JP2003194485A - Evaporator, loop heat pipe with built-in reservoir, and heat transport method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a loop heat pipe with a built-in reservoir that can maintain and improve heat transport performance with easy constitution by suppressing the rise of vapor temperature in the reservoir. <P>SOLUTION: This loop heat pipe 14 with the built-in reservoir comprises an evaporator 15 and a condenser 4; a liquid pipe 6 and a steam pipe 5 connecting the evaporator 15 and condenser 4; an operating fluid 2 whose phase changes; and the reservoir 10 for storing the operating fluid 2 in the evaporator 15. A bayonet tube 17 is arranged offset in an anti-gravity direction. The bayonet tube 17 is thereby exposed into operating fluid vapor 2a in the reservoir 10 even if the heat transport quantity is increased under gravity. As a result, the heat conductance of the operating fluid vapor 2a in the reservoir 10 and inflow operating fluid 2b can be maintained as it is large, and the temperature rise of the operating fluid vapor 2a in the reservoir 10 can be suppressed, so that a large quantity of heat can be transported with small temperature difference between the evaporator 15 and the condenser 4. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an evaporator having a structure in which a wick for sucking a working fluid by its capillary force and a reservoir for storing the working fluid are housed inside an evaporator container, and a reservoir using this evaporator. The present invention relates to a built-in loop heat pipe and a method for transferring heat from an evaporator to a condenser in the reservoir built-in loop heat pipe.

[0002]

2. Description of the Related Art Conventionally, heat generated from an electronic device or the like arranged inside a housing is exhausted by a heat transfer by forced convection that circulates air inside and outside the housing by using a fan or the like. If it is necessary to place the housing in a place where the environment (for example, air) is dirty (including dust) or in a place where internal and external air circulation is not possible, store the electronic device in a sealed housing and circulate the air. It is necessary to exhaust heat by other methods. Similarly, in an artificial satellite or the like used in outer space, it is necessary to exhaust heat from electronic devices inside the satellite by a method other than air circulation. As a device that discharges heat without air circulation by a fan or the like in response to such a demand, there is a loop heat pipe with a built-in reservoir, for example.

FIGS. 18A and 18B show a schematic structure of a conventional loop heat pipe 1 with a built-in reservoir. In the figure, the heating source is, for example, an electronic device (not shown) housed in a closed casing (not shown), and the heat absorption source is, for example, outside air surrounding the sealed casing. The loop heat pipe 1 with a built-in reservoir transfers heat using a working fluid 2 that undergoes a mutual phase change between a gas phase and a liquid phase by exchanging heat, and is roughly classified to absorb heat from a heating source. Evaporator 3, condenser 4 that radiates heat absorbed by the evaporator 3 to a heat absorption source (for example, outside air), steam pipe 5 that guides the working fluid vapor 2a that has changed to the vapor phase in the evaporator 3 to the condenser 4, condensation It is composed of a liquid pipe 6 that circulates the working fluid liquid 2b that has changed to a liquid phase by radiating heat in the container 4 to the evaporator 3.

The working fluid 2 circulating in the loop heat pipe 1 with a built-in reservoir is a tubular evaporator container 7 of the evaporator 3.
The wick 8 having a hollow cylindrical shape with a bottom and a porous structure disposed inside the wick moves by using a capillary force generated by the wick 8. As shown in FIG. 18 (b), the wick 8 has a plurality of groove grooves (steam passages 9) on its surface, and the ridge portions 8 a (non-groove portions) are in close contact with the inner wall surface of the evaporator container 7. , Receives heat from a heating source. The wick 8 is made of, for example, polyethylene thermoplastic having uniform pores having a pore diameter of several μm, and the working fluid 2b easily permeates and is guided to the inner wall surface side of the evaporator container 7.
Further, inside the wick 8, a reservoir 10 is formed as a space for storing the working fluid 2 inside the evaporator container 7. It should be noted that, so that the working fluid 2b permeates the entire wick 8 and also when used under zero gravity,
Make sure that the working fluid 2b penetrates the wick 8,
A concave secondary wick 11 that causes a capillary phenomenon is also formed on the inner peripheral surface of the wick 8. Then, the working fluid liquid 2b that circulates through the liquid pipe 6 passes through the liquid introduction pipe (bayonet pipe) 12 arranged on the central axis of the evaporator 3 and is returned to the reservoir 10.

Next, the operation of the loop heat pipe 1 with a built-in reservoir will be described. The heat applied from the heating source to the evaporator container 7 is transferred to the ridge 8a of the wick 8 which is in contact with the evaporator container 7 by heat conduction, and the working fluid liquid 2b permeating to the outer peripheral side of the wick 8 is introduced. Are vaporized to change their phases to working fluid vapor 2a. Then, the phase-changed working fluid vapor 2 a passes through the vapor passage 9 formed on the surface of the wick 8, flows into the vapor pipe 5, and further reaches the condenser 4.

The working fluid vapor 2a is condensed while passing through the inside of the condenser 4 and radiates latent heat to the heat absorbing source. The working fluid 2b in the liquid phase flows through the liquid pipe 6 using the capillary force of the wick 8 as a driving force, passes through the bayonet pipe 12 and the reservoir 1
It flows into 0. The working fluid 2b in the reservoir 10 directly flows back to the wick 8 under gravity, and returns to the wick 8 via the secondary wick 11 under zero gravity. This cycle transfers heat from the evaporator 3 to the condenser 4.

In the loop heat pipe 1 with a built-in reservoir, the working fluid circulates with a phase change between the two phases in this manner, whereby heat is transferred. Generally, the endothermic source is, for example, outside air or outer space, and its temperature is fixed, while the electronic device or the like serving as the heating source has a temperature range in which its functional performance can be exhibited. That is, how much heat can be transported from the heat source to the heat sink with a small temperature difference is an index of the heat transport performance of the loop heat pipe 1 with a built-in reservoir.

Here, the evaporator 3 which is thermally coupled to the heating source
It is known that the temperature difference between the condenser 4 and the condenser 4 that is thermally coupled to the heat absorption source largely depends on the temperature of the reservoir 10.
The temperature of the reservoir 10 mainly depends on the amount of heat leak flowing into the reservoir 10 due to the heat conduction of the wick 8, the heat conductance (heat transfer coefficient) between the wick 8 and the working fluid vapor 2a in the reservoir 10, and the working fluid in the reservoir 10. It is determined by the ratio of thermal conductance between the vapor 2a and the working fluid liquid 2b flowing into the reservoir 10. That is, in order to reduce the temperature of the reservoir 10, the amount of heat leak is reduced, or the thermal conductance between the wick 8 and the working fluid vapor 2 a in the reservoir 10 and the working fluid vapor 2 in the reservoir 10 are reduced.
It is necessary to reduce the ratio of thermal conductance between a and the working fluid 2b flowing into the reservoir 10 or to achieve both of them.

In the conventional loop heat pipe 1 with a built-in reservoir, a working fluid vapor 2a in the reservoir 10 and a working fluid liquid 2b flowing into the reservoir 10 through a bayonet pipe 12.
By increasing the thermal conductance between them, the temperature rise of the working fluid vapor 2a in the reservoir 10 is suppressed, and the temperature difference between the evaporator 3 and the condenser 4 is reduced.

[0010]

As shown in FIGS. 18 (a) and 18 (b), the loop heat pipe 1 with a built-in reservoir has the following structure.
Under gravity, the liquid condensed through the bayonet tube 12 falls into the working fluid liquid 2b pool due to gravity. However, under zero gravity, as shown in FIGS. 19 (a), 19 (b), and 19 (c), the condensate is thick film 1 around the bayonet tube 12.
3 is formed. As shown in FIGS. 19D and 19E, under gravity, the vapor region in the condenser 4 increases as the amount of heat transport increases, and the working fluid liquid 2b in the liquid pipe 6 is pushed out. In this case, the amount of the working fluid liquid 2b in the reservoir 10 increases, the bayonet tube 12 is buried in the working fluid liquid 2b, and the phenomenon that the working fluid vapor 2a does not contact occurs.

As a result, the heat exchange between the working fluid liquid 2b in the bayonet tube 12 having the lowest temperature and the working fluid vapor 2a in the reservoir 10 is hindered. As a result, the reservoir 10
There is a problem that the thermal conductance between the working fluid vapor 2a therein and the working fluid liquid 2b flowing into the reservoir 10 becomes small, the bayonet tube 12 does not function, and the reservoir temperature rises. Then, the temperature difference between the evaporator 3 and the condenser 4 is increased, and as a result, the heat transport performance is deteriorated. In some cases, the loop heat pipe 1 with a built-in reservoir fails to function.

The present invention has been made in view of the above-mentioned conventional problems, and an object thereof is a reservoir built-in type capable of suppressing an increase in vapor temperature in the reservoir and maintaining and improving heat transport performance with a simple structure. To provide a loop heat pipe.

[0013]

In order to achieve the above object, the present invention provides a wick having a hollow bottomed cylindrical shape and a porous structure having a space which is a reservoir for storing a working fluid therein, An evaporator container for housing the wick is provided so that a vapor passage, which is a gap for fluid vapor flow, is formed between the wick and the inner wall surface of the evaporator container, and the liquid pipe for sucking the working fluid liquid is the evaporator container. A vaporizer that penetrates through and is joined to a wick, and a vapor pipe for delivering a working fluid vapor is in communication with a vapor passage, and a working fluid liquid supplied from a liquid pipe to a reservoir is sucked into the wick by a capillary force. The heat applied to the wick from the heating source through the evaporator container causes the working fluid liquid in the wick to undergo a phase change to working fluid vapor, which is delivered from the wick to the vapor pipe through the vapor passage. In the generator, a heat leak inhibiting member that inhibits a heat leak from the wick inside the reservoir to the working fluid liquid existing inside the reservoir, or promotion of heat transfer between the working fluid liquid supplied to the reservoir and the working fluid vapor inside the reservoir. Members or both shall be provided.

Further, in order to achieve the above object, in the evaporator according to the present invention, the heat transfer promoting member extends in the longitudinal direction within the reservoir, and the working fluid liquid circulating from the liquid pipe is replenished inside the reservoir. It is assumed that the liquid introduction pipe is discharged longitudinally into the reservoir after being longitudinally cut, and is arranged in the reservoir offset from the central axis thereof in a predetermined direction.

In order to achieve the above object, in the evaporator according to the present invention, it is assumed that the liquid introduction pipes arranged in the offset are offset in the antigravity direction.

In order to achieve the above-mentioned object, in the evaporator according to the present invention, the heat transfer promoting member extends in the longitudinal direction inside the reservoir, and the working fluid liquid circulating from the liquid pipe is stored inside the reservoir. Is a liquid introduction pipe that is longitudinally cut and then discharged into the reservoir, and has a wick structure on its outer surface.

Further, in order to achieve the above object, in the evaporator according to the present invention, the heat transfer promoting member extends in the longitudinal direction within the reservoir, and the working fluid liquid circulating from the liquid pipe is stored inside the reservoir. Is a liquid introduction pipe that is longitudinally cut and then discharged into the reservoir, and has a heat absorbing structure on the outer surface of the pipe.

Further, in order to achieve the above object, in the evaporator according to the present invention, the heat leak inhibiting and heat transfer promoting member extends in the longitudinal direction in the reservoir and recirculates from the liquid pipe. A liquid introducing pipe for discharging the liquid to the inside of the reservoir after longitudinally cutting through the inside of the reservoir, and the liquid introducing pipe extends from the open end side for discharging the working fluid liquid to the other end side and surrounds the liquid introducing pipe. , Has a shroud for guiding the discharged working fluid liquid to the other end side.

In order to achieve the above object, in the evaporator according to the present invention, the heat leakage inhibiting and heat transfer promoting member is a liquid introducing pipe having a shroud, and the liquid introducing pipe is folded back in the longitudinal direction. It shall have a structure.

Further, in order to achieve the above-mentioned object, in the evaporator according to the present invention, the folded structure has a double pipe structure.

In order to achieve the above object, in the evaporator according to the present invention, the heat leak inhibiting and heat transfer promoting member is arranged in the reservoir, and the closed end is directed to the wick joint side of the liquid pipe, It is assumed that the shroud has an open end at the other end, and has a structure that guides the working fluid liquid circulating in the reservoir to the open end side along the inner wall of the wick.

In order to achieve the above object, in the evaporator according to the present invention, the shroud has a wick structure on at least the inner peripheral surface.

Further, in order to achieve the above-mentioned object, the present invention operates an evaporator for changing a working fluid liquid heated by a heating source into working fluid vapor and an operating fluid vapor absorbed by a heat absorbing source. A condensate for changing the phase to a fluid liquid, and a vapor pipe for delivering a working fluid vapor from the evaporator to the condenser,
A loop with a built-in reservoir having a wick for supplying the working fluid liquid from the condenser to the evaporator, and a wick for sucking the working fluid liquid by the capillary force inside the evaporator and a reservoir for storing the working fluid therein. In the heat pipe,
The evaporator is the evaporator according to the present invention.

Further, in order to achieve the above object, the present invention operates a working fluid vapor absorbed by a heat absorbing source from an evaporator for changing a working fluid liquid heated by a heating source into a working fluid vapor. A heat transport method in which heat is transported to a condenser that undergoes a phase change to a liquid fluid by sending a working fluid vapor through a steam pipe, and a space as a reservoir in which an evaporator stores a working fluid. And a wick having a hollow bottomed cylindrical and porous structure, and an evaporator container for accommodating the wick so that a steam passage, which is a gap for flowing a working fluid vapor, is formed between the wick and the inner wall surface of the evaporator container. The working fluid liquid, which is supplied to the reservoir from the liquid pipe joined to the wick through the evaporator container and sucked by the wick by the capillary force, is applied to the wick from the heating source through the evaporator container. In the heat transport method for delivering more steam pipe through the phase change is allowed steam path to the working fluid vapor, heat leak into the working fluid that is present from the wick inside the reservoir interferes with heat leakage inhibition member,
Further, it is assumed that the heat transfer promoting member promotes heat transfer between the working fluid liquid and the working fluid vapor in the reservoir, or both.

[0025]

BEST MODE FOR CARRYING OUT THE INVENTION Preferred embodiments of the present invention will be described below with reference to the drawings.

Embodiment 1. 1A and 1B show a loop heat pipe 1 with a built-in reservoir according to the first embodiment.
4 shows a schematic configuration of No. 4. In the figure, the same reference numerals are used for the same members as in the conventional example. In FIG. 1A, the heating source is, for example, an electronic device (not shown) housed in a closed casing (not shown), and the heat absorption source is, for example, outside air surrounding the sealed casing. The loop heat pipe 14 with a built-in reservoir transfers heat using a working fluid 2 that undergoes a mutual phase change between a gas phase and a liquid phase by exchanging heat, and roughly divides and absorbs heat from a heating source. Evaporator 15, condenser 4 that radiates the heat absorbed in evaporator 15 to a heat absorption source (for example, outside air), steam pipe 5 that guides working fluid vapor 2a that has changed to the vapor phase in evaporator 15 to condenser 4, condensation The working fluid liquid 2b that has changed to a liquid phase by radiating heat in the evaporator 4 is evaporated.
It is composed of a liquid pipe 6 which causes free circulation.

The working fluid 2 circulating in the loop heat pipe 14 with a built-in reservoir is a capillary tube generated by the wick 8 having a hollow bottomed cylindrical shape and a porous structure arranged inside the evaporator container 7 of the evaporator 15. Moves with force as driving force. As shown in FIG. 1 (b), the wick 8 has a plurality of groove grooves (steam passages 9) on its surface, and the ridge portions 8 a (non-groove portions) are in close contact with the inner wall surface of the evaporation container 7, It is designed to receive heat from a heating source. The wick 8 is, for example, a polyethylene thermoplastic having uniform pores having a pore diameter of several μm, and the working fluid 2b is easily permeated and guided to the inner wall surface side of the evaporator container 7. Further, inside the wick 8, a reservoir 10 is formed as a space for storing the working fluid 2 inside the evaporation container 7. In addition, a secondary wick 11 having a concave streak that causes a capillary phenomenon is formed on the inner peripheral surface of the wick 8 so that the working fluid 2b penetrates the entire wick 8.

In the first embodiment, the working fluid liquid 2b circulated through the liquid pipe 6 is parallel to the central axis 16 of the evaporator 15, that is, parallel to the center of the reservoir 10 and in a predetermined direction, for example, antigravity. It passes through a liquid introduction pipe (bayonet pipe) 17 which is offset in the direction (direction opposite to gravity) and functions as a heat transfer promotion member, and is returned to the reservoir 10 from its end 17a.

Next, the operation of the loop heat pipe 14 with a built-in reservoir will be described. From the heating source to the evaporator container 7
The heat applied to the wick 8 is transferred to the ridge 8a of the wick 8 that is in contact with the evaporator container 7 by heat conduction, and the working fluid liquid 2b that has permeated to the outer peripheral side of the wick 8 is evaporated and the working fluid is The phase is changed to steam 2a. Then, the working fluid vapor 2 a passes through the vapor passage 9 formed on the surface of the wick 8, flows into the vapor pipe 5, and further reaches the condenser 4.

The working fluid vapor 2a is condensed while passing through the inside of the condenser 4 and releases latent heat to the heat absorbing source. The working fluid liquid 2b in the liquid phase flows through the liquid pipe 6 using the capillary force of the wick 8 as a driving force, and flows into the reservoir 10 through the bayonet pipe 17. The working fluid liquid 2b in the reservoir 10 is
Under gravity, it directly returns to the wick 8. This cycle transfers heat from the evaporator 15 to the condenser 4.

In the first embodiment, the bayonet tube 1
Since 7 is offset in the antigravity direction, even if the heat transport amount increases, the occupation rate of the working fluid vapor 2a in the condenser 4 increases, and the working fluid liquid 2b amount in the reservoir 10 increases, the bayonet The pipe 17 can be located in the working fluid vapor 2a in the reservoir 10 without being buried in the working fluid liquid 2b, and can be constantly in contact with the working fluid vapor 2a. As a result, the working fluid liquid 2b in the bayonet pipe 17 having the lowest temperature and the working fluid vapor 2a in the reservoir 10 can be sufficiently heat-exchanged, and the working fluid vapor 2a in the reservoir 10 and the bayonet pipe 17 can be exchanged.
(Working fluid liquid 2 flowing through the bayonet pipe 17
It is possible to keep the thermal conductance of b) large. That is, the thermal conductance of the working fluid vapor 2 a in the wick 8 and the reservoir 10 and the working fluid vapor 2 a in the reservoir 10 and the working fluid liquid 2 flowing into the reservoir 10.
It is possible to reduce the ratio of the thermal conductance between b, and it is possible to keep the vapor temperature in the reservoir 10 low at all times. As a result, a large amount of heat can be transferred with a small temperature difference between the evaporator 15 and the condenser 4. In addition, the offset amount of the bayonet tube 17 depends on the reservoir 1
It is preferable that the maximum amount of the working fluid liquid 2b that recirculates within 0 be calculated in advance and that the bayonet pipe 17 be set at a position where the bayonet pipe 17 is not buried in the working fluid liquid 2b even during the maximum recirculation.

As described above, according to the configuration of the first embodiment, the evaporator 15 can be heated under gravity even if the heat transport amount increases.
It is possible to continuously carry a large amount of heat with a simple structure without significantly increasing the temperature.

Embodiment 2. FIGS. 2A to 2C show a schematic structure of an evaporator 18 of a loop heat pipe with a built-in reservoir capable of excellent heat transport when used under zero gravity. The portion other than the evaporator 18, that is,
The configurations of the condenser 4, the steam pipe 5, and the liquid pipe 6 are the same as those in the first embodiment, and their illustration is omitted. In addition, in FIG. 2, the same members as those in FIG.

The bayonet tube 19 of the evaporator 18 of the second embodiment has a wick 20 (concavo-convex formed in the circumferential direction of the bayonet tube 19) for generating a capillary force on its outer wall surface. In the second embodiment, the bayonet tube 19 is arranged on the central axis of the evaporator 18 as in the prior art.

The working fluid liquid 2 circulated into the reservoir 10 from the end portion 19a of the bayonet tube 19 under zero gravity.
b mainly gathers in the end of the reservoir 10 in a lump. At this time, the wick 20 provided outside the bayonet tube 19
The working fluid liquid 2b condensed in the bayonet tube 19 by
Communicates with the working fluid 2b in the reservoir 10. Therefore, the working fluid 2b becomes a substantially constant thin film 21 around the bayonet tube 19 even under zero gravity. In other words, the wick 20 prevents a thick film from being formed around the bayonet tube 19, and sufficiently exchanges heat between the working fluid 2b in the bayonet tube 19 having the lowest temperature and the vapor in the reservoir 10. It is possible. As a result, the working fluid vapor 2a and the bayonet tube 19 (the bayonet tube 1
It is possible to prevent a decrease in the thermal conductance of the working fluid 2b) flowing in via 9. As a result, the thermal conductance between the wick 8 and the working fluid vapor 2a in the reservoir 10 and the working fluid vapor 2a in the reservoir 10 and the reservoir 1
It is possible to reduce the ratio of the thermal conductance between the working fluid liquids 2b flowing into zero. That is, the reservoir 10
The internal steam temperature can always be kept low. As a result, a large amount of heat can be transported with a small temperature difference between the evaporator 18 and the condenser 4.

Embodiment 3. FIGS. 3A to 3C show a schematic structure of another evaporator 22 of a loop heat pipe with a built-in reservoir capable of excellent heat transport when used under zero gravity. The configuration other than the evaporator 22, that is, the configuration of the condenser 4, the steam pipe 5, and the liquid pipe 6 is the same as in the first and second embodiments, and the illustration thereof is omitted. Further, in FIG. 3, the same members as those in FIGS. 1 and 2 are designated by the same reference numerals.

The bayonet tube 23 of the evaporator 22 of the third embodiment is provided with two plate-shaped heat absorbing fins 24 on its outer wall surface at, for example, opposing positions. In addition, in the third embodiment, the arrangement position of the bayonet tube 23 is on the central axis of the evaporator 22 as in the prior art.

The working fluid liquid 2b which circulates from the end portion 23a of the bayonet tube 23 into the reservoir 10 is mainly collected at the end portion of the reservoir 10 and the working fluid vapor 2a is located near the center. At this time, by providing the heat absorbing fins 24 on the outside of the bayonet tube 23, as shown in FIG.
A large contact area between the working fluid vapor 2a and the bayonet pipe 23 can be secured. As a result, the working fluid vapor 2a
It is possible to increase the thermal conductance between the bayonet tube 23 (the working fluid liquid 2b flowing through the bayonet tube 23). Further, as is apparent from FIG. 3C, since the joint between the heat absorbing fins 24 and the bayonet tube 23 fulfills the function of a wick, the film 25 formed around the bayonet tube 23 is thin and uniform even under zero gravity. Therefore, the working fluid liquid 2b can be prevented from hindering the heat exchange between the working fluid vapor 2a and the bayonet tube 23.

By thus forming the heat absorbing fins 24 in the bayonet tube 23, it is possible to sufficiently perform heat exchange between the working fluid 2b in the bayonet tube 23 having the lowest temperature and the vapor in the reservoir 10. Become, wick 8
It is possible to reduce the ratio of the thermal conductance between the working fluid vapor 2a in the reservoir 10 and the working fluid vapor 2a in the reservoir 10 to the working fluid liquid 2b flowing into the reservoir 10, so that the ratio in the reservoir 10 The steam temperature can always be kept low. As a result, a large amount of heat can be transferred with a small temperature difference between the evaporator 22 and the condenser 4. Although the size of the heat absorbing fins 24 is arbitrary, the film of the working fluid 2b formed around the bayonet tube 23 may become too thick, so
It is desirable to set in consideration of the balance with the heat absorption efficiency.

Further, FIGS. 4A to 4C show schematic configuration diagrams of an evaporator 27 having another bayonet tube 26 for increasing the heat absorption effect. In this configuration, the bayonet pipe 26 that circulates the working fluid liquid 2b from the end portion 26a has a coil shape in order to secure a contact area with the working fluid vapor 2a as much as possible. In this way, by increasing the contact area with the working fluid vapor 2a, the thermal conductance of the working fluid vapor 2a and the bayonet pipe 26 (the working fluid liquid 2b flowing through the bayonet pipe 26) can be increased. As a result, it is possible to reduce the above-mentioned thermal conductance ratio, and it is possible to keep the vapor temperature in the reservoir 10 low. Then, the evaporator 27 and the condenser 4
A large temperature transport can be enabled with a small temperature difference between.

Fourth Embodiment 5 (a)-(c),
Thermal conductance between the wick 8 and the working fluid vapor 2a in the reservoir 10 and the working fluid vapor 2a in the reservoir 10
The schematic structure of the evaporator 28 for reducing the heat conductance ratio between the working fluid 2b flowing into the reservoir 10 and the reservoir 10 and reducing the heat leak from the wick 8 to the reservoir 10 is shown. The configuration of the parts other than the evaporator 28 is the same as that of the other embodiments, and the illustration thereof is omitted.
Further, in FIG. 5, the same members as those in the other embodiments in the drawing are designated by the same reference numerals.

In the fourth embodiment, the bayonet tube 2
Reference numeral 9 denotes an end portion (open end side) 29 for discharging the working fluid liquid 2b.
The cylindrical shroud 30 extends from a to the other end side (introduction side to the reservoir 10), surrounds the bayonet tube 29, and guides the working fluid liquid 2b that has recirculated (discharged) to the base side of the bayonet tube 29. There is.

Under zero gravity, the working fluid 2b returned from the bayonet tube 29 into the reservoir 10 flows between the wick 8 and the shroud 30 along the axial direction of the reservoir 10 and collects inside the shroud 30. Therefore, due to the heat conduction effect of the working fluid liquid 2b, the wick 8 and the working fluid vapor 2
The thermal conductance between a can be reduced. That is, the ratio of the thermal conductances described above can be reduced, and the temperature rise of the working fluid vapor 2a in the reservoir 10 can be suppressed.

On the other hand, under gravity, as shown in FIG.
As shown in (b), even when the bayonet tube 29 is buried in the working fluid liquid 2b, the shroud 30 projecting into the working fluid vapor 2a acts as a heat absorbing fin, so that the above-mentioned thermal conductance ratio is reduced. can do.

Under gravity, the temperature of the portion of the working fluid 2b in contact with the wick 8 is high, and the temperature of the portion of the reservoir 10 in contact with the working fluid vapor 2a is low. As a result, the working fluid liquid 2 having a small liquid density near the wick 8
Buoyancy is generated in b and rises to the upper portion, that is, toward the liquid / vapor interface. Then, natural convection occurs due to the temperature difference in which the working fluid liquid 2b, which has been cooled and increased in density, descends to the lower portion, that is, the wick 8 side. That is, in this flow, heat is transported from the vicinity of the wick 8 to the liquid / vapor interface, that is, to the working fluid vapor 2a in the reservoir 10, which causes a temperature rise due to heat leakage. However, in the present embodiment, since the shroud 30 is arranged substantially perpendicular to this flow, it functions as a heat leak inhibiting member that acts as a baffle that inhibits natural convection, and the wick 8 and the reservoir It is possible to suppress the heat leak to 10.

Since the vapor temperature in the reservoir 10 can be kept low by forming the shroud 30 in this manner, a large amount of heat can be transported with a small temperature difference between the evaporator 28 and the condenser 4. be able to.

Embodiment 5. 7 (a)-(c),
Working fluid vapor 2 in bayonet tube 31 and reservoir 10
As in the example of FIG. 4, by increasing the contact length with a, the schematic configuration of the evaporator 32 that can increase the heat absorption effect of the bayonet tube 31 is shown. As shown in the figure, the bayonet tube 31 has a double pipe structure. That is, the working fluid liquid 2b that has passed through the liquid pipe 6 (see FIG. 1) passes through the inner pipe 31a of the bayonet pipe 31, then passes through the outer pipe 31b, and accumulates in the vicinity of the end 31c, and further the end of the shroud 33. Moves in the axial direction of the reservoir 10 and is pushed into the shroud 33. That is, the working fluid liquid 2b having a low temperature can come into contact with the working fluid vapor 2a inside the shroud 33 when passing through the inner pipe 31a and the outer pipe 31b, and thus the working fluid vapor 2a.
It becomes possible to increase the thermal conductance between the bayonet pipe 31 (the working fluid liquid 2b flowing through the bayonet pipe 31), reduce the ratio of the thermal conductance, and keep the vapor temperature in the reservoir 10 low. You can As a result, a large amount of heat can be transported with a small temperature difference between the evaporator 32 and the condenser 4.

8 (a) to 8 (c), the contact length between the bayonet tube 34 and the working fluid vapor 2a in the reservoir 10 can be made large, and the bayonet tube 34 is shown.
Another evaporator 3 that can increase the heat absorption effect of
The schematic structure of 5 is shown. As shown in the figure, the bayonet pipe 34 is a U-shaped pipe formed by folding back the pipe.
It has a character tube shape. Also in this case, the liquid pipe 6 (see FIG. 1)
The working fluid liquid 2b that has passed through the passage passes through the outward pipe 34a of the bayonet pipe 34, then passes through the return pipe 34b, and ends 3
It accumulates near 4c, further moves from the end of the shroud 36 in the axial direction of the reservoir 10, and is pushed into the shroud 36. That is, when the working fluid 2b having a low temperature passes through the outward pipe 34a and the return pipe 34b, the shroud 36
It becomes possible to contact the working fluid vapor 2a inside,
It is possible to increase the thermal conductance between the working fluid vapor 2a and the bayonet pipe 34 (the working fluid liquid 2b flowing through the bayonet pipe 34), reduce the ratio of the thermal conductance, and reduce the steam temperature in the reservoir 10. Can be kept low. As a result, a large amount of heat can be transported with a small temperature difference between the evaporator 35 and the condenser 4.

Sixth Embodiment 9 (a)-(c),
The schematic structure of the evaporator 37 according to the sixth embodiment is shown. The sixth embodiment shows an example of the evaporator in which the thermal conductance is reduced while simplifying the structure. The evaporator 37 uses, for example, a shroud 38 while omitting the bayonet tubes 29, 31, 34, etc.,
The temperature inside the reservoir 10 can be sufficiently suppressed. 9 (a) to 9 (c) show the case where the device is used under zero gravity. In this example, the liquid pipe 6 is connected to the evaporator container 7 of the evaporator 37, from which the working fluid liquid 2b circulates directly into the reservoir 10. Here, the shroud 38 has a tubular shape having a closed end 38 a on one side and an open end 38 b on the other side, and is arranged so that the closed end 38 a faces the liquid pipe 6. As a result, the working fluid liquid 2b that has recirculated into the reservoir 10 flows between the wick 8 and the shroud 38 in the reservoir 10 and the shroud 3
8 flows inward from the open end 38b side. According to this structure, the working fluid vapor 2a in the reservoir 10 can come into contact with the working fluid liquid 2b having a low temperature via the shroud 38, and is cooled by heat exchange. That is, the shroud 38 performs the same function of cooling the working fluid vapor 2a as the bayonet pipe 34 and the like. Therefore, bayonet tube 3
Even if 4 and the like are omitted, the thermal conductances of the working fluid vapor 2a and the working fluid liquid 2b are maintained at a large level, and the wick 8 and the working fluid vapor 2a are substantially the same as in the structures shown in the above-described respective embodiments. Since the structure is not in direct contact, the above-mentioned thermal conductance ratio can be reduced and the vapor temperature in the reservoir 10 can be kept low. As a result, a large amount of heat can be transported with a small temperature difference between the evaporator 37 and the condenser 4.

When the evaporator 37 is used under gravity, as shown in FIGS. 9 (d) and 9 (e), the working fluid liquid 2b flowing back from the liquid pipe 6 to the reservoir 10 is in the direction of gravity, that is, the reservoir. Collect under 10 At this time, shroud 3
A part (upper part in the figure) of 8 projects into the working fluid vapor 2 a in the reservoir 10. Therefore, heat can be conducted to the shroud 38 portion buried in the working fluid 2b having a low temperature, the thermal conductance between the working fluid vapor 2a and the working fluid 2b can be kept large, and the ratio of the above-mentioned thermal conductance can be reduced. As a result, the vapor temperature in the reservoir 10 can be kept low. That is, the cooling action similar to that of the configuration shown in FIG. 1 can be performed without using the bayonet tube 34 or the like, and the evaporator 37 can be operated even under gravity.
It is possible to enable a large amount of heat transfer with a small temperature difference between the condenser 4 and the condenser 4.

10 (a) to 10 (c), for example, in the structure shown in FIG. 5, in order to sufficiently supply the working fluid liquid 2b to the wick 8 when the evaporator 28 is used under zero gravity. Shroud 3 with required secondary wick 11
Evaporator 39 is shown which can be omitted by using zero. 10A to 10C and 5A to 5C.
As is clear by comparing (c), in FIG.
Other structures are the same except that the secondary wick 11 shown in FIG. 5B does not exist, and the same members are denoted by the same reference numerals and described.

As shown in the description of FIG. 5, the bayonet pipe 29 extends from the end portion 29a for discharging the working fluid liquid 2b to the other end side, and encloses the bayonet pipe 29 to recirculate the working fluid liquid 2b into the bayonet pipe. It has a cylindrical shroud 30 that leads to the base side of the tube 29. Under weightlessness, the working fluid 2b returned from the bayonet tube 29 into the reservoir 10 forms a narrow space between the wick 40 having no secondary wick and the shroud 30 as shown in FIG. And flows in the shroud 30 and accumulates inside the shroud 30. That is, the working fluid 2b can surely come into contact with the wick 40 while the working fluid 2b collects inside the shroud 30. As a result, the evaporator 4
0 is capable of uniformly supplying the working fluid 2b to the inner wall of the wick 40 without using the capillary force of the secondary wick 11, which simplifies the structure of the wick 40 and is equivalent to that of the other embodiments. The working fluid 2 can be circulated. Of course, shroud 3 at this time
By using 0, the thermal conductance between the wick 8 and the working fluid vapor 2a is reduced, which contributes to reducing the thermal conductance ratio.

Further, FIGS. 11 (a) to 11 (c) show FIG.
In the structure shown in (a) to (c) from which the bayonet tube is omitted, by using the shroud 38, the evaporator 41 in which the secondary wick 11 can also be omitted is shown. It should be noted that FIGS. 11A to 11C and FIGS.
As is clear by comparing (c), in FIG.
Other structures are the same except that the secondary wick 11 shown in FIG. 5B does not exist, and the same members are denoted by the same reference numerals and described.

The way in which the working fluid liquid 2b is circulated from the liquid pipe 6 to the reservoir 10 is the same as that described with reference to FIG. That is, the working fluid liquid 2 b is transferred from the liquid pipe 6 to the reservoir 10.
And flows in the narrow space between the shroud 38 and the wick 40 having no secondary wick in the axial direction of the evaporator 41, and accumulates inside the shroud 38 from the open end 38 b of the shroud 38. That is, the working fluid 2b can surely come into contact with the wick 40 during the process in which the working fluid 2b collects inside the shroud 38. As a result, the evaporator 41 does not use the capillary force of the secondary wick 11 and the working fluid liquid 2 b is applied to the inner wall of the wick 40.
Can be uniformly supplied, the working fluid vapor 2a can be cooled while the structure of the wick 40 is simplified, and the circulation of the working fluid vapor 2a similar to that of the other embodiments can be realized. . As a result, efficient heat transfer can be performed with a simple structure.

Embodiment 7. 12A to 12C show
An example of the evaporator 42 is shown in which the shroud used in each of the above-described embodiments is improved to achieve better circulation of the working fluid 2. The basic structure is shown in FIG.
1 to (c), the same members are designated by the same reference numerals and described.

The bayonet pipe 29 extends from the end portion 29a for discharging the working fluid liquid 2b to the other end side, and surrounds the bayonet pipe 29 and guides the circulating working fluid liquid 2b to the base portion side of the bayonet pipe 29. It has a shroud 43. As is apparent from FIGS. 12B and 12C, the shroud 43 extends in the axial direction of the evaporator 42 at least on the inner peripheral surface (formed on the inner and outer peripheral surfaces in the drawing) of the capillary tube. It has a concave and convex auxiliary wick 43a for generating force. When driving the loop heat pipe with built-in reservoir, the working fluid 2b in the condenser 4
And the working fluid liquid 2 accumulated inside the shroud 43.
Regarding b, it is necessary that the respective liquid amounts change in accordance with the heat transport amount. Inside the shroud 43, the working fluid vapor 2
The presence of a may prevent the working fluid liquid 2b from entering and exiting the inside of the shroud 43. Therefore, in the seventh embodiment, the wick 8 is formed by utilizing the capillary force of the wick 43a on the inner peripheral surface of the shroud 43.
By ensuring the communication between the working fluid liquid 2b between the shroud 43 and the working fluid liquid 2b accumulated inside the shroud 43, the working fluid liquid 2b in the reservoir 10 and the working in the condenser 4 can be operated. This enables a smooth liquid amount distribution of the fluid 2b. As a result, it becomes possible to realize a smooth circulation of the working fluid 2 corresponding to the heat transport amount.

The evaporator 44 shown in FIGS. 13 (a) to 13 (c).
9 (a) to 9 (c) of the sixth embodiment, the shroud 38 is replaced with a shroud 45 with a wick 45a. The relationship between the thermal conductances of the working fluid vapor 2a and the working fluid liquid 2b in the shroud 45 is the same as in FIG.
The supply function and the like of b are the same as those in FIG. As shown in FIG. 12, by using the capillary force of the wick 45 a, the working fluid 2 b between the wick 8 and the shroud 45 and the working fluid 2 b accumulated inside the shroud 45 are reliably connected. By securing the reservoir 1
The working fluid liquid 2b in 0 and the working fluid liquid 2b in the condenser 4 can be smoothly distributed. As a result, it becomes possible to realize smoother circulation of the working fluid 2 in accordance with the heat transport amount. The structure of the wicks 43a and 45a of the shrouds 43 and 45 may be an open artery structure in which the shroud itself is, for example, a mesh.
In this case, as compared with the case where the uneven wick 43a and the like are formed, the manufacturing is easier and the same effect can be obtained.

As described above, by arbitrarily combining the features of the above-described respective embodiments, the respective effects can be sufficiently exhibited and good heat transfer can be contributed.

A part of the combination examples of the respective embodiments will be shown below. 14A to 14C show an evaporator 46 in which the shroud 43 with the wick 43a shown in FIG. 12 and the bayonet tube 23 having the heat absorbing fins 24 shown in FIG. 3 are combined. In this case, the shroud 4 for the working fluid 2b
3 movement, supply of the working fluid 2b to the wick 8,
It is possible to favorably suppress the temperature rise of the working fluid vapor 2a, and it is possible to more efficiently drive the loop heat pipe with a built-in reservoir.

FIGS. 15A to 15C show an evaporator 47 in which a bayonet tube offset as shown in FIG. 1 and a shroud are combined. The bayonet tube 48 of the evaporator 47 is connected to the end 48a of the evaporator 47 at a position offset from the center of the shroud 49, that is, the center of the reservoir 10. In this case, under weightlessness, the bayonet tube 48 is in direct contact with the working fluid vapor 2a located inside the shroud 49, which makes it possible to increase the thermal conductance of the working fluid vapor 2a and the working fluid liquid 2b. The temperature rise of the working fluid vapor 2a is suppressed. on the other hand,
Under gravity, it contacts the working fluid vapor 2a located above the reservoir 10 through the outer wall of the shroud 49, and it is also possible to increase the thermal conductance of the working fluid vapor 2a and the working fluid liquid 2b. The temperature rise of the fluid vapor 2a is suppressed. In this case, since the outer wall of the shroud 49 that contacts the bayonet tube 48 functions as a heat absorbing fin, it is possible to efficiently suppress the temperature rise under gravity.

The evaporator 50 shown in FIGS. 16 (a) to 16 (c).
Is the same as the structure shown in FIG.
This is an example in which the shroud 51 having a is adopted. In this case, in addition to the function of the evaporator 47 of FIG.
Working fluid liquid 2 between wick 8 and shroud 51
b and working fluid liquid 2 accumulated inside the shroud 51
By ensuring the communication of b, the working fluid liquid 2b in the reservoir 10 and the working fluid liquid 2b in the condenser 4 can be smoothly distributed. As a result, it becomes possible to realize smoother circulation of the working fluid 2 in accordance with the heat transport amount.

The evaporator 52 shown in FIGS. 17A to 17C.
Is an example in which the bayonet tube 19 with the wick 20 shown in FIG. 2 is adopted in the structure shown in FIG. in this case,
In addition to the function of the evaporator 42 shown in FIG. 12, the film of the working fluid 2b formed around the bayonet tube 19 has a substantially constant thickness, and the thermal conductance between the working fluid vapor 2a and the bayonet tube 19 is reduced. The effect that can be prevented occurs. As a result, the ratio of the thermal conductance can be reduced, and the temperature rise of the working fluid vapor 2a in the reservoir 10 can be suppressed.

In addition, the bayonet tube 19 with a wick shown in FIG. 2 is arranged offset with respect to the central axis of the reservoir 10, the bayonet tube 23 with a heat absorbing fin 24 shown in FIG. , A combination of them with a bayonet tube having a double pipe structure or a folded structure, a simple type shroud (shown in FIGS. 5 and 9) or a shroud with a wick (shown in FIGS. 12 and 13) By combining a plurality of the characteristic structures shown in each of the above-described embodiments, the effects of each structure can be sufficiently exerted, and it is possible to contribute to the improvement in the heat transport performance of the loop heat pipe with a built-in reservoir. In the thermal design of the loop heat pipe with a built-in reservoir, it is preferable to appropriately select the optimum combination in consideration of the place of use and the like.

[0064]

As described above, according to the evaporator according to the present invention, the heat leak from the wick inside the reservoir to the working fluid existing inside the reservoir is blocked by the heat leak inhibiting member or is supplied to the reservoir. The heat transfer between the working fluid liquid and the working fluid vapor in the reservoir is accelerated by the heat transfer promoting member, or both of them are enabled, so that the temperature rise of the evaporator can be suppressed.

Further, according to the evaporator of the present invention, the liquid introduction pipe for guiding the liquid-phase working fluid (working fluid liquid) circulating from the condenser into the reservoir is provided inside the reservoir in a predetermined direction from the central axis thereof. With the offset arrangement, it is possible to adjust the thermal conductance between the working fluid in the vapor phase (working fluid vapor) in the reservoir and the working fluid in the liquid phase via the liquid introduction pipe. For example, when using the evaporator under gravity,
If the liquid introduction pipe is offset in the anti-gravity direction, the amount of heat transport increases, and even if the amount of the liquid-phase working fluid flowing back to the reservoir increases, the liquid introduction pipe is buried in the liquid-phase working fluid. Without, it is possible to reliably maintain the contact between the gas-phase working fluid and the liquid introduction pipe in the reservoir, and to keep the thermal conductance between the gas-phase working fluid and the liquid-phase working fluid large. As a result, the vapor temperature in the reservoir can be kept low.

Further, according to the evaporator of the present invention, since the outer surface of the liquid introducing pipe has the wick structure, the working fluid in the liquid phase condensed in the liquid introducing pipe is combined with the working fluid in the liquid phase in the reservoir. It becomes possible to communicate with each other, and the film of the working fluid in the liquid phase formed around the liquid introducing pipe can have a substantially constant thickness. Further, it is possible to prevent a decrease in thermal conductance between the vapor-phase working fluid and the liquid-phase working fluid via the liquid introducing pipe. As a result, the vapor temperature in the reservoir can be kept low.

Further, according to the evaporator of the present invention, since the liquid introducing pipe has the heat absorbing structure on the outer surface of the pipe, it is possible to secure a large contact area between the working fluid in the vapor phase and the liquid introducing pipe. As a result, it is possible to increase the thermal conductance between the vapor-phase working fluid and the liquid-phase working fluid via the liquid introducing pipe. As a result, the vapor temperature in the reservoir can be kept low.

Further, according to the evaporator of the present invention, the liquid introduction pipe extends from the open end side for discharging the working fluid in the liquid phase to the other end side thereof, and surrounds the liquid introduction pipe for discharging the liquid phase. By having the shroud for guiding the working fluid to the other end side, the working fluid in the liquid phase returned from the liquid introducing pipe into the reservoir flows between the inner wall of the wick and the shroud. Therefore, the thermal conductance of the liquid-phase working fluid can reduce the thermal conductance between the wick and the vapor-phase working fluid in the reservoir. Furthermore, under gravity, natural convection inside the liquid-phase working fluid in the reservoir can be obstructed, so that heat leakage can be reduced. As a result, the temperature rise of the vapor-phase working fluid in the reservoir can be suppressed.

Further, according to the evaporator of the present invention, the shroud disposed in the reservoir has its closed end directed to the inflow side of the liquid-phase working fluid circulating from the condenser, and has the open end at the other end. By having a shroud that guides the refluxed liquid-phase working fluid to the open end side along the inner wall of the reservoir, the liquid-phase working fluid refluxed in the reservoir flows between the inner wall of the reservoir and the shroud. . Then, the vapor-phase working fluid in the reservoir can come into contact with the low-temperature liquid-phase working fluid via the shroud, and is cooled by heat exchange. Further, under gravity, natural convection inside the liquid-phase working fluid in the reservoir can be obstructed, so that heat leakage can be reduced. As a result, the temperature rise of the vapor-phase working fluid in the reservoir can be suppressed.

Further, according to the evaporator of the present invention, by forming the liquid introducing pipe with a double pipe structure,
By forming a folded structure that is folded back in the longitudinal direction, the contact length between the liquid introduction pipe and the working fluid vapor in the reservoir can be increased, and the heat absorption effect can be increased. As a result, it is possible to increase the thermal conductance with the liquid-phase working fluid flowing in via the liquid introduction pipe.
Then, the temperature rise of the working fluid in the vapor phase in the reservoir can be suppressed.

Further, according to the evaporator of the present invention, by forming the wick at least on the inner peripheral surface of the shroud, the capillary force is generated on the inner peripheral surface of the shroud, and the liquid phase between the wick and the shroud is generated. It is possible to reliably secure the communication between the working fluid and the working fluid in the liquid phase accumulated inside the shroud, and to smoothly change the amount of the working fluid in the reservoir according to the heat transport amount.

Further, according to the loop heat pipe with built-in reservoir according to the present invention, since the evaporator according to the present invention is used, a large amount of heat can be transported with a small temperature difference between the evaporator and the condenser. Therefore, the heat transport performance can be improved.

In the heat transport method according to the present invention, the heat leak from the wick inside the reservoir to the working fluid liquid existing inside the reservoir is inhibited, and between the working fluid liquid and the working fluid vapor inside the reservoir. Since the heat transfer is promoted and both of them are realized, the effect of improving the heat transport performance by suppressing the temperature rise of the evaporator can be obtained by a relatively simple means.

[Brief description of drawings]

FIG. 1 is an explanatory diagram illustrating a schematic configuration of a reservoir built-in loop heat pipe according to a first embodiment of the present invention.

FIG. 2 is an explanatory diagram illustrating a schematic configuration of an evaporator according to a second embodiment of the present invention.

FIG. 3 is an explanatory diagram illustrating a schematic configuration of an evaporator according to a third embodiment of the present invention.

FIG. 4 is an explanatory diagram illustrating another schematic configuration of the evaporator according to the third embodiment of the present invention.

FIG. 5 is an explanatory diagram illustrating a schematic configuration of an evaporator according to a fourth embodiment of the present invention.

FIG. 6 is an explanatory diagram illustrating an operation of an evaporator according to a fourth embodiment of the present invention under gravity.

FIG. 7 is an explanatory diagram illustrating a schematic configuration of an evaporator according to a fifth embodiment of the present invention.

FIG. 8 is an explanatory diagram illustrating another schematic configuration of the evaporator according to the fifth embodiment of the present invention.

FIG. 9 is an explanatory diagram illustrating a schematic configuration of an evaporator according to a sixth embodiment of the present invention.

FIG. 10 is an explanatory diagram illustrating a configuration in which a secondary wick is omitted in the evaporator according to the fourth embodiment of the present invention.

FIG. 11 is an explanatory diagram illustrating a configuration in which a secondary wick is omitted in the evaporator according to the sixth embodiment of the present invention.

FIG. 12 is an explanatory diagram illustrating a schematic configuration using a shroud with a wick in an evaporator according to a fifth embodiment of the present invention.

FIG. 13 is an explanatory diagram illustrating a schematic configuration using a shroud with a wick in the evaporator according to the sixth embodiment of the present invention.

FIG. 14 is an explanatory diagram illustrating an example of a combination of the embodiments according to the present invention.

FIG. 15 is an explanatory diagram illustrating another combination example of the embodiment according to the present invention.

FIG. 16 is an explanatory diagram illustrating another example of a combination of the embodiments according to the present invention.

FIG. 17 is an explanatory diagram illustrating another example of a combination of the embodiments according to the present invention.

FIG. 18 is an explanatory diagram illustrating a schematic configuration of a conventional loop heat pipe with a built-in reservoir.

FIG. 19 is an explanatory diagram illustrating operating states of an evaporator of a conventional loop heat pipe with built-in reservoir under zero gravity and under gravity.

[Explanation of symbols]

2 working fluid, 2a working fluid vapor, 2b working fluid liquid, 4 condenser, 5 vapor pipe, 6 liquid pipe, 7 evaporator container, 8 wick, 9 vapor passage, 10 reservoir, 1
1 Secondary wick, 14 Reservoir built-in loop heat pipe, 15 Evaporator, 16 Central axis, 17 Bayonet tube (liquid introduction tube), 17a End part.

Front page continuation (51) Int.Cl. ⁷ Identification code FI theme code (reference) F28D 15/02 103 F28D 15/02 103Z

Claims (12)

[Claims] 1. A wick having a hollow bottomed cylindrical shape and a porous structure having a space as a reservoir for storing a working fluid therein, and a steam passage which is a gap for flowing a working fluid steam and a wick and an evaporator container. An evaporator container for accommodating the wick so as to be formed between the inner wall surface and the inner wall surface, and a liquid pipe for sucking the working fluid liquid is penetrated through the evaporator container and joined to the wick to deliver the working fluid vapor. An evaporator in which a vapor pipe communicates with a vapor passage, and a working fluid liquid supplied from a liquid pipe to a reservoir is sucked into a wick by a capillary force, and wick is generated by heat applied to a wick from a heating source through an evaporator container. In the evaporator in which the working fluid liquid inside undergoes a phase change to working fluid vapor, and this working fluid vapor is delivered from the wick to the vapor pipe through the vapor passage, from inside the wick to inside the reservoir A heat leak inhibiting member that inhibits a heat leak to the working fluid liquid existing in the reservoir, a heat transfer promoting member between the working fluid liquid supplied to the reservoir and the working fluid vapor in the reservoir, or both. And an evaporator. 2. The heat transfer promoting member is a liquid introduction pipe that extends in the longitudinal direction inside the reservoir and discharges the working fluid liquid circulating from the liquid pipe into the reservoir after longitudinally cutting the inside of the reservoir in the longitudinal direction. The evaporator according to claim 1, wherein the evaporator is offset from the central axis in a predetermined direction inside the reservoir. 3. The liquid introducing pipe arranged offset,
The evaporator according to claim 2, wherein the evaporator is offset in the antigravity direction. 4. The heat transfer promoting member is a liquid introducing pipe that extends in the longitudinal direction inside the reservoir and discharges the working fluid liquid, which circulates from the liquid pipe, longitudinally inside the reservoir and then discharges it into the reservoir. The evaporator according to claim 1, wherein the outer surface of the tube has a wick structure. 5. The heat transfer promoting member is a liquid introducing pipe that extends in the longitudinal direction inside the reservoir and discharges the working fluid liquid circulating from the liquid pipe into the reservoir after longitudinally cutting the inside of the reservoir in the longitudinal direction. The evaporator according to claim 1, wherein the evaporator has an endothermic structure on its outer surface. 6. The member for inhibiting heat leakage and promoting heat transfer,
A liquid introducing pipe that extends in the longitudinal direction inside the reservoir and flows back from the liquid pipe into the reservoir after longitudinally traversing the inside of the reservoir in the longitudinal direction. The liquid introducing pipe discharges the working fluid liquid. The evaporator according to claim 1, further comprising a shroud that extends from the open end side to the other end side, surrounds the liquid introduction pipe, and guides the discharged working fluid liquid to the other end side. 7. The evaporator according to claim 6, wherein the heat leak inhibiting and heat transfer promoting member is a liquid introducing pipe having a shroud, and the liquid introducing pipe has a folded structure in a longitudinal direction. 8. The evaporator according to claim 7, wherein the folded structure has a double pipe structure. 9. The member for inhibiting heat leakage and promoting heat transfer,
A shroud arranged in a reservoir, having a closed end directed to the wick joint side of a liquid pipe and an open end at the other end, which is a structure for guiding the working fluid liquid circulating in the reservoir to the open end side along the inner wall of the wick. The evaporator according to claim 1, wherein: 10. The evaporator according to claim 6, wherein the shroud has a wick structure on at least an inner peripheral surface thereof. 11. An evaporator for changing the phase of working fluid liquid heated by a heating source into working fluid vapor, a condensate for changing the phase of working fluid vapor absorbed by a heat absorbing source into working fluid liquid, and evaporation. A vapor pipe for sending working fluid vapor from the condenser to the condenser, and a liquid pipe for feeding working fluid liquid from the condenser to the evaporator, in which the evaporator has a working fluid liquid by a capillary force. A loop with a built-in reservoir having a wick for sucking in a fluid and a reservoir for storing a working fluid, wherein the evaporator is the evaporator according to any one of claims 1 to 12. heat pipe. 12. From an evaporator, which changes the working fluid liquid heated by a heating source into working fluid vapor, to a condenser, which changes the working fluid vapor absorbed by a heat absorbing source into working fluid liquid. A heat transport method for transporting heat by feeding working fluid vapor through a steam pipe, wherein an evaporator has a hollow bottomed cylindrical and porous structure having a space as a reservoir for storing a working fluid therein. A wick having a wick, and an evaporator container accommodating the wick so that a steam passage, which is a gap for flowing a working fluid vapor, is formed between the wick and the inner wall surface of the evaporator container, and the wick penetrates through the evaporator container. The working fluid liquid supplied to the reservoir from the liquid pipe joined to the wick and sucked by the wick by the capillary force is changed into the working fluid vapor by the heat applied to the wick from the heating source through the evaporator container, and the vapor passage is changed. In the heat transport method of delivering to the steam pipe via the heat leak inhibiting member, the heat leak from the wick to the working fluid liquid existing inside the reservoir is blocked by the heat leak inhibiting member, and A heat transport method characterized by promoting heat transfer between working fluid vapors, or both.