, causing the heat dissipation plate 2 to receive heat from the working fluid, and the heat is then dissipated from the heat dissipation plate 2 to the outside of the SHP1A. The working fluid in the gas phase, whose temperature has decreased, condenses into a liquid phase and moves towards the heat receiving plate 3A. Due to the capillary force of the first capillary structure 4, the second capillary structure 5A, and the second capillary structure 6A, it moves to the first capillary structure 4, the second capillary structure 5A, and the third capillary structure 6A, and is held inside the first capillary structure 4, the first concave heat receiving section 14A, and the second concave heat receiving section 15. In this way, heat is transported by the working fluid inside the SHP1A, the heat sources P1, P2, and P3 are cooled, and the temperature rise of the equipment can be mitigated.

[0042] In this embodiment, the first capillary structure 4, the second capillary structure 5A, and the third capillary structure 6A are of different capillary structures, while the second capillary structure 5A and the third capillary structure 6A are of the same type. However, the first capillary structure 4, the second capillary structure 5A, and the third capillary structure 6A may all be of the same type to achieve equivalent retention rates of the working fluid in the liquid phase. In that case, the first capillary structure 4, the second capillary structure 5A, and the third capillary structure 6A may be formed integrally. Alternatively, the first capillary structure 4 and the second capillary structure 5A may be of the same type to achieve equivalent retention rates of the working fluid in the liquid phase, while the third capillary structure 6A may be of a different type to achieve different retention rates of the working fluid in the liquid phase. In that case, the first capillary structure 4 and the second capillary structure 5A may be formed as a single unit. Alternatively, the first capillary structure 4 and the third capillary structure 6A may be made of the same type of capillary structure to have the same retention rate of the working fluid in the liquid phase, while the second capillary structure 5A may be made of a different type of capillary structure to have a different retention rate of the working fluid in the liquid phase. In that case, the first capillary structure 4 and the third capillary structure 6A may be formed as a single unit. Alternatively, the first capillary structure 4, the second capillary structure 5A, and the third capillary structure 6A may all be made of different types of capillary structures to have a different retention rate of the working fluid in the liquid phase.

[0043] As described above, the SHP1A of this embodiment is a sheet-shaped heat pipe 1A having an internal space S formed between a heat dissipation plate 2 and a heat receiving plate 3A, the internal space S containing a capillary structure and a working fluid, the heat receiving plate 3A having a housing portion 11 protruding in the opposite direction from the heat dissipation plate 2, the bottom portion 12 of the housing portion 11 having a plurality of heat receiving portions, at least one of the plurality of heat receiving portions being a first concave heat receiving portion 14A formed in a concave shape, and the capillary structure is arranged in the bottom portion 12 and the first concave heat receiving portion 14A. By bringing the first concave heat receiving section 14A, which has a large capacity to hold liquid-phase working fluid, into thermal contact with a low-temperature heat source P1, and the second concave heat receiving section 15, which has a small capacity to hold liquid-phase working fluid, into thermal contact with a high-temperature heat source P2, even if the temperatures of heat sources P1 and P2 rise, it is possible to make it difficult for heat from heat sources P2 and P3 to be conducted to heat source P1 by the liquid-phase working fluid within the first concave heat receiving section 14A.

[0044] Furthermore, the SHP1A of this embodiment has a second concave heat receiving section 15 in which multiple heat receiving sections are formed in a concave shape, and a third capillary structure 6A is disposed in the second concave heat receiving section 15, and the fluid retention rate of at least one of the second capillary structure 5A disposed in the first concave heat receiving section 14A and the third capillary structure 6A disposed in the second concave heat receiving section 15 may be equivalent to the fluid retention rate of the first capillary structure 4 disposed in the bottom section 12. In that case, the liquid phase fluid can be uniformly held in the first capillary structure 4 and at least one of the second capillary structure 5A and the third capillary structure 6A.

[0045] Furthermore, in this embodiment, the SHP1A may have different working fluid retention rates for the first capillary structure 4 located on the bottom surface 12, the second capillary structure 5A located on the first concave heat receiving section 14A, and the third capillary structure 6A located on the second concave heat receiving section 15. In such cases, if the temperatures of the heat sources P1, P2, and P3 to be cooled are all different, it is possible to select a capillary structure with an appropriate working fluid retention rate according to those temperatures.

[0046] Furthermore, the SHP1A of this embodiment has a second concave heat receiving section 15 in which multiple heat receiving sections are formed in a concave shape, and a third capillary structure 6A is disposed in the second concave heat receiving section 15, and the volume of the first concave heat receiving section 14A and the volume of the second concave heat receiving section 15 are different. Therefore, the amount of working fluid to be held can be selected according to the temperature of the heat sources P1 and P2 to be cooled.

[0047] Furthermore, in this embodiment of the SHP1A, the fluid retention rate of the working fluid in the first capillary structure 4 disposed on the bottom surface 12, the fluid retention rate of the second capillary structure 5A disposed on the first concave heat receiving section 14A, and the fluid retention rate of the third capillary structure 6A disposed on the second concave heat receiving section 15 may all be the same. In that case, the liquid phase working fluid held in the first capillary structure 4, the second capillary structure 5A, and the third capillary structure 6A can be made uniform.

[0048] Furthermore, in this embodiment, the SHP1A has a structure in which multiple heat receiving sections are in thermal contact with different heat sources P1, P2, and P3. When the temperatures of heat sources P1 and P2 are different, the second concave heat receiving section 15, which has a small capacity to hold working fluid, is in thermal contact with the heat source P2, which has a higher temperature, and the first concave heat receiving section 14A, which has a large capacity to hold working fluid, is in thermal contact with the heat source P1, which has a lower temperature. Therefore, even if the temperatures of heat sources P1, P2, and P3 rise, the working fluid in the liquid phase within the first concave heat receiving section 14A makes it difficult for heat from heat source P2 to be conducted to heat sources P1 and P3.

[0049] Furthermore, in this embodiment, the SHP1A has a first capillary structure 4 disposed on the bottom surface 12 which is a mesh body made of woven metal wires, and a second capillary structure 5A and a third capillary structure 6A disposed on the first concave heat receiving section 14A and the second concave heat receiving section 15 which are made of sintered fiber felt made of sintered metal fibers. Since sintered fiber felt has a higher retention rate of liquid-phase working fluid than mesh body, it is possible to easily move the liquid-phase working fluid from the first capillary structure 4 to the second capillary structure 5A and the third capillary structure 6A. As a result, it is possible to easily store liquid-phase working fluid in the first concave heat receiving section 14A and the second concave heat receiving section 15.

[0050] Furthermore, in this embodiment, the SHP1A has different areas at the bottom 16A of the first concave heat receiving section 14A and the bottom 17 of the second concave heat receiving section 15. By bringing the first concave heat receiving section 14A, which has a large capacity to store liquid-phase working fluid, into thermal contact with a low-temperature heat source P1, and the second concave heat receiving section 15, which has a small capacity to store liquid-phase working fluid, into thermal contact with a high-temperature heat source P2, even if the temperatures of heat sources P1, P2, and P3 rise, the liquid-phase working fluid in the first concave heat receiving section 14A makes it difficult for heat from heat sources P2 and P3 to be conducted to heat source P1.

[0051] Furthermore, in this embodiment, SHP1A has a flat heat receiving section 19 in which at least one of the multiple heat receiving sections is formed flat. Therefore, the heat source P3 can be cooled by bringing it into thermal contact with the flat heat receiving section 19, which is not formed in a concave shape.

[0052] Figures 7 and 8 show the SHP1B in the third embodiment of the present invention. Here, the differences from the first and second embodiments will be explained, and the explanation of the commonalities with the first and second embodiments will be omitted. This embodiment uses a heat receiving plate 3B in which the depth of the first concave heat receiving section 14B is greater than the depth of the second concave heat receiving section 15. The area of ​​the bottom 16B of the first concave heat receiving section 14B and the bottom 17 of the second concave heat receiving section 15 in a plan view is the same, but because the depth of the first concave heat receiving section 14B is greater than that of the second concave heat receiving section 15, the volume of the first concave heat receiving section 14B is greater than that of the second concave heat receiving section 15. Therefore, the amount of liquid-phase working fluid that can be stored is greater in the first concave heat receiving section 14B than in the second concave heat receiving section 15.

[0053] In this embodiment, a second capillary structure 5B and a third capillary structure 6B of the same type are housed in the first concave heat receiving section 14B and the second concave heat receiving section 15, but the volume of the second capillary structure 5B housed in the first concave heat receiving section 14B is larger than the volume of the third capillary structure 6B housed in the second concave heat receiving section 15. Therefore, the amount of liquid-phase working fluid that can be held is greater in the second capillary structure 5B than in the third capillary structure 6B.

[0054] In this embodiment as well, as the temperatures of heat sources P1, P2, and P3 rise, the liquid-phase working fluid receives heat through the heat receiving plate 3B (bottom 16B, 17, flat heat receiving section 19) and becomes a gaseous working fluid, which then moves to the heat dissipation plate 2 side. At this time, even if the heat from heat source P2 is conducted to the first concave heat receiving section 14B side via the bottom 12 or the gaseous working fluid, the liquid-phase working fluid is retained within the first concave heat receiving section 14B, so the heat from heat source P2 is received by this liquid-phase working fluid and is extremely difficult to transfer to heat source P1. The gaseous working fluid comes into thermal contact with the heat dissipation plate 2, causing the heat dissipation plate 2 to receive heat from the working fluid, and the heat is then dissipated from the heat dissipation plate 2 to the outside of SHP1B. The working fluid in the gas phase, whose temperature has decreased, condenses into a liquid phase and moves towards the heat receiving plate 3B. Due to the capillary force of the first capillary structure 4, the second capillary structure 5B, and the third capillary structure 6B, it moves to the first capillary structure 4, the second capillary structure 5B, and the third capillary structure 6B, and is held inside the first capillary structure 4, the first concave heat receiving section 14B, and the second concave heat receiving section 15. In this way, heat is transported by the working fluid inside the SHP1B, the heat sources P1, P2, and P3 are cooled, and the temperature rise of the equipment can be mitigated.

[0055] In this embodiment, the first capillary structure 4, the second capillary structure 5B, and the third capillary structure 6B are of different capillary structures, while the second capillary structure 5B and the third capillary structure 6B are of the same type. However, the first capillary structure 4, the second capillary structure 5B, and the third capillary structure 6B may all be of the same type to achieve equivalent retention rates of the working fluid in the liquid phase. In that case, the first capillary structure 4, the second capillary structure 5B, and the third capillary structure 6B may be formed integrally. Alternatively, the first capillary structure 4 and the second capillary structure 5B may be of the same type to achieve equivalent retention rates of the working fluid in the liquid phase, while the third capillary structure 6B may be of a different type to achieve different retention rates of the working fluid in the liquid phase. In that case, the first capillary structure 4 and the second capillary structure 5B may be formed as a single unit. Alternatively, the first capillary structure 4 and the third capillary structure 6B may be made of the same type of capillary structure to have the same retention rate of the working fluid in the liquid phase, while the second capillary structure 5B may be made of a different type of capillary structure to have different retention rates of the working fluid in the liquid phase. In that case, the first capillary structure 4 and the third capillary structure 6B may be formed as a single unit. Alternatively, the first capillary structure 4, the second capillary structure 5B, and the third capillary structure 6B may all be made of different types of capillary structures to have different retention rates of the working fluid in the liquid phase.

[0056] As described above, the SHP1B of this embodiment is a sheet-shaped heat pipe 1B having an internal space S formed between a heat dissipation plate 2 and a heat receiving plate 3B, the internal space S containing a capillary structure and a working fluid, the heat receiving plate 3B having a housing portion 11 that protrudes in the opposite direction from the heat dissipation plate 2, the bottom surface portion 12 of the housing portion 11 having a heat receiving portion, at least one of the multiple heat receiving portions being a first concave heat receiving portion 14B formed in a concave shape, and the capillary structure is arranged in the bottom surface portion 12 and the first concave heat receiving portion 14B. By bringing the first concave heat receiving section 14B, which has a large capacity to hold liquid-phase working fluid, into thermal contact with a low-temperature heat source P1, and the second concave heat receiving section 15, which has a small capacity to hold liquid-phase working fluid, into thermal contact with a high-temperature heat source P2, even if the temperatures of heat sources P1 and P2 rise, the liquid-phase working fluid in the first concave heat receiving section 14B makes it difficult for heat from heat sources P2 and P3 to be conducted to heat source P1.

[0057] Furthermore, the SHP1B of this embodiment has a second concave heat receiving section 15 in which a plurality of heat receiving sections are formed in a concave shape, and a third capillary structure 6B is disposed in the second concave heat receiving section 15, and the fluid retention rate of at least one of the second capillary structure 5B disposed in the first concave heat receiving section 14B and the third capillary structure 6B disposed in the second concave heat receiving section 15 may be equivalent to the fluid retention rate of the first capillary structure 4 disposed in the bottom section 12. In that case, the liquid phase fluid can be uniformly held in the first capillary structure 4 and at least one of the second capillary structure 5B and the third capillary structure 6B.

[0058] Furthermore, in this embodiment, the SHP1B may have different working fluid retention rates for the first capillary structure 4 located on the bottom surface 12, the second capillary structure 5B located on the first concave heat receiving section 14B, and the third capillary structure 6B located on the second concave heat receiving section 15. In such cases, if the temperatures of the heat sources P1, P2, and P3 to be cooled are all different, a capillary structure with an appropriate working fluid retention rate can be selected according to the temperature.

[0059] Furthermore, the SHP1B of this embodiment has a second concave heat receiving section 15 in which multiple heat receiving sections are formed in a concave shape, and a third capillary structure 6B is disposed in the second concave heat receiving section 15, and the volume of the first concave heat receiving section 14B and the volume of the second concave heat receiving section 15 are different. Therefore, the amount of working fluid to be held can be selected according to the temperature of the heat sources P1 and P2 to be cooled.

[0060] Furthermore, in this embodiment, the SHP1B may have the same fluid retention rate for the working fluid in the first capillary structure 4 located on the bottom surface 12, the second capillary structure 5B located on the first concave heat receiving section 14B, and the third capillary structure 6B located on the second concave heat receiving section 15. In this case, the liquid phase working fluid held in the first capillary structure 4, the second capillary structure 5B, and the third capillary structure 6B can be made uniform.

[0061] Furthermore, the SHP1B of this embodiment has a structure in which multiple heat receiving sections are in thermal contact with different heat sources P1, P2, and P3. When the temperatures of heat sources P1 and P2 are different, the second concave heat receiving section 15, which has a small capacity to hold working fluid, is in thermal contact with the heat source P2, which has a higher temperature, and the first concave heat receiving section 14B, which has a large capacity to hold working fluid, is in thermal contact with the heat source P1, which has a lower temperature. Therefore, even if the temperatures of heat sources P1, P2, and P3 rise, the working fluid in the liquid phase within the first concave heat receiving section 14B makes it difficult for heat from heat sources P2 and P3 to be conducted to heat source P1.

[0062] Furthermore, in this embodiment, the SHP1B has a first capillary structure 4 disposed on the bottom surface 12 which is a mesh body made of woven metal wires, and a second capillary structure 5B and a third capillary structure 6B disposed on the first concave heat receiving section 14B and the second concave heat receiving section 15 which are made of sintered fiber felt made of sintered metal fibers. Since sintered fiber felt has a higher retention rate of liquid-phase working fluid than mesh body, it is possible to easily move the liquid-phase working fluid from the first capillary structure 4 to the second capillary structure 5B and the third capillary structure 6B. As a result, it is possible to easily store liquid-phase working fluid in the first concave heat receiving section 14B and the second concave heat receiving section 15.

[0063] Furthermore, in this embodiment, the SHP1B has different depths for the first concave heat receiving section 14B and the second concave heat receiving section 15. By bringing the first concave heat receiving section 14B, which has a large capacity to store liquid-phase working fluid, into thermal contact with a low-temperature heat source P1, and the second concave heat receiving section 15, which has a small capacity to store liquid-phase working fluid, into thermal contact with a high-temperature heat source P2, even if the temperatures of heat sources P1, P2, and P3 rise, the liquid-phase working fluid in the first concave heat receiving section 14B makes it difficult for heat from heat source P2 to be conducted to heat sources P1 and P3.

[0064] Furthermore, in this embodiment, the SHP1B has a flat heat receiving section 19 in which at least one of the multiple heat receiving sections is formed flat. Therefore, the heat source P3 can be cooled by bringing it into thermal contact with the flat heat receiving section 19, which is not formed in a concave shape.

[0065] Figure 9 shows SHP1C in the fourth embodiment of the present invention. Here, the differences from the first to third embodiments will be explained, and the explanation of the commonalities with the first to third embodiments will be omitted. This embodiment has a capillary structure consisting of a first capillary structure 4C, a second capillary structure 5C, and a third capillary structure 6C.

[0066] The first capillary structure 4C is divided into a one-sided capillary structure 4C1 and a other-sided capillary structure 4C2. The one-sided capillary structure 4C1 is integrally formed with the second capillary structure 5C, and the other-sided capillary structure 4C2 is integrally formed with the third capillary structure 6C. The one-sided capillary structure 4C1 and the other-sided capillary structure 4C2 may be joined by methods such as diffusion bonding, laser welding, or brazing.

[0067] The one-sided capillary structure 4C1 and the second capillary structure 5C are formed from the same type of fibrous sintered felt, and the other-sided capillary structure 4C2 and the third capillary structure 6C are formed from the same type of fibrous sintered felt. In this embodiment, the retention rate of the liquid phase working fluid in the one-sided capillary structure 4C1 and the second capillary structure 5C is higher than that of the other-sided capillary structure 4C2 and the third capillary structure 6C. However, the retention rate of the liquid phase working fluid in the one-sided capillary structure 4C1 and the second capillary structure 5C may be equal to or less than that of the other-sided capillary structure 4C2 and the third capillary structure 6C.

[0068] In this embodiment as well, as the temperatures of heat sources P1, P2, and P3 rise, the liquid-phase working fluid receives heat through the heat receiving plate 3 (bottom portions 16, 17, flat heat receiving portion 19) and becomes a gaseous working fluid. When this gaseous working fluid is converted to a gaseous working fluid, it moves to the heat dissipation plate 2 side. At this time, even if the heat from heat source P2 is conducted to the first concave heat receiving portion 14 side via the bottom portion 12 or the gaseous working fluid, the liquid-phase working fluid is retained within the first concave heat receiving portion 14. Therefore, the heat from heat source P2 is received by this liquid-phase working fluid, and it is extremely difficult for heat to be transferred to heat source P1. The gaseous working fluid comes into thermal contact with the heat dissipation plate 2, causing the heat dissipation plate 2 to receive heat from the working fluid, and the heat is then dissipated from the heat dissipation plate 2 to the outside of the SHP1C. The working fluid in the gas phase, whose temperature has decreased, condenses into a liquid phase and moves towards the heat receiving plate 3. Due to the capillary force of the first capillary structure 4C, the second capillary structure 5C, and the third capillary structure 6C, it moves to the first capillary structure 4C, the second capillary structure 5C, and the third capillary structure 6C, and is held inside the first capillary structure 4C, the first concave heat receiving section 14, and the second concave heat receiving section 15. In this way, heat is transported by the working fluid inside the SHP1C, the heat sources P1, P2, and P3 are cooled, and the temperature rise of the equipment can be mitigated.

[0069] As described above, the SHP1C of this embodiment is a sheet-shaped heat pipe 1C having an internal space S formed between a heat dissipation plate 2 and a heat receiving plate 3, the internal space S containing a capillary structure and a working fluid, the heat receiving plate 3 having a housing portion 11 that protrudes in the opposite direction from the heat dissipation plate 2, the bottom portion 12 of the housing portion 11 having a plurality of heat receiving portions, at least one of the plurality of heat receiving portions being a first concave heat receiving portion 14 formed in a concave shape, and the capillary structure is arranged in the bottom portion 12 and the first concave heat receiving portion 14. By bringing the first concave heat receiving section 14, which has a large capacity to hold liquid-phase working fluid, into thermal contact with a low-temperature heat source P1, and the second concave heat receiving section 15, which has a small capacity to hold liquid-phase working fluid, into thermal contact with a high-temperature heat source P2, even if the temperatures of heat sources P1, P2, and P3 rise, the liquid-phase working fluid in the first concave heat receiving section 14 makes it difficult for heat from heat sources P2 and P3 to be conducted to heat source P1.

[0070] Furthermore, the SHP1C of this embodiment has a second concave heat receiving section 15 in which multiple heat receiving sections are formed in a concave shape, and a second capillary structure 6C is disposed in the second concave heat receiving section 15, and the fluid retention rate of at least one of the second capillary structure 5C disposed in the first concave heat receiving section 14 and the third capillary structure 6C disposed in the second concave heat receiving section 15 is equivalent to the fluid retention rate of the first capillary structure 4C disposed in the bottom section 12. Therefore, the liquid phase working fluid can be uniformly held in the one-side capillary structure 4C1 and the second capillary structure 5C. Also, the liquid phase working fluid can be uniformly held in the other-side capillary structure 4C2 and the third capillary structure 6C.

[0071] Furthermore, the SHP1C of this embodiment has a structure in which multiple heat receiving sections are in thermal contact with different heat sources P1, P2, and P3, and when the temperatures of heat sources P1, P2, and P3 are different, the second concave heat receiving section 15, which has a small capacity to hold working fluid, is in thermal contact with the heat source P2, which has a higher temperature, and the first concave heat receiving section 14, which has a large capacity to hold working fluid, is in thermal contact with the heat source P1, which has a lower temperature. Therefore, even if the temperatures of heat sources P1, P2, and P3 rise, the working fluid in the liquid phase within the first concave heat receiving section 14 makes it difficult for heat from heat sources P2 and P3 to be conducted to heat source P1.

[0072] Furthermore, in this embodiment, the SHP1C has a flat heat receiving section 19 in which at least one of the multiple heat receiving sections is formed flat. Therefore, the heat source P3 can be cooled by bringing it into thermal contact with the flat heat receiving section 19, which is not formed in a concave shape.

[0073] Figure 10 shows the SHP1D in the fifth embodiment of the present invention. Here, the differences from the first to fourth embodiments will be explained, and the explanation of the commonalities with the first to fourth embodiments will be omitted. This embodiment uses a heat receiving plate 3D that does not have the second concave heat receiving portion 15 of the first embodiment. Since the second concave heat receiving portion 15 is not formed, the third capillary structure 6 is also not used. The other parts are the same as the SHP1 of the first embodiment.

[0074] In this embodiment, as the temperatures of heat sources P1 and P3 rise, the liquid-phase working fluid receives heat through the heat receiving plate 3D (bottom 16, flat heat receiving section 19) and becomes a gaseous working fluid. This gaseous working fluid then moves to the heat dissipation plate 2 side. The gaseous working fluid comes into thermal contact with the heat dissipation plate 2, causing the heat dissipation plate 2 to receive heat from the working fluid, and the heat is then dissipated from the heat dissipation plate 2 to the outside of the SHP1D. The gaseous working fluid, whose temperature has decreased, condenses into a liquid phase and moves to the heat receiving plate 3D side. Due to the capillary force of the first capillary structure 4 and the second capillary structure 5, it moves to the first capillary structure 4 and the second capillary structure 5, and is held inside the first capillary structure 4 and the first concave heat receiving section 14. In this way, heat is transported by the working fluid inside the SHP1D, the heat sources P1 and P3 are cooled, and the temperature rise of the equipment can be mitigated.

[0075] As described above, the SHP1D of this embodiment is a sheet-shaped heat pipe 1D in which an internal space S is formed between a heat dissipation plate 2 and a heat receiving plate 3D. The internal space S contains a capillary structure and a working fluid. The heat receiving plate 3D has a housing portion 11 that protrudes in the opposite direction to the heat dissipation plate 2, and the bottom portion 12 of the housing portion 11 has a plurality of heat receiving portions, at least one of which is a first concave heat receiving portion 14 formed in a concave shape. The capillary structure is arranged in the bottom portion 12 and the first concave heat receiving portion 14. Even if the temperature of heat sources P1 and P3 rises, the working fluid in the liquid phase within the first concave heat receiving portion 14 makes it difficult to conduct heat from heat source P3 to heat source P1.

[0076] Furthermore, in this embodiment, the SHP1D has a first capillary structure 4 arranged on the bottom surface 12 which is a mesh body made of woven metal wires, and a second capillary structure 5 arranged on the first concave heat receiving section 14 which is a sintered fiber felt made of sintered metal fibers. Since the sintered fiber felt has a higher retention rate of the liquid phase working fluid than the mesh body, it is possible to easily move the liquid phase working fluid from the first capillary structure 4 to the second capillary structure 5. As a result, it is possible to easily store the liquid phase working fluid in the first concave heat receiving section 14.

[0077] Furthermore, in this embodiment, the SHP1D has a flat heat receiving section 19 in which at least one of the multiple heat receiving sections is formed flat. Therefore, the heat source P3 can be cooled by bringing it into thermal contact with the flat heat receiving section 19, which is not formed in a concave shape.

[0078] Figure 11 shows the SHP1E in the sixth embodiment of the present invention. Here, the differences from the first to fifth embodiments will be explained, and the explanation of the commonalities with the first to fifth embodiments will be omitted. The SHP1E is composed of a heat dissipation plate 2E as a first plate, a heat receiving plate 3E as a second plate, a first capillary structure 4 and a second capillary structure 5 as capillary structures housed in the heat receiving plate 3E, and a working fluid (not shown).

[0079] The heat dissipation plate 2E is formed with multiple support columns 8 and multiple support columns 8E that are longer than the support columns 8, projecting toward the heat receiving plate 3E.

[0080] The heat receiving plate 3E integrally includes a first concave heat receiving portion 14 recessed in the direction opposite to that of the heat dissipation plate 2E, a second concave heat receiving portion 15E recessed in the direction of the heat dissipation plate 2E, and a flat heat receiving portion 19 that is formed flat.

[0081] The housing portion 11E of the heat receiving plate 3E is formed deeper than the housing portion 11 of the first to fifth embodiments because the second concave heat receiving portion 15E is formed therein.

[0082] The bottom 16 of the first concave heat receiving section 14 is in thermal contact with the heat source P1 to be cooled, the top plate 20 of the second concave heat receiving section 15E is in thermal contact with the heat source P2 to be cooled, and the flat heat receiving section 19 is in thermal contact with the heat source P3 to be cooled.

[0083] The first capillary structure 4 is arranged along the bottom surface 12 and is bent along the second concave heat receiving section 15E. The support column 8 abuts against the portion of the first capillary structure 4 that is arranged along the second concave heat receiving section 15E, and the support column 8E abuts against the remaining portion.

[0084] In this embodiment, as the temperatures of heat sources P1, P2, and P3 rise, the liquid-phase working fluid receives heat through the heat receiving plate 3 (bottom portion 16, top portion 20, flat heat receiving portion 19), and when it becomes a gaseous working fluid, the gaseous working fluid moves to the heat dissipation plate 2E side. At this time, even if the heat from heat source P2 is conducted to the first concave heat receiving portion 14 side via the bottom portion 12 or the gaseous working fluid, the liquid-phase working fluid is retained within the first concave heat receiving portion 14, so the heat from heat source P2 is received by this liquid-phase working fluid, and it is extremely difficult for heat to be transferred to heat source P1. The gaseous working fluid comes into thermal contact with the heat dissipation plate 2E, causing the heat dissipation plate 2E to receive heat from the working fluid, and the heat is then dissipated from the heat dissipation plate 2E to the outside of SHP1E. The working fluid in the gas phase, whose temperature has decreased, condenses into a liquid phase and moves towards the heat receiving plate 3E. Due to the capillary force of the first capillary structure 4 and the second capillary structure 5, it moves to the first capillary structure 4 and the second capillary structure 5, and is held inside the first capillary structure 4 and the first concave heat receiving section 14. In this way, heat is transported by the working fluid inside the SHP1E, the heat sources P1, P2, and P3 are cooled, and the temperature rise of the equipment can be mitigated.

[0085] As described above, the SHP1E of this embodiment is a sheet-shaped heat pipe 1E having an internal space S formed between a heat dissipation plate 2E and a heat receiving plate 3E, the internal space S containing a capillary structure and a working fluid, the heat receiving plate 3E having a housing portion 11E protruding in the opposite direction from the heat dissipation plate 2E, the bottom surface portion 12 of the housing portion 11E having a plurality of heat receiving portions, at least one of the plurality of heat receiving portions being a first concave heat receiving portion 14 formed in a concave shape, and the capillary structure is arranged in the bottom surface portion 12 and the first concave heat receiving portion 14. By bringing the first concave heat receiving section 14, which stores a liquid-phase working fluid, into thermal contact with a low-temperature heat source P1, and the second concave heat receiving section 15 into thermal contact with a high-temperature heat source P2, even if the temperatures of heat sources P1, P2, and P3 rise, the liquid-phase working fluid in the first concave heat receiving section 14 makes it difficult for heat from heat sources P2 and P3 to be conducted to heat source P1.

[0086] Furthermore, in this embodiment, the SHP1E has a first capillary structure 4 disposed on the bottom surface 12 which is a mesh body made of woven metal wires, and a second capillary structure 5 disposed on the first concave heat receiving section 14 which is a sintered fiber felt made of sintered metal fibers. Since the sintered fiber felt has a higher retention rate of the liquid phase working fluid than the mesh body, it is possible to easily move the liquid phase working fluid from the first capillary structure 4 to the second capillary structure 5. As a result, it is possible to easily store the liquid phase working fluid in the first concave heat receiving section 14.

[0087] Furthermore, in this embodiment, the SHP1E has a flat heat receiving section 19 in which at least one of the multiple heat receiving sections is formed flat. Therefore, the heat source P3 can be cooled by bringing it into thermal contact with the flat heat receiving section 19, which is not formed in a concave shape.

[0088] It should be noted that the present invention is not limited to the embodiments described above, and various modifications are possible without departing from the spirit of the invention. For example, the external shapes of SHP1, 1A, 1B, 1C, 1D, and 1E can be other external shapes corresponding to the position of the heat source of the equipment on which SHP1, 1A, 1B, 1C, 1D, and 1E are mounted, and the arrangement of surrounding components. Furthermore, the shape, depth, and type of sintered fiber felt contained in the first concave heat receiving sections 14, 14A, and 14B, the second concave heat receiving sections 15 and 15E, and SHP1, 1A, 1B, 1C, 1C, 1D, and 1E can be appropriately determined in accordance with the shape, position, temperature, etc., of the heat source. In addition, three or more heat receiving sections may be formed. [Explanation of symbols]

[0089] 1 SHP (Sheet Heat Pipe) 1A SHP (Sheet Heat Pipe) 1B SHP (Sheet Heat Pipe) 1C SHP (Sheet Heat Pipe) 1D SHP (Sheet Heat Pipe) 1E SHP (Sheet Heat Pipe) 2. Heat dissipation plate (first plate) 2E Heat dissipation plate (first plate) 3. Heat receiving plate (second plate) 3A Heat receiving plate (second plate) 3B Heat receiving plate (second plate) 3D heat receiving plate (second plate) 3E Heat receiving plate (second plate) 4. First capillary structure (capillary structure) 4C First capillary structure (capillary structure) 5. Second capillary structure (capillary structure) 5A Second capillary structure (capillary structure) 5B Second capillary structure (capillary structure) 5C Second capillary structure (capillary structure) 6. The third capillary structure (capillary structure) 6A Third capillary structure (capillary structure) 6B The third capillary structure (capillary structure) 6C Third capillary structure (capillary structure) 11. Storage Unit 11E Storage Unit 12 Bottom part 14 First concave heat receiving part 14A 1st concave heat receiving part 14B 1st concave heat receiving part 15 Second concave heat receiving part 16A bottom 17 Bottom 19 Flat heat receiving part P1 Heat source (object to be cooled) P2 Heat source (object to be cooled) P3 Heat source (object to be cooled) S interior space

Claims

1. A sheet-shaped heat pipe having an internal space formed between a first plate and a second plate, The aforementioned internal space contains a capillary structure and a working fluid. The second plate has a housing portion that protrudes in the opposite direction to the first plate, The bottom surface of the aforementioned housing section has multiple heat receiving sections. At least one of the plurality of heat receiving parts is a first concave heat receiving part formed in a concave shape, The capillary structure is arranged in the bottom portion and the first concave heat receiving portion. A sheet-shaped heat pipe characterized by having the following features.

2. The plurality of heat receiving parts have a second concave heat receiving part formed in a concave shape, The capillary structure is arranged in the second concave heat receiving section. The sheet-like heat pipe according to claim 1, characterized in that the fluid retention rate of at least one of the capillary structure disposed in the first concave heat receiving portion and the capillary structure disposed in the second concave heat receiving portion is equivalent to the fluid retention rate of the capillary structure disposed in the bottom portion.

3. The sheet-like heat pipe according to claim 2, characterized in that the fluid retention rate of the capillary structure disposed on the bottom surface, the fluid retention rate of the capillary structure disposed on the first concave heat receiving portion, and the fluid retention rate of the capillary structure disposed on the second concave heat receiving portion are all different.

4. The plurality of heat receiving parts have a second concave heat receiving part formed in a concave shape, The capillary structure is arranged in the second concave heat receiving section. The sheet-like heat pipe according to claim 1, characterized in that the volume of the first concave heat receiving portion and the volume of the second concave heat receiving portion are different.

5. The sheet-like heat pipe according to claim 4, characterized in that the fluid retention rate of the capillary structure disposed on the bottom surface, the fluid retention rate of the capillary structure disposed on the first concave heat receiving portion, and the fluid retention rate of the capillary structure disposed on the second concave heat receiving portion are all the same.

6. Each of the aforementioned heat receiving units is in thermal contact with a different object to be cooled. The sheet-like heat pipe according to claim 1, characterized in that, when the temperatures of the objects to be cooled are different, the heat receiving portion, which has a smaller capacity to hold the working fluid, is brought into thermal contact with the object to be cooled at a higher temperature, and the heat receiving portion, which has a larger capacity to hold the working fluid, is brought into thermal contact with the object to be cooled at a lower temperature.

7. The capillary structure disposed on the bottom surface is a mesh body made of woven metal wires. The sheet-like heat pipe according to claim 1, characterized in that the capillary structure disposed in the heat receiving section is a sintered fiber felt obtained by sintering metal fibers.

8. The sheet-like heat pipe according to claim 4 or 5, characterized in that the area of ​​the bottom of the first concave heat receiving portion and the area of ​​the bottom of the second concave heat receiving portion are different.

9. The sheet-like heat pipe according to claim 4 or 5, characterized in that the depth of the first concave heat receiving portion and the depth of the second concave heat receiving portion are different.

10. The sheet-like heat pipe according to claim 1, characterized in that at least one of the plurality of heat receiving sections is a flat heat receiving section formed in a flat manner.

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