KR101600667B1 - Thin Type Heat Pipe Provided with a Wick Fixed Obliquely - Google Patents

Abstract

The present invention relates to a thin heat pipe having a wick of a staggered structure, comprising: a housing (3) constituting a plate-like outer body thinner than a length or width; A working fluid which is evaporated in an evaporating section of one side of the housing (3) and then is condensed in a condensing section of the other side to transfer heat of the evaporating section to the condensing section; And a wick (5) extending in the longitudinal direction so that the working fluid condensed in the condensing portion is returned to the evaporator, wherein the wick (5) has a flow cross sectional area in the width direction of the working space (S) So that the cross-sectional area of the injection port required for degassing is sufficiently secured, and even when the boiling working fluid is discharged into the liquid-phase lump state It is possible to expect an improvement in the quality and production efficiency of the heat pipe.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a thin type heat pipe having a wick having a stagger structure,

The present invention relates to a heat pipe, and more particularly, to a heat pipe, in which wicks arranged vertically in the housing are arranged alternately so as to collect the working fluid condensed in the condenser to the heat generating portion, The present invention relates to a thin heat pipe having an improved staggered wick.

Generally, the heat flux is tens or hundreds of times larger than that of a high heat conductive metal such as silver, copper, or aluminum. Therefore, the heat pipe has a very wide range of applications, which is useful in various fields such as cooling of a heat part at a specific position such as a CPU of a computer, recovery of exhaust gas heat, collection of geothermal heat or solar heat Is a heat transfer device that is being used.

The heat pipe is made of a gas-tight solid such as stainless steel, copper, or aluminum, and forms a closed space, that is, a housing, in the form of a tube or the like, to contain a working fluid therein. Therefore, when the heat is applied from one side of the housing, the working fluid evaporates in the internal space of the heating part, and the evaporated steam rapidly moves to the other side where the heat is not applied and is condensed so that latent heat of the fluid is condensed It functions to be transported to department. The condensed liquid is returned to the heating section by the capillary force by the wick structure provided inside the housing. Thereafter, the heat transfer cycle is repeated infinitely, so that the heat of the heating section is continuously transferred to the condensation section.

Although the above-described heat pipe operates in a relatively simple structure as compared with other heat transfer devices, the basic factors affecting the heat transfer performance (heat pipe performance), namely, the type of the working fluid, the material and shape of the housing, The material and structure of the wick and the remaining non-condensable gas should be carefully designed and manufactured. In particular, manufacturers of heat pipes can design heat pipes by determining the material, shape, etc. of working fluid, housing, and wick to maximize heat transfer by theoretical approaches such as numerical calculation and simulation. However, if the non-condensable gas can not be shut off or removed in the manufacturing process, the heat pipe is not only deteriorated in thermal performance over time, but also has an extremely short service life.

That is, the non-condensed gas generated in the heat pipe is a major cause of degradation of the heat pipe. This is because the working fluid must be repeatedly evaporated at the high temperature portion and condensed at the low temperature portion to maintain the heat transfer to reach the effective thermal equilibrium. However, the amount of the working fluid evaporated when the noncondensing gas is contained in the working fluid, This is because the amount is relatively reduced and the thermal equilibrium performance is reduced. Also, during operation, the non-condensable gas accumulates at one end of the condenser and gradually becomes blocked, which results in a sudden temperature drop at the interface of the gas and working fluid vapors.

In addition, the heat pipe has an amount of working fluid that can exhibit the optimum performance depending on the operating fluid. Generally, when the fluid volume is maintained to 15 to 55% of the inner volume of the housing with minimizing the non-condensing gas, The heat pipe performance of the pipe is exerted, and when the operating fluid is maintained at 20 to 40%, more preferably 25 to 35%, the best heat pipe performance is exhibited. If there is a working fluid below the applicable range, the amount of gasified vaporized gas in the heating part of the heat pipe is condensed in the condensing part and becomes greater than the amount of the condensed part returned to the heating part, so that the dry- And the operation as a heat pipe is interrupted. In addition, when there is a working fluid over the range, the amount of applied heat for evaporating the fluid in the heating part becomes long. Therefore, it takes a long time for heating, a space for moving the generated steam is insufficient, The steam condensed in the boiler is mixed with the liquid phase before the boiler reaches the heating section, and the heat transfer is not properly performed.

Non-condensable gas can be generated in various ways. First, the housing (or the container) and the working fluid inside the housing responsible for heat transfer are chemically reacted to cause corrosion, thereby changing the characteristics and shape of the original material of the housing and the working fluid, This is one of the causes of the generation of non-condensable gas such as hydrogen and oxygen. The material of the housing may be stainless steel, copper, aluminum, nickel or the like in the case of a heat pipe for room temperature (use temperature range 230 to 500 K). Examples of the working fluid include methanol, ethanol, ammonia, And water can be used. The generation of non-condensable gas by chemical reaction can be fundamentally interrupted if the housing material and working fluid are properly combined. For example, a combination of copper and ammonia or a combination of aluminum and water can not be used because it is an improper combination in which a chemical reaction occurs to generate a non-condensing gas. However, the combination of copper and water, aluminum and acetone, So that the generation of non-condensable gas due to this can be prevented.

Non-condensable gases can also occur in the manufacturing process, regardless of the chemical reaction. Generally, most of the solid material exposed to the air adsorbs nitrogen, oxygen, water, etc. on the surface even when the dust, oil and other dirt are properly removed in a clean state, and the liquid used as the working fluid, Nitrogen and the like may be present in a dissolved state in the liquid, and a fluid such as acetone or ammonia may absorb moisture in the atmosphere. Therefore, factors that may cause non-condensable gases during the process should be removed.

Such a heat pipe is manufactured by a vacuum injection method or a heating deaeration method, which is the core of the removal of the noncondensing gas. According to the heating and degassing process, as shown in FIG. 1, 101 and the working fluid are heated through a pretreatment process to remove non-condensable gas molecules and foreign substances adsorbed or dissolved on the inner surface. Then, a working fluid such as a syringe or the like is injected into the thus prepared housing 103 in an amount greater than the amount of the working fluid when the heat pipe 101 is completed in the optimum condition. Then, a part of the lower end of the housing 103 into which the working fluid is injected is heated by a heating device such as an oil bath 105. Accordingly, as the working fluid in the housing 103 starts to be heated by heating, bubbles such as noncondensing gas are generated in the working fluid and the wall of the housing 103 and in the working fluid, and these bubbles become liquid or gaseous working fluid And is discharged to the outside.

Since the liquid or gaseous working fluid can be discharged to the outside together with the non-condensing gas in the heating / degassing process, the upper end working fluid inlet 109 is quickly sealed by the removable lid 107 after an appropriate time elapses. However, the discharge of the noncondensing gas by one heating is insufficient for sufficiently discharging the noncondensing gas contained in the housing 103 and the fluid. Therefore, the housing 103 sealed with the lid 107 is cooled down by the cooling device such as the cooling bath 111 or the like to liquefy the gas of the working fluid remaining on the upper portion of the housing 103. [ In this process, the non-condensable gas sinks back to the lower end. After a certain period of cooling time has elapsed, one end of the housing 103, which is once again closed, is heated to the boiling point of the working fluid or higher and the inlet 109 is opened to discharge the non-condensed gas again. This process is repeated two to three times, and the heat pipe 101 is completed by compressing or squeezing / welding and sealing the planned position with the pinch in a state where the main inlet 109 is finally closed.

Theoretically, the vapor pressure of the working fluid, which is one atmosphere at the boiling point of the atmospheric pressure condition, continuously rises as the temperature rises. Actually, as the temperature of the housing 103 approaches the boiling point, the liquid or gaseous working fluid expands And the working fluid vapor and the noncondensing gas together with some liquid working fluid flow into the inlet 103 of the housing 103 because the bubbles are irregular and unevenly generated inside the working fluid or at the contact surface of the working fluid and the housing 103. Therefore, .

Thus, the housing injection port 109 is compressed and sealed by a pinch or the like in a state where the housing 103 is blocked by the removable lid 107 immediately after the heating and deaeration. In this case, since the cross- The injection port 109 must be blocked before the discharge through the injection port 109 takes place in earnest. In order to facilitate the sealing (or welding) of the injection port 109 after the fluid injection, an injection pipe or adapter having a size smaller than the diameter of the heat pipe 101 is separately prepared and welded, brazed, The injection port 109 should be made smaller than the original diameter of the housing 103 by a swaging compression process in the case of a circular tube.

Accordingly, since the working fluid in the liquid phase and the gas phase expanded in the housing 103 during heating is discharged to the outside together with the non-condensing gas through the wide inlet 109, it is impossible to selectively remove the non-condensing gas, Not only can the working fluid irregularly rise from the injection port 109 and can not be controlled but also the amount of the working fluid necessary for the heat pipe 101 There is a problem in that it is difficult to match.

In addition, in order to prevent the loss of the working fluid generated by discharging a large amount of the working fluid accompanying the non-condensing gas as described above, it is necessary to limit the time during which the inlet 109 is opened during heating, The non-condensed gas must be discharged by repeating the same heating and cooling process. Therefore, there is a problem in that the process time is lengthened and the productivity is increased in mass production.

2, when the heat pipe 201 is made thin, the specific gravity of the wick 205 in the operating space S of the housing 203 becomes relatively large. Therefore, The gap g of the injection port 217 is significantly narrowed between the protrusions 221 of the wick 205 and the gap between the protrusions 221 is large. When the gap between the grooves 223 is equal to the gap between the grooves 223, the gap between the projections 221 is set to be larger than the gap between the grooves 223 There is a problem in that the heat resistance of the heat pipe 201 is increased by increasing the flow resistance of the working fluid.

3, the upper and lower protrusions 221 are first brought into contact with each other to seal the gap between the injection port 217, i.e., the groove 223 and the groove, in the process of sealing the injection port 217 after the deaeration with a pinch or the like The sealing operation of the injection port 217, which requires rapid degassing after the degassing, is prolonged. Therefore, the amount of fluid loss of the working fluid can not be precisely controlled, thereby deteriorating the quality of the heat pipe 1.

The present invention has been proposed in order to solve the problems of the conventional heat pipe as described above. In the thin heat pipe having a relatively large specific gravity of the working space occupied by the wick in the housing, the wicks formed on the upper and lower surfaces of the housing are staggered , The working fluid heated to the boiling point is discharged in a liquid-state lump state while sufficiently securing the cross-sectional area of the housing injection port so as not to further increase the internal pressure by heating in the degassing operation for removing the condensed gas during the production of the heat pipe It is an object of the present invention to increase the discharge rate of the noncondensing gas at the time of clogging and to reduce the loss rate of the working fluid.

In order to achieve the above object, the present invention provides a flat panel display comprising a pair of flat plates arranged to face each other, and a pair of side walls connecting the opposite ends of the flat plate to form an operating space therein, A housing having a thin plate-like outer body; A working fluid contained in the operating space in a sealed state and evaporated in an evaporating portion of one side of the housing and then condensed in another condensing portion to transfer heat of the evaporating portion to the condensing portion; And a wick formed to face the inner circumferential surface of each flat plate and extending in the longitudinal direction so that the working fluid condensed in the condensing portion returns to the evaporator, A plurality of protrusions protruding from the inner circumferential surface of each of the flat plate bodies in a transverse direction at a predetermined distance in the inner circumferential surface of each of the flat plate bodies; And a plurality of grooves formed between the plurality of projections and forming a path for the working fluid to be condensed in the condensing portion.

In addition, it is preferable that the inner circumferential surfaces of the pair of side walls are inclined in the same direction as the staggered direction of the wick.

The housing has a multi-channel structure that is divided in the width direction by a plurality of partition walls arranged in the working space to form a plurality of channels, wherein the partition wall has its inner peripheral surface inclined in the same direction as the staggered direction of the wicks .

In addition, it is preferable that the gap g of the housing inlet is 0.1 to 0.4 mm.

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In addition, it is preferable that the protrusions or the grooves of the one side of the flat plate and the grooves or the protrusions of the other side of the flat plate corresponding thereto are formed to be engaged with each other when the housing is compressed.

It is preferable that the projection is inclined in the same direction as the inclination direction of the inner surface of the pair of side walls or the partition wall.

It is preferable that each of the projections has a cross-sectional shape selected from a triangle, a quadrangle, a semicircle, or a semi-ellipse.

According to the present invention, since the wicks formed on the upper and lower flat plates of the housing are staggered from each other, the flow cross-sectional area of the flow generated in the width direction in the working space is kept constant, The flow resistance of the working fluid can be largely reduced under the assumption that the cross sectional area of the working fluid is constant, and the cross-sectional area of the injection port required for degassing can be sufficiently ensured while the working fluid heated at the time of degassing boils and discharged into a liquid- .

Therefore, the discharge efficiency of the noncondensing gas due to the deaeration is improved compared to the same cross-sectional area of the injection port, and the loss rate of the working fluid is greatly reduced, so that the quality of the heat pipe can be expected to be improved and the production efficiency can be greatly increased .

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view for explaining a general heat pipe manufacturing process by a heating deaeration technique; Fig.
2 is a transverse front view showing a conventional thin type heat pipe.
Fig. 3 is a transverse front view showing the thin heat pipe of Fig. 2 squeezed by a pinch; Fig.
4 is a cross-sectional perspective view of a thin heat pipe according to one embodiment of the present invention.
5 is a transverse front view of a thin heat pipe according to another embodiment of the present invention.
6 is a transverse front view of a thin heat pipe according to another embodiment of the present invention.
7 is a transverse front view of a thin heat pipe according to another embodiment of the present invention.
Fig. 8 is a transverse front view showing the thin-walled heat pipe shown in Fig. 6 during a process of being compressed by a pinch; Fig.
9 is a transverse front view showing the thin-walled heat pipe shown in Fig. 7 during a process of being compressed by a pinch;

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a thin heat pipe having a staggered wick according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.

The heat pipe of the present invention comprises a housing 3, a working fluid, and a wick 5, as shown by reference numeral 1 in Figs.

4, the housing 3 is a part of the heat pipe 1, and includes a pair of flat plates 11 arranged vertically facing each other in the figure, A pair of sidewalls 13 connecting left and right ends of the flat plate 11, a rear wall connecting the rear ends of the flat plate 11, and a finishing end of the front closed by the pinch after injecting the working fluid, And the flat plate 11 and the side wall 13 together with the rear wall and the finishing end form an operating space S for receiving a working fluid therein. Among them, the flat plate 11 constitutes the heat transfer surface of the heat pipe 1 and has a significantly longer length and / or width than the side wall body 13 and the rear wall which form the thickness of the heat pipe 1 Therefore, the heat pipe 1 is formed in a thin plate shape as a whole. At this time, as the material of the housing 3, stainless steel, copper, aluminum, nickel or the like can be used for a room-temperature heat pipe (use temperature range 230 to 500 K).

In addition, the housing 3 may have a single operation space S enclosed by the flat plate 11, but it is preferable that the housing 3 has a multi-channel structure as shown in FIG. 4 and the like. To this end, the housing 3 is partitioned by a plurality of partitions 15 to form a plurality of channels, each partition 15 having a working space S at a constant distance in the width direction So that each channel has the same shape.

The working fluid is a heat transfer medium which is accommodated in a thin plate-like housing 3 and rapidly transfers the heat applied to the evaporator of the one end of the housing 3 to the condenser of the other end to discharge it to the outside. 4 in the operating space S shown in Fig. Therefore, the working fluid is heated and vaporized by the heat of the heat source adhering to the evaporator, cooled in the condenser, and recovered to the evaporator. At this time, as the working fluid, methanol, ethanol, ammonia, an ethene, a fluorocarbon compound, and water can be used.

The wick 5 is a passage through which the working fluid cooled and condensed in the condensing portion of the housing 3 is returned to the evaporator. The wick 5 is a passage through which the inner surface of the flat plate 11 of the housing 3, And extend in the lengthwise direction from the evaporator formed at one end of the housing 3 extending in the longitudinal direction to the condenser formed at the other end.

The wick 5 may be formed in various shapes. In particular, in the present invention, as shown in FIG. 4 and below, the wicks 5 are formed on the inner circumferential surfaces of the upper and lower flat plates 11 so that they are staggered in the width direction of the housing 3 do. This is so that when the thickness of the thin type heat pipe 1, that is, the height of the working space S is relatively small, the flow cross sectional area of the flow formed in the width direction in the working space S is kept constant by the wick 5 This is closely related to the efficiency of the heat pipe manufacturing process.

That is, the heating deaeration technique, which is related to the gap g of the inlet 3 of the housing 3, is performed by injecting the working fluid into the housing 3 in an amount larger than the final filling amount, And the non-condensing gas generated in the form of bubbles is discharged to the outside together with the liquid or gaseous working fluid. In the process of degassing the non-condensing gas, the discharge of the non-condensing gas The length ratio between the width w and the gap g is a key factor in order to smooth the injection port 17. The larger the aspect ratio is, that is, the square of 2x2, When the aspect ratio is 1, the loss rate of the working fluid is larger than that of the rectangular injection port 17 having the same area but the aspect ratio of 4. This is because as the aspect ratio of the same area decreases, it is difficult to suppress the discharge of the boiling working fluid for liquefaction in the liquid state.

On the other hand, if the aspect ratio of the injection port 17 is too large, the pressure inside the housing 3 for discharging the non-condensing gas or the like must be increased and the working fluid must be continuously heated at a temperature higher than the boiling point. The thickness of the housing 3 is limited.

Accordingly, the heat pipe 1 of the present invention employs a thin housing 3 having a large aspect ratio, that is, a thinner thickness, to increase the aspect ratio of the injection port 17, The wicks 5 are arranged alternately so as to keep the flow cross-sectional area of the flow formed in the width direction in the operating space S constant so that the injection port 17 is provided within a range that can suppress the discharge of the liquid mass of the working fluid And has a maximum cross-sectional area. Therefore, during the degassing operation of the heat pipe 1 for boiling the working fluid, the working fluid heated up to the boiling point in the housing 3 of the present invention is not discharged into the liquid lump state without the internal pressure being greatly increased.

For this purpose, the gap g of the inlet 17 is preferably maintained at 0.1 to 0.4 mm, the inlet 17 having a gap g in this range, while minimizing the loss of the working fluid, And the like. However, if the gap g of the injection port 17 is too small to be less than 0.1 mm, the pressure inside the housing 3 for discharging foreign matter such as non-condensed gas must be high as described above, It is required to be continuously heated at a high temperature, and therefore, the time required for discharging the non-condensable gas becomes longer and the production efficiency is lowered. In addition, when the gap g of the injection port 17 is 0.4 mm or more, the working fluid boils and is lost through the injection port 17 in a lumpy state as well as in the liquid phase, so that the optimal filling amount, (3) it is difficult to retain 28 to 36% of the internal volume, and therefore, the injection port 17 must be shut off before the non-condensed gas or the like is completely discharged.

 In the case of a multi-channel structure, as shown in FIG. 5 and subsequent drawings, the partition 3 and the partition wall 15 are also staggered with the staggered portion of the wick 5, It is preferable to tilt in the same direction. 3, when the side wall member 13 or the partition wall 15 is not inclined in the staggered direction of the wick 5 or inclined in the opposite direction, not shown, This is because unevenness is caused and the flow resistance of the working fluid is increased.

4, the wick 5 includes a plurality of protrusions 21 and a plurality of grooves 23 formed therebetween. The protrusions 21 are formed in the housing 21, And extends along the longitudinal direction of the housing 3 so as to extend along the groove 23 together with the adjacent protrusions 21. The groove 23 is formed in the inner surface of the flat plate 11 of the housing 3 at a predetermined distance in the width direction, Thereby connecting the evaporating portion of the housing 3 and the condensing portion. 5, each of the projections 21 can be inclined in the same direction as the inner peripheral surface of the sidewall 13 or the inclined direction of the partition 15. In this case, the inclined sidewall 13 is inclined, The flow resistance of the working fluid through the wick 5 can be reduced in the same manner as the partition wall 15 or the partition wall 15. Each of the protrusions 21 may have a rectangular or semicircular cross section as shown in Figs. 5 and 6, or may be changed into various shapes such as a triangular shape or a semi-elliptical shape.

As described above, the groove 23 is a moving passage for collecting the working fluid condensed in the condensing portion to the evaporating portion, and is provided between the projection 21 and the projection 21 as shown in Figs. 4 to 9 And is elongated in the lengthwise direction of the housing 3 like the projection 21. The capillary force moves the working fluid condensed in the condenser to the evaporator.

In this case, the wick 5 according to the present invention is not only different in position from each other formed on the upper and lower flat plates 11 as shown in Fig. 4 and below, The protrusions 21 and the grooves 23 corresponding to the upper and lower portions are engaged with each other during the process of pinching the injection port 17 of the housing 3 as shown in FIG. The gap g of the injection port 17 to be sealed through the pinch becomes narrower than when the gap g of the injection port 17 is not engaged and the sealing of the injection port 17 is performed more quickly. The injection amount of the working fluid of the completed heat pipe 1 can be adjusted more precisely.

Now, the operation of the heat pipe 1 according to the preferred embodiment of the present invention will be described as follows.

The thin type heat pipe 1 having the twisted wick of the present invention is installed between the heat generating source and the heat releasing end for discharging the heat of the heat generating source to the heat releasing end. As described above, In the evaporation part, the working fluid is heated and vaporized, thereby depriving the heat of the heat source. The vaporized working fluid moves to the condenser and is deprived of heat by the heat-releasing end in contact with the condenser, and is cooled and condensed. The condensed working fluid is returned to the evaporator through the wick 5 to complete a series of heat transfer cycles. By repeating this cycle indefinitely, the heat of the heat source is continuously discarded at the heat sink.

Particularly, the heat pipe 1 of the present invention employs a thin-walled housing 3 while alternately arranging the wicks 5 in a staggered arrangement so that the flow cross-sectional area of the flow generated in the widthwise direction in the working space S is constant So as to reduce the flow resistance of the working fluid in the working space S including the injection port 17 and to prevent the working fluid in the form of a liquid mass It is possible to prevent it from being discharged. Therefore, the housing 3 prevents the working fluid heated up to the boiling point from being lost to the liquid-like lump state while the inner pressure does not increase greatly during the degassing.

As described above, since the protrusions 21 and the grooves 23 of the upper and lower wicks 5, which are staggered from each other, are engaged with each other even in the process of pinching to seal the injection port 17 after the degassing is completed, The gap g of the injection port 17 to be sealed by the pinch is narrowed and the sealing of the injection port 17 can be performed more quickly while maintaining the maximum cross sectional area of the injection port 17 and therefore the sealing time is reduced, , The injection amount can be controlled more precisely.

1: heat pipe 3: housing
5: wick 11: flat plate
13: side wall 15: partition wall
17: Injection port 21:
23: home S: working space

Claims (8)

And a pair of side walls 13 connecting the opposite side ends of the flat plate 11 and forming an operating space S therein, A housing 3 constituting a plate-like outer body thinner than the housing 3;
A working fluid which is received in the operating space S in a sealed state and which is evaporated in the evaporator at one side of the housing 3 and then is condensed at the other condenser to transfer the heat of the evaporator to the condenser; And
And a wick (5) formed to face each other on the inner circumferential surface of the flat plate (11) and extending in the longitudinal direction so that the working fluid condensed in the condensing portion returns to the evaporator portion,
The wick 5 is disposed on the inner circumferential surface of each of the flat plates 11 so as to be offset from each other in the width direction so as to keep the flow cross sectional area in the width direction of the working space S constant,
The wick (5)
A plurality of protrusions (21) protruding from the inner circumferential surface of each flat plate (11) at a predetermined distance in the width direction; And
And a plurality of grooves (23) formed between the plurality of projections (21) and forming a path for the working fluid to be condensed in the condensing portion. The method according to claim 1,
Wherein the housing (3) has an inner circumferential surface of the pair of side walls (13) inclined in the same direction as the staggered direction of the wick (5). The method of claim 2,
The housing 3 has a multi-channel structure that is divided in the width direction by a plurality of partitions 15 arranged in the operating space S to form a plurality of channels,
Wherein the partition wall (15) has an inner circumferential surface inclined in the same direction as the staggered direction of the wick (5). The method of claim 3,
Wherein the inlet (17) of the housing (3) has a gap (g) of 0.1 to 0.4 mm. delete The method according to claim 1,
The protrusions 21 or the grooves 23 and the grooves 23 or protrusions 21 of the flat plate 11 on the other side of the flat plate 11 on one side are formed by pressing the housing 3 Wherein the wick is formed so as to be engaged with each other. The method of claim 6,
Characterized in that the projections (21) are inclined in the same direction as the inner peripheral surface of the pair of side wall bodies (13) or the inclined direction of the inner peripheral surface of the plurality of partition walls (15) arranged in the working space (S) A thin heat pipe with structural wick. The method of claim 7,
Wherein each of the protrusions (21) has a cross-sectional shape selected from a triangle, a quadrangle, a semicircle, or a semi-ellipse.

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