JP5778302B2 - Heat transport equipment - Google Patents

Description

  The present invention relates to a heat transport device in which a heat receiving portion is provided on one end side of a heat pipe and a heat radiating portion is provided on the other end side.

  In general, a heat transport device is known that includes a heat pipe in which a working fluid is sealed in a container, a heat receiving portion is provided on one end side of the heat pipe, and a heat radiating portion is provided on the other end side. In this type of heat transport device, the working fluid is transported by repeatedly evaporating and condensing in the container. That is, the hydraulic fluid evaporates on the heat receiving portion side in the container, and the evaporated hydraulic fluid moves inside the container to the heat radiation side due to a pressure difference. The evaporated working fluid is condensed on the heat radiation side to become a liquid, and this working fluid is returned to the heat receiving portion side by the capillary force of the wick provided on the inner wall of the container. As described above, in the heat transport apparatus including the heat pipe, the apparent thermal conductivity of the container is several times to several tens of times that of a metal such as copper or aluminum. It is mounted on an electronic device such as a computer and used to cool a cooling target component such as a CPU.

By the way, this type of heat pipe has a top heat in which the heat receiving part is arranged at the upper part in the gravity direction and a bottom heat in which the heat receiving part is arranged in the lower part in the gravitational direction, depending on the position of the heat receiving part in which the cooling target component is provided. It is divided into and. When the heat pipe is arranged in the top heat, the flow of the hydraulic fluid to the heat receiving portion located at a high position is hindered by gravity, so that the amount of heat transport is greatly reduced.
As a technique for solving this problem, a configuration has been proposed in which a vibrator is attached to a heat pipe to assist the return of the working fluid to a heat receiving portion provided above the direction of gravity (see, for example, Patent Document 1). .

Japanese Patent Laid-Open No. 2-115692

However, the conventional technology as described in Patent Document 1 requires a complicated mechanism by providing a vibrator, and further has a problem that the volume of the container (heat pipe) is significantly increased. Thereby, since the whole heat transport apparatus becomes large, mounting in small electronic devices, such as a personal computer, becomes difficult.
The present invention has been made to solve the above problems, and an object of the present invention is to provide a heat transport device capable of improving heat transport characteristics with a simple configuration.

In order to achieve the above object, the present invention provides a heat transport apparatus including a heat pipe in which a working fluid is sealed, a heat receiving portion provided on one end side of the heat pipe, and a heat radiating portion provided on the other end side. On the inner wall of the heat pipe, a first wick having a relatively large capillary pressure is disposed in the heat receiving portion of the heat pipe, and a second fluid flow having a relatively low flow resistance is disposed in the heat radiating portion of the heat pipe. wick is arranged, said with the first wick and the second wick boundary portion is disposed below the gravity direction, Bei give a bent bent portion between said heat receiving portion and the heat radiating portion, the The heat receiving part is arranged in the upper part in the gravity direction from the bent part .

In this configuration , the second wick may include a plurality of grooves extending in the longitudinal direction on the inner wall of the heat pipe.

  Moreover, it is good also considering the depth of the said groove part as 0.10-0.20 mm. The depth of the groove may be 30 to 70% with respect to the thickness of the heat pipe.

  The first wick may include a porous sintered metal produced by sintering a spherical body or an irregular powder. The second wick may include a metal braided wire or a fine metal net. Further, the second wick includes a porous sintered metal produced by sintering a spherical body or atypical powder at the center in the width direction of the heat pipe, and the heat pipe sandwiching the porous sintered metal Steam flow paths may be formed on the left and right inside. The second wick includes a semi-elliptical porous sintered metal produced by sintering one or more spherical bodies or irregular powders in the center in the width direction of the heat pipe, and the semi-elliptic porous A flat portion of the sintered metal may be installed on the inner wall of the heat pipe, and a steam channel may be formed on the left and right sides of the heat pipe sandwiching the semi-elliptical porous sintered metal.

  The heat pipe may be pressed and flattened so that the other end side is relatively thinner than the one end side. Further, the hydraulic fluid may be stored at a boundary between the plurality of types of wicks.

  According to the present invention, the heat pipe includes a plurality of types of wicks that transfer the hydraulic fluid to an inner wall, and a boundary portion of the plurality of types of wicks is disposed at a lower portion in the gravity direction of the heat transport device. The boundary is immersed in the hydraulic fluid that has flowed down due to gravity. For this reason, heat transport efficiency can be enhanced with a simple configuration by promoting the reflux of the working fluid to one end of the heat pipe provided with the heat receiving portion. Moreover, since a heat pipe is provided with the bending part bent between the said one end side and the other end side, a hydraulic fluid can be easily stored in a bending part.

It is a perspective view of the heat transport apparatus of this embodiment. It is the figure which showed typically the internal structure of the heat transport apparatus. It is sectional drawing of the one end side of a heat pipe. It is sectional drawing of the other end side of a heat pipe. It is a schematic diagram of the internal structure of the heat transport apparatus according to Example A. It is a schematic diagram of the internal structure of the heat transport apparatus according to Example B. It is a schematic diagram of the internal structure of the heat transport apparatus according to Example C. It is a schematic diagram of the internal structure of the heat transport apparatus according to Example D. It is a schematic diagram of the internal structure of the heat transport apparatus concerning the modification of this embodiment. It is a schematic diagram of the internal structure of the heat transport apparatus concerning another embodiment. It is sectional drawing of the other end side of the heat pipe concerning Example 8. It is a schematic diagram of the internal structure of the heat transport apparatus concerning another embodiment. It is sectional drawing of the other end side of a heat pipe. It is sectional drawing of the other end side of the heat pipe concerning Example 9. FIG.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a perspective view showing a heat transport device 10 of the present embodiment.
The heat transport device 10 according to the present embodiment cools various heating elements 14 such as a CPU and a semiconductor memory mounted in a personal computer, an information home appliance, and the like.
As shown in FIG. 1, the heat transport device 10 includes a heat pipe 11, a heat receiving plate (heat receiving portion) 12 provided on the one end 11 </ b> A side of the heat pipe 11, and a heat radiation fin ( A heat dissipating part) 13. A heat generating element 14 as a part to be cooled is attached to the heat receiving plate 12.

The heat pipe 11 includes a container 15 having a hollow interior made of a metal material having excellent thermal conductivity, such as aluminum, aluminum alloy, copper, etc., and a working fluid 24 (FIG. 2) is provided in the container 15. ) Is enclosed.
As shown in FIG. 1, the heat pipe 11 includes a bent portion 11C that is bent at a substantially right angle between one end 11A and the other end 11B, and the one end 11A of the heat pipe 11 extends vertically upward from the bent portion 11C. ing. That is, the heat pipe 11 of the present embodiment is in a so-called top heat mode in which the heat receiving plate 12 is disposed in the upper part in the gravity direction, and the bending portion 11C is disposed in the lower part in the gravity direction.

The heat pipe 11 has a flat shape (substantially elliptical cross section) at one end 11A and the other end 11B, and heat exchange is possible by contacting the heat receiving plate 12 and the radiation fin 13 in a wide range. The bent portion 11C is formed in a cylindrical shape, and a large heat transport space is provided inside. In the present embodiment, the cylindrical container 15 is bent halfway to form the bent portion 11C, and the one end 11A and the other end 11B are pressed and flattened.
A heat receiving plate 12 is attached to one end 11A of the heat pipe 11 by means of, for example, welding, brazing, or soldering, and the other end 11B of the heat pipe 11 is a hole formed in the radiating fin 13. It is fixed through.
The heat receiving plate 12 is formed of a metal plate such as aluminum metal, and the heat radiating fins 13 are formed of a plurality of fin plates formed in a substantially U-shaped cross-section by bending both side edges of a metal plate such as aluminum substantially in parallel. Prepare. These fin plates are arranged side by side in the extending direction of the heat pipe 11, and the fin plates are integrally fixed by soldering.

2 is a diagram schematically showing the internal structure of the heat transport device 10, FIG. 3 is a cross-sectional view of the heat pipe 11 on the one end 11A side, and FIG. 4 is a cross-sectional view on the other end 11B side.
As shown in FIG. 2, the first wick 21 for transferring the sealed working fluid 24 to the inner wall surface 15 </ b> A (inner wall) of the container 15 by the capillary pressure is sealed inside the container 15. And a second wick 22 are provided.
The first wick 21 and the second wick 22 are different types of wicks, and the first wick 21 is provided along the longitudinal direction of the heat pipe 11 (container 15) from the one end 11A side of the heat pipe 11. The second wick 22 is provided from the other end 11B side of the heat pipe 11 along the longitudinal direction of the heat pipe 11 (container 15). And the boundary part 23 of these 1st wicks 21 and the 2nd wicks 22 is provided so that it may be located in the lowest part in the bending part 11C of the heat pipe 11. FIG.
For this reason, the hydraulic fluid 24 condensed in the heat pipe 11 is accumulated in the boundary portion 23, and the hydraulic fluid 24 is always immersed in the first wick 21 connected to the boundary portion 23.

The first wick 21 is a wick having a relatively large capillary pressure. In this embodiment, as shown in FIG. 3, a spherical body or atypical powder metal having a particle size of about 45 to 200 μm is formed on the inner wall surface 15A. A porous sintered metal 31 produced by sintering is provided. The working fluid 24 immersed in the porous sintered metal 31 penetrates the gap between the porous sintered metal 31 by the capillary pressure and reaches the heat receiving plate 12. The internal space surrounded by the porous sintered metal 31 becomes a steam flow path 32 through which the working fluid vapor evaporated by the heat supplied from the heat receiving plate 12 (FIG. 1) flows.
The second wick 22 is a wick having relatively low flow resistance and high permeability. In the present embodiment, the second wick 22 is configured as a groove wick 34 having a plurality of grooves 33 extending in the longitudinal direction on the inner wall surface 15A. Yes. The hydraulic fluid 24 condensed by the radiating fins 13 reaches the boundary portion 23 through these groove portions 33. In this case, the lead angle of the groove 33 (groove) with respect to the longitudinal direction of the heat pipe 11 (container 15) is preferably in the range of 0 degrees to 20 degrees.
In this embodiment, as shown in FIGS. 3 and 4, the height H1 of the one end 11A of the heat pipe 11 is higher than the height H2 of the other end 11B, and further, the wall thickness t1 of the container 15 at the one end 11A. Is formed to be relatively thicker than the wall thickness t2 on the other end 11B side.

  According to the present embodiment, in the heat transport device 10 including the heat pipe 11 in which the working fluid 24 is sealed, the heat receiving plate 12 is provided on the one end 11A side of the heat pipe 11, and the heat radiation fins 13 are provided on the other end 11B. The heat pipe 11 includes a bent portion 11C that is bent between the one end 11A side and the other end 11B side, and the bent portion 11C is disposed in the lower part in the gravitational direction, so that the working fluid 24 easily accumulates in the bent portion 11C. . Further, the first wick 21 and the second wick 22 for transferring the working fluid 24 to the inner wall of the heat pipe 11 are provided, and the boundary portion 23 between the first wick 21 and the second wick 22 is disposed in the bent portion 11C. The boundary portion 23 between the wick 21 and the second wick 22 is immersed in the hydraulic fluid 24 accumulated in the bending portion 11C. Therefore, due to the capillary pressure of the first wick 21, the first wick 21 serves as a pump for returning the working fluid 24 to a higher position, and the second wick 22 quickly transfers the working fluid 24 from the liquid reservoir to the first wick 21. It plays the role of a water transmission pipe, and efficient hydraulic fluid circulation is performed. Thereby, since the recirculation | reflux of the hydraulic fluid 24 to the one end 11A side of the heat pipe 11 in which the heat receiving plate 12 is provided is accelerated | stimulated, heat transport efficiency can be improved with simple structure.

  Further, according to the present embodiment, the first wick 21 having a relatively large capillary pressure is arranged on the one end 11A side of the heat pipe 11, and the flow resistance is relatively on the other end 11B side of the heat pipe 11. Since the small second wick 22 is disposed, for example, even when the heat receiving plate 12 is disposed in the top heat mode in which the heat receiving plate 12 is disposed at the upper part in the gravity direction, the working fluid 24 to the one end 11A side of the heat pipe 11 is supplied. It can be refluxed efficiently.

Moreover, according to this embodiment, since the 1st wick 21 was set as the structure provided with the porous sintered metal 31 produced | generated by sintering spherical body or atypical powder, a wick with relatively large capillary pressure is easy. It can be formed with a simple structure.
Moreover, according to this embodiment, since the 2nd wick 22 is provided with the some groove part 33 extended in the longitudinal direction in 15 A of inner wall surfaces of the heat pipe 11, a wick with relatively small flow resistance is formed with a simple structure. be able to.

Next, examples will be described.
Example 1
The container 15 of the heat pipe 11 was a cylindrical container having an outer diameter of 10 mm, a wall thickness of 0.3 mm, and a length of 260 mm. The heat pipe 11 (container 15) was pressed and flattened so that the thickness H1 on one end 11A side was 4.0 mm and the thickness H2 on the other end 11B side was 2.5 mm. A heat receiving plate 12 made of copper metal was arranged on the one end 11A side, and a heat radiation fin 13 made of aluminum and having a length of 100 mm was arranged on the other end 11B side.
Further, on the inner wall surface 15A of the container 15, as the first wick 21, a porous sintered metal 31 is arranged on the one end 11A side so that the thickness is 1.3 mm and the height of the steam channel 32 is 0.8 mm. did. Further, the second sintered wick 22 was also disposed on the other end 11B side so that the porous sintered metal 31 had a thickness of 0.7 mm and the vapor channel 32 had a height of 0.5 mm.
The heat pipe 11 was provided with a bent portion 11C between the one end 11A and the other end 11B, and the boundary portion 23 of the wick made of two types of porous sintered metals 31 was formed to be the bent portion 11C. In this state, a heater having a size of 16 mm × 16 mm was attached to the heat receiving plate 12, and the maximum heat transport amount and the thermal resistance between the heater and room temperature were measured.

The maximum heat transport amount is the maximum heat amount that can be transported by the heat pipe 11, and is the maximum value at which the hydraulic fluid 24 does not dry out in the heat pipe 11.
The temperature at one end 11A serving as the evaporation section and the temperature at the other end 11B serving as the condensing section are respectively measured, and when these temperature differences are equal to or greater than a predetermined temperature difference, it is determined that the dryout has occurred. The amount of heat of the heater immediately before this dryout was measured.
Further, the thermal resistance between the heater and the room temperature is a value obtained by dividing the temperature difference between the heater temperature and the room temperature (atmosphere temperature) during the maximum heat transport by the maximum heat transport amount. This value was measured and calculated.

(Example 2)
Compared to Example 1, the porous sintered metal 31 constituting the first wick 21 is different in that the thickness is 1.0 mm and the height of the steam channel 32 is 1.4 mm. Other configurations are the same as those in the first embodiment, and thus the description thereof is omitted.

(Example 3)
In Example 3, the second wick 22 provided on the other end 11B side of the heat pipe 11 is not a porous sintered metal 31 but a groove wick 34 having a plurality of grooves 33 extending in the longitudinal direction. This is different from the first embodiment. Other configurations are the same as those of the first embodiment.
In Example 3, the depth d of the groove 33 (groove) was 0.25 mm, and the height of the steam channel 32 was 1.4 mm. Since the thickness H2 on the other end 11B side is 2.5 mm, the thickness t2 of the heat pipe 11 (container 15) on the other end 11B side is 0.3 mm. For this reason, the depth d of the groove 33 (groove) with respect to the thickness t2 of the heat pipe 11 (container 15) is 83.3%.

Example 4
The fourth embodiment is different from the third embodiment in that the depth d of the groove 33 (groove) in the second wick 22 is 0.20 mm and the height of the steam flow path 32 is 1.5 mm. Others are the same as Example 3.
In Example 4, the depth d of the groove 33 (groove) with respect to the thickness t2 of the heat pipe 11 (container 15) is 66.7%.

(Example 5)
The fifth embodiment is different in that the porous sintered metal 31 constituting the first wick 21 is arranged so that the thickness is 1.0 mm and the height of the steam channel 32 is 1.4 mm. Others are the same as the fourth embodiment.

(Example 6)
The sixth embodiment is different from the third embodiment in that the depth d of the groove 33 (groove) in the second wick 22 is 0.15 mm and the height of the steam flow path 32 is 1.6 mm. Others are the same as Example 3.
In Example 6, the depth d of the groove 33 (groove) with respect to the wall thickness t2 of the heat pipe 11 (container 15) is 50%.

(Example 7)
The seventh embodiment is different from the third embodiment in that the depth d of the groove 33 (groove) in the second wick 22 is 0.10 mm and the height of the steam flow path 32 is 1.7 mm. Others are the same as Example 3.
In Example 6, the depth d of the groove 33 (groove) with respect to the thickness t2 of the heat pipe 11 (container 15) is 33.3%.

  Table 1 shows values of the maximum heat transport amount and the heater-room temperature thermal resistance in Examples 1 to 7.

この表１によれば、第２ウィック２２に多孔質焼結金属３１よりも相対的に流動抵抗の小さいグルーブウィック３４を設けた構成では、第１ウィック２１及び第２ウィック２２に多孔質焼結金属３１を設けた既存の構成に比べて、最大熱輸送量で１．５倍、熱抵抗において約０．２度／Ｗの低減という熱輸送特性の向上効果が得られた。
更に、第２ウィック２２として、長手方向に延びる複数の溝部３３を備えたグルーブウィック３４を設けた構成の中でも、溝部３３の深さｄを０．１０〜０．２０ｍｍとした構成では、最大熱輸送量が１１０Ｗ以上となり、ヒーター・室温間熱抵が０．７０℃／Ｗ以下となる。
このため、溝部３３の深さｄを闇雲に設定するのではなく、溝部３３の深さｄは、ヒートパイプ１１の肉厚に対して３０〜７０％の深さとすることで、より一層の熱輸送特性の向上を図ることができる。

According to Table 1, in the configuration in which the second wick 22 is provided with the groove wick 34 having a smaller flow resistance than the porous sintered metal 31, the first wick 21 and the second wick 22 are porously sintered. Compared with the existing configuration in which the metal 31 is provided, the effect of improving the heat transport property is obtained, that is, the maximum heat transport amount is 1.5 times and the thermal resistance is reduced by about 0.2 degrees / W.
Further, among the configurations in which the groove wick 34 provided with a plurality of groove portions 33 extending in the longitudinal direction is provided as the second wick 22, the maximum heat is obtained when the depth d of the groove portion 33 is 0.10 to 0.20 mm. The transport amount is 110 W or more, and the heat resistance between the heater and room temperature is 0.70 ° C./W or less.
For this reason, the depth d of the groove part 33 is not set to a dark cloud, but the depth d of the groove part 33 is set to a depth of 30 to 70% with respect to the thickness of the heat pipe 11, thereby further increasing heat. The transport characteristics can be improved.

Next, a configuration in which the position of the boundary portion 23 between the first wick 21 and the second wick 22 is changed will be described.
(Example A)
FIG. 5 is a schematic diagram of the internal structure of the heat transport device according to Example A.
In the embodiment A, the boundary portion 23 between the first wick 21 and the second wick 22 is provided at a position that is 0 degree in the direction of gravity with respect to the bending portion 11C. Specifically, the angle formed between the reference line 50 extending in the direction of gravity (vertically downward) from the bending center O of the bending part 11C and the boundary part 23 is 0 degrees, that is, the boundary part 23 is positioned on the reference line 50. Is provided.
The configuration other than the position of the boundary portion 23 of the heat pipe 100 is the same as that of the fifth embodiment described above.

(Example B)
FIG. 6 is a schematic diagram of the internal structure of the heat transport device according to Example B.
In the embodiment B, the boundary portion 23 between the first wick 21 and the second wick 22 is provided at a position shifted from the reference line 50 toward the other end 11B of the heat pipe 11. Specifically, the boundary portion 23 is provided at a position moved from the reference line 50 to the other end 11B side of the heat pipe 11 by a predetermined distance L (20 mm). The configuration other than the position of the boundary portion 23 of the heat pipe 100 is the same as that of the fifth embodiment described above.

(Example C)
FIG. 7 is a schematic diagram of the internal structure of the heat transport device according to Example C.
In Example C, the boundary portion 23 between the first wick 21 and the second wick 22 is provided at a position that is 45 degrees in the direction of gravity with respect to the bending portion 11C. Specifically, the angle formed by the reference line 50 and the boundary portion 23 is provided at a position of 45 degrees.
The configuration other than the position of the boundary portion 23 of the heat pipe 100 is the same as that of the fifth embodiment described above.

(Example D)
FIG. 8 is a schematic diagram of the internal structure of the heat transport device according to Example D.
In Example D, the boundary portion 23 between the first wick 21 and the second wick 22 is provided at a position that is 90 degrees in the direction of gravity with respect to the bending portion 11C. Specifically, the angle between the reference line 50 and the boundary part 23 is 90 degrees, that is, the boundary part 23 is located on the horizontal reference line 51 extending in the horizontal direction from the bending center O of the bending part 11C. ing.
The configuration other than the position of the boundary portion 23 of the heat pipe 100 is the same as that of the fifth embodiment described above.

  Table 2 shows values of the maximum heat transport amount and the thermal resistance between the heater and the room temperature (relationship between the wick boundary installation position and the characteristics) in Examples A to D.

According to this configuration, in Examples A to C in which the boundary portion 23 is provided at an angular position smaller than 45 degrees in the gravity direction with respect to the bending portion 11C, the boundary portion 23 is in the gravity direction with respect to the bending portion 11C. As compared with Example D provided at the position of 90 degrees, the maximum heat transport amount was 1.5 times and the heat resistance was improved by about 0.2 degrees / W in thermal resistance.
Thus, the boundary part 23 can be immersed in the hydraulic fluid 24 by configuring the heat pipe 11 so that the boundary part 23 between the first wick 21 and the second wick 22 is located in the lower part in the direction of gravity. Therefore, due to the capillary pressure of the first wick 21, the first wick 21 serves as a pump for returning the working fluid 24 to a higher position, and the second wick 22 quickly transfers the working fluid 24 from the liquid reservoir to the first wick 21. It plays the role of a water transmission pipe, and efficient hydraulic fluid circulation is performed. Thereby, since the recirculation | reflux of the hydraulic fluid 24 to the one end 11A side of the heat pipe 11 in which the heat receiving plate 12 is provided is accelerated | stimulated, heat transport efficiency can be improved with a simple structure.

Next, a modification of this embodiment will be described.
FIG. 9 is a schematic diagram of the internal structure of the heat transport device 10 according to the modification.
In this configuration, as shown in FIG. 9, the heat pipe 11 not only includes a bent portion 11C between the one end 11A and the other end 11B, but the bent portion 11C is located at the lowermost portion of the heat pipe 11 in the gravity direction. A storage unit 11D that is positioned and stores the hydraulic fluid 24 is provided. And the boundary part 23 of the 1st wick 21 and the 2nd wick 22 is formed so that it may be located in the storage part 11D of the bending part 11C.
In this configuration, the hydraulic fluid 24 condensed by the heat radiating fins 13 on the other end 11B side of the heat pipe 11 flows to the storage unit 11D through the second wick 22, and is stored in the storage unit 11D. Thereby, since the hydraulic fluid 24 collected in the storage part 11D is always immersed in the first wick 21, the return of the hydraulic fluid 24 to the one end 11A side of the heat pipe 11 provided with the heat receiving plate 12 is promoted. Therefore, the heat transport efficiency can be further increased.

Next, another embodiment will be described.
FIG. 10 is a schematic diagram of the internal structure of a heat transport device 110 according to another embodiment.
In the above-described embodiment, the configuration in which the groove wick 34 provided with the plurality of groove portions 33 extending in the longitudinal direction is provided as the second wick 22 having relatively small flow resistance on the other end 11B side of the heat pipe 11 has been described. . However, the second wick 122 having a different configuration may be provided as long as the flow resistance is relatively small.
In another embodiment, a metal braided wire 131 may be provided as the second wick 122. The metal braided wire 131 is formed by forming a plurality of fine metal wires in a net shape, and has a smaller flow resistance than the porous sintered metal 31 of the first wick 21.
As shown in FIG. 11, the metal braided wire 131 is disposed on both ends in the width direction of the other end 11 </ b> B that has been pressed and flattened, and a steam channel 132 is formed at the center. The metal braided wire 131 may be provided at one end in the width direction described above. In addition, a metal wire mesh or a fine metal net may be arranged as the second wick 122. Moreover, you may combine the structure provided with the above-mentioned storage part 11D in the heat pipe 11 of embodiment separately.

(Example 8)
In Example 8, two metal braided wires in which 250 fine metal wires (elementary wire Φ0.06 mm) are formed in a net shape are used, and these metal braided wires 131 are disposed on both ends in the width direction of the other end 11B. Arranged respectively. The other configuration except for the other end 11B side is the same as that of the second embodiment.

Furthermore, another embodiment will be described.
FIG. 12 is a schematic diagram of the internal structure of a heat transport device 210 according to another embodiment.
In this other embodiment, the heat transport device 210 includes, on the other end 11B side of the heat pipe 11, a porous sintered metal 231 formed by sintering a spherical body or atypical powder as the second wick 222. . As shown in FIG. 13, the porous sintered metal 231 is provided at the center in the width direction of the heat pipe 11, and steam flow paths 232 are provided on the left and right inside the heat pipe 11 with the porous sintered metal 231 sandwiched therebetween. Is formed.
Moreover, you may combine the structure provided with the above-mentioned storage part 11D in the heat pipe 11 of embodiment separately.

Example 9
FIG. 14 is a cross-sectional view of the other end 11B side of the heat pipe 11 according to the ninth embodiment.
In Example 9, semi-elliptical porous sintered metals 231 and 231 formed by sintering one or more spherical bodies or irregular powders are formed so that the elliptical arc surfaces are opposed to each other. It is provided in the center in the width direction. Specifically, the elliptic porous sintered metal 231 has a width of 0.95 mm when two are stacked with a width of 6 mm. The other configuration except for the other end 11B side is the same as that of the second embodiment.

  Table 3 shows values of the maximum heat transport amount and the thermal resistance between the heater and room temperature in Examples 8 and 9.

In Examples 8 and 9, the metal braided wire 131 or the porous sintered metal 231 is provided as the second wick 122 provided on the inner wall surface 15A of the other end 11B of the heat pipe 11, so that the configuration of Example 2 is achieved. In comparison, the effect of improving the heat transport property was obtained, in which the maximum heat transport amount was 1.5 times or more and the thermal resistance was reduced by about 0.2 degrees / W.
In particular, the reason why Example 9 is good is that, in addition to the capillary force of the semi-elliptical porous sintered metals 231 and 231, an acute angle portion is constructed by contact between the arc surfaces, and a groove groove is formed at that portion. It is considered that the additional capillary force and low flow resistance are achieved.

As mentioned above, although this invention was concretely demonstrated based on embodiment, this invention is not limited to the said embodiment, It can change in the range which does not deviate from the summary.
For example, in the above-described embodiment, the heat transport devices 10, 110, and 210 have been described with respect to the configuration in the top heat mode in which the heat receiving plate 12 is located at the upper part in the gravity direction, but the heat receiving plate 12 is located at the lower part in the gravitational direction. It is obvious that the present invention may be applied to the configuration of the bottom heat mode.

10, 110, 210 Heat transport device 11 Heat pipe 11A One end 11B The other end 11C Bending portion 11D Reserving portion 12 Heat receiving plate (heat receiving portion)
13 Heat radiation fin (heat radiation part)
14 Heating elements (cooling target parts)
15 container 15A inner wall surface (inner wall)
21 First wick 22, 122, 222 Second wick 23 Boundary portion 24 Hydraulic fluid 31, 232 Porous sintered metal 32, 132, 232 Steam flow path 33 Groove portion 34 Groove wick 131 Metal braided wire

Claims (10)

In a heat transport device comprising a heat pipe enclosing a working fluid, providing a heat receiving part on one end side of the heat pipe, and providing a heat radiating part on the other end side,
On the inner wall of the heat pipe, a first wick having a relatively large capillary pressure is disposed at the heat receiving portion of the heat pipe, and a first fluid wick having a relatively low flow resistance is disposed at the heat radiating portion of the heat pipe. 2 and wick is arranged, together with arranging the boundary portion of the first wick and the second wick at the bottom of the gravity direction, Bei give a bent bent portion between the heat dissipating part and the heat receiving portion, The heat transport device according to claim 1, wherein the heat receiving portion is disposed at an upper portion in the gravity direction from the bent portion . The heat transport apparatus according to claim 1, wherein the second wick includes a plurality of grooves extending in a longitudinal direction on the inner wall of the heat pipe . The heat transport device according to claim 2, wherein the depth of the groove is 0.10 to 0.20 mm . The depth of the said groove part is a depth of 30 to 70% with respect to the thickness of the said heat pipe, The heat transport apparatus of Claim 2 or Claim 3 characterized by the above-mentioned. The heat transport device according to any one of claims 1 to 4 , wherein the first wick includes a porous sintered metal formed by sintering a spherical body or atypical powder . The heat transport device according to claim 1 , wherein the second wick includes a metal braided wire or a fine metal net . The second wick includes a porous sintered metal produced by sintering a spherical body or atypical powder at the center in the width direction of the heat pipe, and the inside of the heat pipe with the porous sintered metal sandwiched therebetween. The heat transport device according to claim 1 or 5 , wherein steam flow paths are formed on the left and right . The second wick includes a semi-elliptical porous sintered metal produced by sintering one or more spherical bodies or irregular powders in the center in the width direction of the heat pipe, and the semi-elliptical porous firing metal. the flat portion of the sintered metal is disposed on an inner wall of the heat pipe, according to claim 1 or claim, characterized in that the formation of the steam flow path to the left and right inside the heat pipe across the semi elliptical porous sintered metal Item 6. The heat transport device according to Item 5 . The heat transport device according to any one of claims 1 to 8, wherein the heat pipe has a thickness that is relatively thinner at the other end than at the one end, and is pressed and flattened . The heat transport device according to any one of claims 1 to 9 , wherein the hydraulic fluid is stored in a boundary portion between the plurality of types of wicks .

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