WO2018116951A1 - 放熱モジュール - Google Patents
放熱モジュール Download PDFInfo
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- WO2018116951A1 WO2018116951A1 PCT/JP2017/044904 JP2017044904W WO2018116951A1 WO 2018116951 A1 WO2018116951 A1 WO 2018116951A1 JP 2017044904 W JP2017044904 W JP 2017044904W WO 2018116951 A1 WO2018116951 A1 WO 2018116951A1
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- wick
- working fluid
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- facing
- container
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
- H01L23/00—Details of semiconductor or other solid state devices
- H01L23/34—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements
- H01L23/42—Fillings or auxiliary members in containers or encapsulations selected or arranged to facilitate heating or cooling
- H01L23/427—Cooling by change of state, e.g. use of heat pipes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0233—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes the conduits having a particular shape, e.g. non-circular cross-section, annular
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
- F28D15/046—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure characterised by the material or the construction of the capillary structure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0028—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cooling heat generating elements, e.g. for cooling electronic components or electric devices
Definitions
- the present invention relates to a heat dissipation module.
- This application claims priority on December 20, 2016 based on Japanese Patent Application No. 2016-247075 for which it applied to Japan, and uses the content here.
- Patent Document 1 discloses a heat pipe as one form of a heat dissipation module.
- a heat pipe basically encloses a fluid such as water or alcohol that evaporates and condenses in a target temperature range as a working fluid in a container (container) from which non-condensable gas such as air has been degassed.
- the container further includes a wick for generating a capillary force for refluxing the liquid-phase working fluid.
- the working fluid When the temperature difference occurs in the container, the working fluid is heated and evaporated in the high temperature evaporation section, and the internal pressure of the container also rises.
- the working fluid vapor generated in the evaporating part moves toward the condensing part having a low temperature and pressure, and the heat received by the evaporating part is transported to the condensing part as latent heat of the vapor.
- the working fluid vapor In the condensing section, the working fluid vapor is condensed by heat radiation. Then, the condensed working fluid permeates the wick and returns to the evaporation portion by the capillary force of the wick.
- the operating condition of such a heat dissipation module is expressed by the following calculation formula (a), where the capillary pressure ⁇ PC is the vapor pressure loss ⁇ PV and the liquid pressure loss is ⁇ PL. ⁇ PC ⁇ ⁇ PV + ⁇ PL (a) As can be seen from the calculation formula (a), in order to increase the maximum heat transport amount of the heat dissipation module, it is necessary to increase the capillary force and reduce the pressure loss of the vapor and the liquid.
- a thin heat dissipation module is required to dissipate heat from a CPU or the like mounted on the mobile device.
- a thin heat dissipation module it is necessary to devise the suppression of the decrease in the maximum heat transport amount and the maintenance of the mechanical strength. That is, for a relatively large heat dissipation module, a wide vapor flow path and liquid flow path can be secured, so that the pressure loss of vapor and liquid can be reduced.
- a thin heat dissipation module it is difficult to ensure these widely.
- the thickness of the container is also thin, and it is difficult to ensure its mechanical strength.
- a plurality of wicks may be provided or a plurality of wicks may be branched to form a plurality of liquid flow paths. .
- the steam flow path formed between the wicks in this part becomes narrow, and the pressure loss of the steam may increase locally. There is sex. Further, if the width of the steam flow path is simply increased, a cavity inside the container is expanded, so that the mechanical strength is weakened, which may cause deformation of the container.
- the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a heat dissipation module capable of reducing the pressure loss of the working fluid vapor and ensuring the mechanical strength of the container.
- a heat dissipation module includes a container having an evaporation portion that encloses a working fluid and evaporates the enclosed working fluid, and a condensation portion that condenses the evaporated working fluid, and the container And a wick that moves the condensed working fluid by capillary force from the condensation section to the evaporation section, and the wick has a plurality of liquid flow paths from the condensation section to the evaporation section.
- the facing portion may be provided only in the evaporation portion.
- the uneven portion is formed on both of the facing portions, and in the uneven portion formed on both of the facing portions, the convex portion formed on one of the facing portions is You may provide so that the recessed part formed in the other may be opposed.
- all the vapor flow paths may be connected in the evaporation section.
- a second uneven portion may be formed at a tip of the protruded portion of the uneven portion.
- mode WHEREIN You may have a pillar part between these wick parts.
- mode WHEREIN The side surface of the said pillar part is flat, and the said uneven
- the uneven portion may be formed on the entire side surface of the wick facing the steam flow path except for the facing portion and the facing portion.
- the facing portion may not be provided in the condensing portion.
- mode WHEREIN The convex part and recessed part of the said uneven
- FIG. 2 is a cross-sectional view taken along line AA of the vapor chamber shown in FIG. It is an enlarged view of the opposing part which concerns on one Embodiment of this invention. It is an enlarged view of the modification of the opposing part which concerns on one Embodiment of this invention. It is a plane sectional view of the test device which evaluates the performance of the vapor chamber concerning one embodiment of the present invention. It is a table
- FIG. 1 is a plan sectional view of a vapor chamber 1 according to this embodiment.
- FIG. 2 is a cross-sectional view taken along the line AA of the vapor chamber 1 shown in FIG.
- the vapor chamber 1 is a heat transport element that uses the latent heat of the working fluid.
- the vapor chamber 1 includes a container 2 that encloses a working fluid therein, and a wick 3 that is disposed inside the container 2.
- the working fluid is a heat transport medium composed of a well-known phase change material, and changes phase between the liquid phase and the gas phase in the container 2.
- a phase change material for example, water (pure water), alcohol, ammonia or the like can be employed as the working fluid.
- the working fluid may be described by describing the case of liquid phase as “working fluid” and the case of gas phase as “vapor”. Further, when the liquid phase and the gas phase are not particularly distinguished, they may be described as working fluid. The working fluid is not shown.
- the container 2 is a hermetically sealed hollow container, and is formed in a flat shape in which the dimension in the plane direction (up and down, left and right direction in FIG. 1) is larger than the thickness direction (vertical direction in FIG. 1 and up and down direction in FIG. 2). Has been.
- the thickness of the container 2 is, for example, a comma number of mm to about 3 mm.
- the container 2 has a substantially rectangular shape in plan view as viewed from the thickness direction.
- the container 2 is formed with an evaporation unit 4 for evaporating the enclosed working fluid and a condensing unit 5 for condensing the evaporated working fluid.
- the evaporation part 4 is formed in the center above the paper surface in FIG.
- the evaporation unit 4 is a region that receives heat from the heat source 100.
- the evaporation unit 4 may receive heat not only from the same region as the outer shape (mounting area) of the heat source 100 but also from a region that is slightly larger than the outer shape.
- the condensation unit 5 is a region formed around the evaporation unit 4 and is a region other than the evaporation unit 4.
- the heat source 100 an electronic component of an electronic device, for example, a CPU or the like can be given.
- the container 2 has a container body 10, a top plate 11, and a bottom plate 12, as shown in FIG.
- the container body 10 can be formed from, for example, copper, copper alloy, aluminum, aluminum alloy, or the like.
- the top plate 11 and the bottom plate 12 are made of, for example, copper, copper alloy, aluminum, aluminum alloy, iron, stainless steel, a composite material of copper and stainless steel (Cu-SUS), or a composite material in which stainless steel is sandwiched between copper (Cu -SUS-Cu), a composite material of nickel and stainless steel (Ni-SUS), a composite material in which stainless steel is sandwiched between nickel (Ni-SUS-Ni), and the like.
- the top plate 11 and the bottom plate 12 are formed from a material having high hardness to prevent deformation of the container 2.
- the top plate 11 and the bottom plate 12 are a composite material of copper and stainless steel (Cu-SUS), a composite material in which stainless steel is sandwiched between copper (Cu-SUS).
- -SUS-Cu a composite material of nickel and stainless steel
- Ni-SUS nickel and stainless steel
- Ni-SUS-Ni a composite material in which stainless steel is sandwiched between nickel
- top plate 11 and the bottom plate 12 may be formed of the same material or different materials. Moreover, the top plate 11 and the bottom plate 12 may have the same thickness or different thicknesses. Further, either the top plate 11 or the bottom plate 12 may be formed integrally with the container body 10. For example, by forming a groove with one of the top plate 11 and the bottom plate 12 by press molding, a member that also serves as a frame portion 10a and a column portion 10b described later of the container body 10 is formed, and the other is joined thereto. Therefore, the container 2 may be formed.
- the container body 10 includes a frame portion 10 a that forms the outer shape of the container 2, and a plurality of column portions 10 b that are arranged in a region surrounded by the frame portion 10 a.
- the plurality of column portions 10 b are arranged at a certain interval in the short direction of the container 2, and extend parallel to the longitudinal direction of the container 2.
- the plurality of column portions 10 b are provided to prevent expansion and dent in the thickness direction of the container 2.
- the plurality of pillar portions 10 b serve as pillars (reinforcing members) that support the container 2 and ensure the mechanical strength of the thin vapor chamber 1.
- a gap is formed between the frame portion 10a and the column portion 10b and between the adjacent column portions 10b, and the working fluid flow path 13 is formed in the gap.
- the working fluid flow path 13 of this embodiment is composed of a plurality of (four in this embodiment) channels 13a.
- the longitudinal direction is the vertical direction in FIG.
- the working fluid flow path 13 is sealed by joining the top plate 11 and the bottom plate 12 to the container body 10 as shown in FIG.
- the working fluid flow path 13 has a first surface 14 that receives heat from the heat source 100, a second surface 15 opposite to the first surface 14, and a connection that connects the first surface 14 and the second surface 15. And is surrounded by a surface 16.
- the container 2 of the present embodiment is configured to receive heat from the heat source 100 from the bottom plate 12 side, and the upper surface of the bottom plate 12 becomes the first surface 14 and the lower surface of the top plate 11 becomes the second surface 15.
- the side surface of the column part 10 b (or the inner side surface 10 a 1 of the frame part 10 a shown in FIG. 1) is configured to be the connection surface 16.
- the side surface of the column part 10 b faces the steam channel 17.
- the connection surface 16 of the column part 10b is flat (that is, no concavo-convex part is provided), and the column part 10b alone is not configured to generate a capillary force.
- the wick 3 is arranged in the working fluid flow path 13 as shown in FIG.
- the working liquid evaporates in the evaporating unit 4 to become vapor, and in the condensing unit 5, the vapor is condensed into the working liquid, and is moved from the condensing unit 5 to the evaporating unit 4 by capillary force ( Reflux).
- the wick 3 of this embodiment includes a plurality of wick branches 20 (wick parts) disposed in each channel 13a of the working fluid flow path 13 and a wick trunk 21 that connects the roots of the plurality of wick branches 20 to each other. .
- Each wick branch 20 and the width of the wick trunk 21 are formed to be the same.
- the wick 3 is formed of a mesh in which a plurality of fine lines are knitted in a lattice shape.
- a copper material having a high thermal conductivity can be suitably used.
- the fine wire has a diameter of several tens of ⁇ m to several tens of ⁇ m.
- a working fluid vapor channel 17 is formed between the side surface 3a of the wick 3 and the connection surface 16 disposed with a space in between the side surface 3a.
- the gap 18 a formed at the interface between the wick 3 and the first surface 14 and the second surface 15 becomes a liquid flow path 18 for flowing the working fluid, and the working fluid is refluxed from the condensing unit 5 to the evaporation unit 4.
- the narrow wire gap 18 b inside the wick 3 also becomes a liquid flow path 18 for flowing the working fluid, and the working fluid is refluxed from the condensing unit 5 to the evaporation unit 4.
- the narrow gap 18b has a smaller space than the gap 18a formed at the interface between the wick 3 and the first surface 14 and the second surface 15, and therefore the liquid flow path 18 of the gap 18a is closer to the gap 18b.
- the hydraulic fluid transport capacity is greater than that of the liquid flow path 18.
- the plurality of wick branches 20 form a plurality of the liquid channels 18 described above.
- the plurality of wick branches 20 are inserted into the channels 13 a from the wick trunk 21, extend from the channels 13 a to the mounting region of the heat source 100, and the respective distal ends are inserted into the evaporation unit 4 independently.
- the first wick branch portion 20a and the fourth wick branch portion 20d extend along the inner surface 10a1 of the frame portion 10a from the condensation portion 5 and are inserted into the evaporation portion 4.
- the second wick branch part 20 b and the third wick branch part 20 c extend between the adjacent column parts 10 b from the condensing part 5 and are inserted into the evaporation part 4.
- Each is formed with a pillar portion 20.
- tip parts of the some wick branch part 20 are concentrated. For this reason, all the vapor flow paths 17 are connected in the evaporation part 4.
- the plurality of wick branches 20 have opposing parts 23 that face each other across the vapor flow path 17 (space) in the evaporation part 4.
- the evaporating unit 4 has a facing part 23ab where the first wick branch part 20a and the second wick branch part 20b face each other, and a facing part where the second wick branch part 20b and the third wick branch part 20c face each other.
- FIG. 3 is an enlarged view of the facing portion 23 according to the present embodiment.
- FIG. 3 is a schematic view of the facing portion 23ab of the first wick branch portion 20a and the second wick branch portion 20b, but the other facing portions 23 have the same configuration.
- an uneven portion 30 is formed in the facing portion 23ab.
- the concavo-convex portion 30 of the present embodiment includes a facing portion 23a of the first wick branch portion 20a facing the second wick branch portion 20b and a facing portion 23b of the second wick branch portion 20b facing the first wick branch portion 20a. It is formed in both.
- the concavo-convex part 30 has a plurality of convex parts 31 and concave parts 32, and the convex parts 31 and the concave parts 32 are alternately arranged along the steam flow path 17.
- the convex part 31 and the concave part 32 of the concavo-convex part 30 are each formed in a rectangular shape in plan view shown in FIG. That is, the corner portion of the convex portion 31 and the corner portion of the concave portion 32 are formed at right angles.
- Such a concavo-convex portion 30 can be formed by die cutting with a press.
- the lengths of the convex portion 31 and the concave portion 32 in the direction along the steam flow path 17 are the same. In addition, the length of the direction along the steam flow path 17 of the convex part 31 and the recessed part 32 may mutually differ.
- the convex portion 31 of the concavo-convex portion 30 formed on one of the opposing portions 23ab is the concave portion 32 of the concavo-convex portion 30 formed on the other of the opposing portions 23ab (for example, the opposing portion 23b). It is provided so as to face each other. That is, the protrusions 31 (or the recesses 32) are alternately arranged in the uneven portion 30 formed in the facing portion 23a and the uneven portion 30 formed in the facing portion 23b.
- the main flow path width of the steam flow path 17 refers to the space width between the side surfaces 3a of the wicks 3 facing each other when the uneven portion 30 is not present.
- 3 indicates the length (depth) from the tip of the convex portion 31 of the concavo-convex portion 30 to the bottom of the concave portion 32.
- the tip of the convex portion 31 is the side surface 3a of the wick 3
- the concave portion 32 is a groove formed at a depth b with respect to the side surface 3a.
- the depth b is formed to a size of about 2 mm, for example, when the width of the wick branch 20 shown in FIG. 1 is 5 mm.
- the maximum width c of the steam flow path 17 is formed larger than the main width a.
- the maximum width c is about twice as large as 4 mm.
- the concavo-convex portion 30 formed on the facing portion 23a and the concavo-convex portion 30 formed on the facing portion 23b are arranged so that the convex portions 31 (or the concave portions 32) are staggered,
- the maximum width c of the steam channel 17 is constant.
- the vapor chamber 1 receives the heat generated by the heat source 100, whereby the working fluid in the evaporation unit 4 evaporates.
- the working fluid that has permeated the wick 3 evaporates.
- the vapor generated in the evaporation unit 4 flows in the vapor channel 17 toward the condensing unit 5 having a lower pressure and temperature than the evaporation unit 4.
- the wick 3 is disposed with a gap from the connection surface 16, the steam can flow along the side surface 3 a of the wick 3.
- the steam that has reached the condensing unit 5 is cooled and condensed.
- the hydraulic fluid generated in the condensing unit 5 permeates the wick 3 and is refluxed from the condensing unit 5 to the evaporation unit 4.
- the wick 3 has a plurality of wick branches 20 extending from the condenser 5 to the evaporator 4, and the working fluid is recirculated from the condenser 5 to the evaporator 4 by the liquid flow path 18 formed by each wick branch 20. . Since the wick branch portion 20 is in contact with the first surface 14 and the second surface 15 of the working fluid flow path 13 from the condensation portion 5 to the evaporation portion 4 as shown in FIG. The mechanical strength of the thin vapor chamber 1 is ensured.
- the concavo-convex part 30 is formed in these facing parts 23.
- the pressure loss is energy loss in the flow direction due to the shear stress acting on the pipe acting as friction on the fluid in the case of laminar flow in the pipe flow. This shear stress is greatest at the wall surface forming the flow path.
- the side surface 3a of the wick 3 is arranged uniformly with respect to the steam flow path 17, whereas in the wick structure of this embodiment, the steam flow is as shown in FIG.
- the main width a of the channel 17 is the same as that of the conventional structure, the wall surface can be moved away from the steam channel 17 by the presence of the recess 32. For this reason, pressure loss can be reduced compared with the conventional structure. For this reason, in this embodiment, even if all the steam flow paths 17 are connected via the evaporator 4, the vapor pressure in all the steam paths 17 can be made uniform while reducing the pressure loss.
- the facing portion 23 is provided only in the evaporation portion 4. Note that the position of the facing portion 23 is not limited to the evaporation portion 4 alone.
- the material of the container 2 is thin so as to secure the internal space as much as possible. For this reason, in the vapor chamber 1 in which the inside is a negative pressure, if the width of the steam flow path 17 is simply increased in order to reduce the pressure loss of the steam, there is a possibility that the steam chamber 17 is easily deformed. For this reason, in the wick structure of the present embodiment, not only the recesses 32 but also the projections 31 are formed, so that the columns that support the containers 2 are partially left and the containers 2 are reinforced. That is, according to the wick structure of the present embodiment, the container 2 can be reinforced while the flow passage width of the vapor flow passage 17 is widened by forming the uneven portion 30 in the facing portion 23. For this reason, according to the wick structure of the present embodiment, the pressure loss of the steam can be reduced and the mechanical strength of the container 2 can be ensured.
- the convex portion 31 formed in one opposing portion 23 is provided so as to oppose the concave portion 32 of the other opposing portion 23. According to this configuration, even if the concave portion 32 is formed in the wick branch portion 20, the convex portion 31 protrudes from the wick branch portion 20 facing the wick branch portion 20 toward the concave portion 32.
- the width of the path 17 is never greater than c. Further, since the width of the steam flow path 17 in the facing portion 23 is kept constant at c, the width of the steam flow path 17 is not locally reduced, and the pressure loss of the steam can be suitably reduced. it can.
- the facing portions 23 of the plurality of wick branch portions 20 are provided in the evaporation portion 4. Since the concavity and convexity portions 30 are formed in the facing portions 23, the thermal resistance of the evaporation portion 4 can be reduced. That is, as shown in FIG. 2, when the wick branch 20 is in contact with the first surface 14 and the second surface 15 of the working fluid channel 13, the evaporation is performed on the side surface 3 a (portion in contact with the vapor channel 17). Arise.
- grooved part 30 is formed in the part which contact
- FIG. 4 is an enlarged view of a modified example of the facing portion 23 according to the present embodiment.
- a second uneven portion 30 a is formed at the tip of the protruded portion 31 of the uneven portion 30.
- the second concavo-convex portion 30a is formed by making a plurality of cuts at the tip of the convex portion 31 of the concavo-convex portion 30 with a cutter or the like.
- the 2nd uneven part 30a has the convex part 31a and the recessed part 32a, and the convex part 31a has spread toward the steam flow path 17 like the hair of a brush.
- the second uneven portion 30a can secure a larger evaporation area than the wick structure shown in FIG. 3, and the thermal resistance of the evaporation portion 4 can be further reduced.
- FIG. 5 is a plan sectional view of a test apparatus for evaluating the performance of the vapor chamber 1 according to the present embodiment.
- FIG. 6 is a table showing test results obtained by the test apparatus shown in FIG.
- a test apparatus as shown in FIG. 5 was prepared.
- a heat source 100 (heater sensor) is attached to one plate surface (for example, the back surface) of the vapor chamber 1, and a plurality of temperature sensors T1 to T7 are mounted to the other plate surface (for example, the front surface) of the vapor chamber 1. It is configured.
- the temperature of the evaporation unit 4 was measured by a heater sensor as the heat source 100, the temperature of the condensing unit 5 was measured by a plurality of temperature sensors T1 to T7, and the performance of the vapor chamber 1 was evaluated by thermal resistance.
- the thermal resistance is obtained by the following formula (1).
- Q [W] is the amount of heat (so-called heat input) applied per unit time by the heat source 100.
- Th [° C.] is the temperature of the heat source 100 (evaporating unit 4).
- T1-7 [° C.] is the temperature of the condensing unit 5 detected by the temperature sensors T1-7.
- the amount of heat input is the amount of power when the heat source 100 is an electric heater.
- the temperature Th is measured in a state where the amount of heat input from the heat source 100 balances with the amount of heat released through the vapor chamber 1 and reaches equilibrium. In addition, thermal resistance becomes small, so that the heat transport capability of the vapor chamber 1 is high.
- FIG. 6 shows, as a comparative example, a normal wick structure in which the concavo-convex portion 30 is not provided in the facing portion 23, a wick structure in the present embodiment in which the concavo-convex portion 30 is formed in the facing portion 23, and a first
- grooved parts 30a (cut) was formed is shown.
- the total thickness of the test apparatus of the vapor chamber 1 provided with each wick structure is the same.
- the wick structure of the present embodiment in which the concavo-convex portion 30 is formed has a thermal resistance of about 20% smaller than the normal wick structure (the heat transport capability is 20%).
- the wick structure of the modified example in which the second uneven portion 30a is further formed has a thermal resistance of about 40% smaller than the normal wick structure (the heat transport capability is increased by about 40%).
- the thermal resistance is increased by about 40%.
- the container having the working fluid enclosed therein, the evaporation section 4 for evaporating the sealed working fluid, and the condensing section 5 for condensing the evaporated working fluid.
- a wick 3 that is disposed inside the container 2 and moves the condensed working fluid from the condensing unit 5 to the evaporating unit 4 by capillary force, and the wick 3 includes a plurality of components from the condensing unit 5 to the evaporating unit 4.
- a plurality of wick branches 20 that form the liquid flow path 18, and the plurality of wick branches 20 have opposing portions 23 that face each other across the vapor flow path 17 of the working fluid.
- the vapor chamber 1 that can reduce the pressure loss of the vapor of the working fluid and ensure the mechanical strength of the container 2 is obtained. Moreover, according to this structure, the evaporation area of a working fluid can be expanded in the evaporation part 4, a thermal resistance can be reduced, and heat transport capability can be improved.
- FIGS. 7 to 9C can be adopted.
- the same or equivalent components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is simplified or omitted.
- the concavo-convex portion 30 is formed not only on the facing portion 23 but also on the entire side surface 3a that is in contact with the steam flow path 17 other than the facing portion 23. According to this configuration, the pressure loss can be reduced in the entire steam flow path 17 and the mechanical strength of the container 2 can be ensured. That is, while the side surface (connection surface) of the column part 10b is flat, the uneven
- the convex portion 31 of the concavo-convex portion 30 formed on one of the facing portions 23ab is formed on the other of the facing portions 23ab (for example, the facing portion 23b). It is provided so as to face the convex portion 31 of the formed concave-convex portion 30.
- the uneven portion 30 is not formed on one of the facing portions 23ab (for example, the facing portion 23a), and the other of the facing portions 23ab (for example, the facing portion 23b). An uneven portion 30 is formed on the surface.
- the wall surface can be moved away from the steam flow path 17 as in the above-described embodiment, so that the pressure loss is reduced compared to the conventional structure, and the container 2 The mechanical strength of can be ensured.
- the wick structure shown in FIG. 8B having more concave portions 32 is preferable to the wick structure shown in FIG. 8A, and the maximum width c is larger than the wick structure shown in FIG. 8A.
- the fixed wick structure shown in FIGS. 3 and 4 is preferred.
- the wick 3D according to the modification shown in FIG. 9A has a concavo-convex portion 30d formed in a wave shape, and the convex portion 31d and the concave portion 32d are each formed in a curved shape in plan view.
- the wick 3E according to the modification shown in FIG. 9B has a concavo-convex portion 30e with rounded corners, and the convex portion 31e and the concave portion 32e are formed in a substantially rectangular shape in plan view.
- the wick 3F according to the modification shown in FIG. 9C has a triangular uneven portion 30f, and the convex portion 31f and the concave portion 32f are each formed in a triangular shape in plan view.
- the wall surface can be moved away from the steam flow path 17 as in the above-described embodiment, so that the pressure loss is reduced as compared with the conventional structure, and the container 2 The mechanical strength of can be ensured.
- the configuration shown in FIGS. 9A to 9C when the concavo-convex portions 30d to 30f are formed by press working, compared with the configuration shown in FIG.
- the rectangular wick structure shown in FIGS. 3 and 4 that can ensure a long outline of the edge of the side surface 3a is preferable.
- the configuration in which the wick 3 is divided into a plurality of parts to form the plurality of liquid flow paths 18 has been described.
- the structure which forms 18 may be sufficient.
- the plurality of wick portions may be composed of a plurality of wicks 3.
- the facing portion of the wick portion may be provided at a place other than the evaporation portion 4.
- the wick 3 is a fiber, metal powder, felt, a groove (groove) formed in the container 2, or a combination thereof. It may be formed from.
- the vapor chamber 1 is exemplified as the heat dissipation module, but the above configuration may be applied to a heat pipe which is another form of the heat dissipation module.
- the use of the heat dissipation module of the present embodiment is not particularly limited, but as an example, a smartphone, a tablet terminal, a mobile phone, a personal computer, a server, a copy machine, a game machine, a multifunction machine, a projector, an electronic device, a fuel cell, Examples include artificial satellites.
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Abstract
Description
本願は、2016年12月20日に、日本に出願された特願2016-247075号に基づき優先権を主張し、その内容をここに援用する。
ΔPC ≧ ΔPV+ΔPL …(a)
この計算式(a)から分かるように、放熱モジュールの最大熱輸送量を大きくするためには、毛細管力を大きくし、蒸気と液体の圧力損失を小さくする必要がある。
上記一態様において、前記対向部の両方に、前記凹凸部が形成され、前記対向部の両方に形成された前記凹凸部において、前記対向部の一方に形成された凸部が、前記対向部の他方に形成された凹部に対向するように設けられていてもよい。
上記一態様において、前記蒸発部において全ての蒸気流路は繋がっていてもよい。
上記一態様において、前記凹凸部の凸部の先端に、第2の凹凸部が形成されていてもよい。
上記一態様において、前記複数のウィック部の間に柱部を有してもよい。
上記一態様において、前記柱部の側面が平坦であり、前記ウィックの前記柱部の側面に対向する面に前記凹凸部が形成されていてもよい。
上記一態様において、前記凹凸部は、前記対向部および前記対向部以外で前記蒸気流路に面する前記ウィックの側面の全体に形成されていてもよい。
上記一態様において、前記対向部は、前記凝縮部に設けられていなくてもよい。
上記一態様において、前記凹凸部の凸部と凹部は、それぞれ平面視で三角形状に形成されていてもよい。
以下の説明では、放熱モジュールの一実施形態として薄型のベーパーチャンバーを例示する。
ベーパーチャンバー1は、作動流体の潜熱を利用する熱輸送素子である。このベーパーチャンバー1は、図1に示すように、作動流体を内部に封入したコンテナ2と、コンテナ2の内部に配置されたウィック3と、を有する。
複数のウィック枝部20は、蒸発部4において、蒸気流路17(空間)を挟んで互いに対向する対向部23を有する。具体的に、蒸発部4には、第1ウィック枝部20aと第2ウィック枝部20bとが対向する対向部23abと、第2ウィック枝部20bと第3ウィック枝部20cとが対向する対向部23bcと、第3ウィック枝部20cと第4ウィック枝部20dとが対向する対向部23cdと、第4ウィック枝部20dと第1ウィック枝部20aとが対向する対向部23daと、が設けられている。これらの対向部23には、凹凸部30が形成されている。
図3に示すように、対向部23abには、凹凸部30が形成されている。本実施形態の凹凸部30は、第2ウィック枝部20bに対向する第1ウィック枝部20aの対向部23aと、第1ウィック枝部20aに対向する第2ウィック枝部20bの対向部23bの両方に形成されている。
ベーパーチャンバー1は、熱源100で生じた熱を受け取ることによって、蒸発部4内の作動液が蒸発する。蒸発部4では、ウィック3に浸透している作動液が蒸発する。蒸発部4で生じた蒸気は、蒸発部4よりも圧力および温度が低い凝縮部5へ向けて蒸気流路17内を流動する。ウィック3は、図2に示すように、接続面16と隙間をあけて配置されていているため、蒸気はウィック3の側面3aに沿って流動することができる。
なお、本実施形態では、蒸発部4のみに対向部23が設けられている。なお、対向部23の位置は蒸発部4のみに限定されない。
図4は、本実施形態に係る対向部23の変形例の拡大図である。
図4に示すウィック3Aには、凹凸部30の凸部31の先端に、第2の凹凸部30aが形成されている。第2の凹凸部30aは、凹凸部30の凸部31の先端に、カッター等によって複数の切れ込みを入れることで形成されている。第2の凹凸部30aは、凸部31a及び凹部32aを有し、凸部31aはブラシの毛のように蒸気流路17に向かって広がっている。
ベーパーチャンバー1の性能を評価するため、図5に示すような試験装置を作成した。
この試験装置では、ベーパーチャンバー1の一方の板面(例えば裏面)に熱源100(ヒーターセンサー)を取り付け、ベーパーチャンバー1の他方の板面(例えば表面)に複数の温度センサーT1~7を取り付けた構成になっている。蒸発部4の温度は、熱源100であるヒーターセンサーで測定し、凝縮部5の温度は、複数の温度センサーT1~7で測定し、ベーパーチャンバー1の性能を熱抵抗によって評価した。
入熱量は、熱源100が電気ヒーターの場合、電力量である。温度Thは、熱源100からの入熱量が、ベーパーチャンバー1を通じた放熱量と釣り合い、平衡に達した状態において測定する。なお、ベーパーチャンバー1の熱輸送能力が高いほど、熱抵抗は小さくなる。
また、図8Bに示す変形例に係るウィック3C1は、対向部23abの一方(例えば、対向部23a)には凹凸部30が形成されておらず、対向部23abの他方(例えば、対向部23b)には凹凸部30が形成されている。
図9Bに示す変形例に係るウィック3Eは、角部が丸まった凹凸部30eを有し、凸部31eと凹部32eが、それぞれ平面視で略矩形状に形成されている。
図9Cに示す変形例に係るウィック3Fは、三角形状の凹凸部30fを有し、凸部31fと凹部32fが、それぞれ平面視で三角形状に形成されている。
また、ウィック部の対向部は、蒸発部4以外の場所に設けられていてもよい。
Claims (10)
- 作動流体を内部に封入し、該封入した作動流体を蒸発させる蒸発部と、該蒸発した作動流体を凝縮させる凝縮部と、を有するコンテナと、 前記コンテナの内部に配置され、毛細管力によって前記凝縮した作動流体を前記凝縮部から前記蒸発部に移動させるウィックと、を備え、
前記ウィックは、前記凝縮部から前記蒸発部に至る複数の液体流路を形成する複数のウィック部を有し、
前記複数のウィック部は、前記作動流体の蒸気流路を挟んで互いに対向する対向部を有し、
前記対向部の少なくともいずれか一方に、凹凸部が形成されている放熱モジュール。 - 前記対向部は、前記蒸発部のみに設けられている請求項1に記載の放熱モジュール。
- 前記対向部の両方に、前記凹凸部が形成され、前記対向部の両方に形成された前記凹凸部において、前記対向部の一方に形成された凸部が、前記対向部の他方に形成された凹部に対向するように設けられている請求項1または2に記載の放熱モジュール。
- 前記蒸発部において全ての蒸気流路は繋がっている請求項1~3のいずれか一項に記載の放熱モジュール。
- 前記凹凸部の凸部の先端に、第2の凹凸部が形成されている請求項1~4のいずれか一項に記載の放熱モジュール。
- 前記複数のウィック部の間に柱部を有する請求項1~5のいずれか一項に記載の放熱モジュール。
- 前記柱部の側面が平坦であり、前記ウィックの前記柱部の側面に対向する面に前記凹凸部が形成されている請求項6に記載の放熱モジュール。
- 前記凹凸部は、前記対向部および前記対向部以外で前記蒸気流路に面する前記ウィックの側面の全体に形成されている請求項1~7のいずれか一項に記載の放熱モジュール。
- 前記対向部は、前記凝縮部に設けられていない請求項1~8のいずれか一項に記載の放熱モジュール。
- 前記凹凸部の凸部と凹部は、それぞれ平面視で三角形状に形成されている請求項1~9のいずれか一項に記載の放熱モジュール。
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US16/470,070 US20200080791A1 (en) | 2016-12-20 | 2017-12-14 | Heat dissipation module |
CN201780077550.5A CN110088557A (zh) | 2016-12-20 | 2017-12-14 | 散热模块 |
KR1020197014727A KR20190071783A (ko) | 2016-12-20 | 2017-12-14 | 방열 모듈 |
JP2018557721A JPWO2018116951A1 (ja) | 2016-12-20 | 2017-12-14 | 放熱モジュール |
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