JP2001317894A - High efficiency multi-channel type loop heat transfer apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a high efficiency multi-channel type loop heat transfer apparatus adapted to spontaneously resume an operation when a load is operated after a complete stop by not needing other devices than a fluid storage container, complicated starting step, controller and pump necessary to start and operate a capillary pumping group. SOLUTION: The heat transfer apparatus transfers a heat while changing a phase of an operating fluid in one loop. The apparatus comprises external OLF fins formed with strips cut to have a collision angle β to a main flowing gas, a fluid supply flat tube inserted with a fluid supply header after forming and assembling a core structure by dividing a liquid capillary pumping and a structure of an evaporating channel for transferring evaporated vapor into multi-channels and having parallel coupled and constituted evaporator and condenser, a vapor tube and a liquid tube coupling between the evaporator and the condenser coupled by a vapor tube and a liquid tube. Thus, a heat transfer expediting effect via a vortex motion and a boundary layer fracture is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high-efficiency multi-channel type loop heat transfer device in which the working fluid inside transfers heat while changing phases in one loop. Each of these flat tubes is used to constitute an evaporating section and a condensing section to renew the channel shape inside each flat tube, facilitating the capillary pumping of the liquid inside the tube and the transfer of evaporated vapor. Not only that, heat pipes occupy a large part of thermal resistance, and the shape of the outer fin part that causes the bottleneck phenomenon of heat transfer is renewed, and the heat transfer promotion effect through eddy motion and boundary layer destruction is improved. The present invention relates to an apparatus having a significantly improved heat transfer capability as compared with a high-performance heat pipe.

[0002]

2. Description of the Related Art In general, heat transfer at two non-adjacent positions includes conduction heat transfer, single phase flow (single phase flow).
se flow) heat transfer, two-phase flow heat transfer, etc., but the conductive heat transfer system, except in very specific cases,
Not used due to considerable weight and expense.

The single-phase flow heat transfer system has a considerably larger heat transfer capability than the conduction heat transfer system. However, single-phase flow heat transfer systems are not suitable where a high degree of reliability is required or maintenance and repair costs are reduced due to the need for external power to drive mechanical devices such as pumps. In addition, the single-phase flow heat transfer system has a disadvantage that a large temperature drop occurs because sensible heat is transmitted by the working fluid, and if this is reduced, the size of the heat exchange unit must be considerably large.

In the two-phase flow heat transfer system, since the heat transfer process is kept almost isothermal and the required mass flow rate is small, the weight per unit volume (specific weight) can be greatly reduced. Developed for

[0005] Heat transfer devices transfer heat from one location to another through evaporation, condensation, and mass flow.

[0006] A loop heat transfer device can be thought of as a thermodynamic cycle in which it completely depletes as pumping energy during one loop. In this thermodynamic cycle, the liquid is pumped into the evaporator by the pressure of the capillary generated by the core structure, and the liquid working fluid that has received sensible heat in the evaporator becomes saturated liquid, and the remaining liquid necessary for evaporation is obtained. It is further heated by the heat and evaporated.

[0007] Evaporation occurs at the liquid / vapor interface at the core of the capillary, causing the volume to expand while the fluid evaporates and the vapor to flow to the condensing section with the lowest vapor pressure. At this time, the pressure difference generated between the evaporator and the condenser is due to the temperature difference between the vapor in the evaporator and the vapor in the condenser, and is a substantial driving force of all the heat transfer devices. .

[0008] The thermal energy transmitted to the working fluid in the evaporator is conveyed to the condenser, where the residual heat is released from the working fluid while the condensing proceeds.

In the liquid tube, the sensible heat is released to the surroundings, the temperature is sufficiently lowered and supercooled to maintain the necessary temperature difference at the liquid / vapor interface in the evaporator.

[0010] Conventional two-phase heat transfer systems include a loop heat pipe (LHP) and a capillary pumping loop (CP).
L), in the loop heat pipe, the evaporating part and the condensing part form a loop in a single channel form, resulting in poor heat transfer efficiency, and the evaporating part has a compensating cavity.
It has a disadvantage that it has a very slow adaptability due to load fluctuations.

In the above-mentioned capillary pumping pin group, the evaporating part and the condensing part form a loop in a multi-channel form and have a very high heat transfer capability, but due to the structural characteristics of the evaporating part, the liquid is transferred to the core structure inside the evaporating part. There is a structural disadvantage that a liquid storage tank that can be supplied and a temperature controller that can control the liquid level are required.

Further, since the loop heat pipe and the capillary pumping pin group have been developed for space use, there is almost no flow outside the pipe, and they have a structure suitable for radiation and radiation, and are used for general industrial use and home use on the ground. Has the disadvantage that the heat transfer efficiency is very low.

Also, the loop heat pipe and the capillary pumping loop heat transfer device, like most heat pipes, are inferior in facilitating the capillary pumping of the liquid inside the tube and the transfer of evaporated vapor. Not important is the heat transfer bottleneck, which accounts for the majority of the thermal resistance due to the low heat transfer coefficient. Therefore, it is necessary to improve the external fin portion so that the bottleneck phenomenon of heat transfer does not occur.

Fins used in conventional heat exchangers include:
Representatively, there are louver fins and offset strip fins (OSF), but the louver fins are known to have the best thermal efficiency up to now. In the first half of the strip, the flow is formed according to the louver angle, the length of the flow becomes longer and the heat transfer efficiency is good, but in the second half the efficiency decreases,
The fin strip is designed to have a collision angle of 90 ° with respect to the main flow, so that there is no swirling flow and there is little heat transfer efficiency due to the longitudinal vortex.

In the offset strip fins, the strip fins are alternately formed to obtain a boundary layer breaking effect utilizing a one-dimensional staggering effect. There is a disadvantage that there is only an offset effect (in one direction) and the heat transfer efficiency is relatively lower than that of the louver fin.

[0016]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and an object thereof is to form an evaporating section by a flat tube installed in parallel with a loop heat pipe,
The evaporation channel inside the flat tube is designed as a multi-channel, and the core in each channel is made of porous material or matrix mat, screen mesh, twisted knitting of fine wire to enable the role of fluid diode at the liquid / vapor interface. Improve the core structure to perform the function of the fluid diode in the heat transfer loop only when a negative temperature gradient is maintained in the liquid layer upstream (in the flow direction) of the boundary surface and the vapor downstream, and on both sides of the evaporator Heat is supplied to the surface and a desired temperature gradient is generated in the evaporating section, so that the loop can be operated in a supercooled state with a low temperature difference. In addition, the steam pipe and the liquid pipe of the loop heat transfer device are separated into two, and the steam pipe is insulated so as to maintain the temperature higher than the liquid pipe, and the liquid working fluid in the condensing part is always liquid by the steam pressure of the steam pipe. By moving in the direction of the tube, a conventional capillary pumping group (cap
fluid storage containers, complex start-up processes, control devices, necessary for starting and running of the oily pumping loop)
It is an object of the present invention to provide a high-efficiency multi-channel loop heat transfer device in which a pump and other devices are not required, and when a thermal load is applied after a complete stop, the operation always starts again spontaneously.

[0017]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems and to solve the above-mentioned problems, the present invention provides a system for transferring heat while changing the phase of a working fluid from one loop. Thus, the present invention relates to a high-efficiency multi-channel loop heat transfer device having a larger heat transfer capacity than a high-performance heat pipe.

Generally, in a heat transfer device, heat transfer is performed by a phase change of an internal heat medium, so that the heat resistance between the evaporating section and the heat medium inside the condensing section is negligibly small. Therefore, the heat resistance of the external gas (air) side accounts for 90% or more of the entire heat resistance, and the performance of the fins determines the performance of the heat transfer device. Due to the small hydraulic diameter and low gas density of such fins, they provide various geometrical changes over a wide flow velocity range and improve heat transfer performance by reducing thermal resistance.

Such a structure with improved heat transfer performance is disclosed in Patent Application 10 (199) filed by the present inventors in Korea.
8) The structure is described in detail in -49932, but this will be briefly described. An oblique louver fin designed to be inclined with respect to the main flowing gas by an impact angle β (−90 ° ≦ β ≦ 90 °).
fin, OLF) and the transverse eddy current (transv
vortex and axial vortex (longit)
Udinal vortex is generated to enhance the heat transfer by increasing the mixing effect of the vortex, and also to improve the heat transfer from the flat tube by colliding the main flow with the flat tube which is the base. In addition, the fin is given a collision angle β and folded, and a three-dimensional (3
The boundary layer where the gas grows through the strip surface of the fins, with the effect of offsetting (in the direction), increasing the length of the flow through the fins, which can be adjusted by the collision angle β, Much more effective than fins, they enhance the heat transfer in the vortex region between the connected strips by periodically breaking and reducing the thickness of the boundary layer. Accordingly, it is possible to provide a heat exchanger having fins having both advantages of the existing offset strip fins and louver fins, and at the same time, adjust the capacity as needed by modularizing and connecting the main body to the socket when manufacturing the heat exchanger. This is the content of the heat exchanger.

The present invention relates to a system in which the content of the above-mentioned application is further improved and applied to a loop heat transfer device having two phases in one loop. Instead of a single circular tube used in the above, several flat tubes connected in parallel are used to configure the evaporating unit and the condensing unit, respectively, and a new channel shape inside each flat tube is proposed. In addition to facilitating the capillary pumping of the liquid inside the tube and the transfer of the evaporated vapor, the shape of the outer fin part, which occupies most of the heat resistance in the heat pipe and causes the bottleneck phenomenon of heat transfer, is newly proposed. This is a high-efficiency multi-channel loop heat transfer device with improved heat transfer promotion effect through eddy motion and boundary layer destruction.

The structure of each of the evaporating section and the condensing section is such that the fluid supply connecting pipe is inserted into each side hole formed on one side face of the header to continuously stack the fluid supply flat tubes. Upper and lower 2 to close and secure the end of
It consists of a heat exchanger support frame installed in two places.

[0022]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing a configuration of an embodiment of the present invention;

FIG. 1a is a schematic front view of the evaporator of the apparatus of the present invention, FIG. 1b is a schematic plan view of the evaporator of the apparatus of the present invention,
FIG. 1c is a schematic bottom view of the evaporator of the apparatus of the present invention, FIG.
Fig. 9b is a schematic front view showing a brazing joint assembly between the steam condensing section and the header of the double row air material heating section of the apparatus of the present invention, Fig. 9b.
Fig. 9c is a schematic plan view showing a brazed joint assembly between the condensing section and the header of the double-row air material heating section of the apparatus of the present invention, and Fig. 9c is a vapor condensation section of the double-row air material heating section of the present apparatus. And a schematic bottom view showing the braze joint assembly between the and the header.

The fluid supply headers 13 are connected and installed so as to be located at both ends.
An inclined louver fin (OLF) formed with a strip cut to provide a cutting edge is provided, and both ends are processed to a cutting angle of 90 °, and at the same time, the processed ends are formed on one side of a fluid supply header. The flat tube 11 for fluid supply inserted and assembled in each side hole, and the flat tube 11 is provided at two upper and lower positions so as to close the end of the header using the end cap 15 and to fix and support the flat tube 11 at the same time. The heat exchanger support frame 21 has a "U" -shaped cross section with one side open, and the size can be adjusted as required by modularizing each part and connecting it to a socket.

In the above, the fin side surface inclination angle γ is −60.
Brazing is performed in a range of ° ≦ γ ≦ 60 ° (see FIG. 5b), and a range of the collision angle β is designed to be inclined in a range of −90 ° ≦ β ≦ 90 ° (see FIG. 6).

In the above, it is desirable to form one line,
Usually, when the size of the condensing part is larger than the evaporating part,
Preferably, it is modified to indicate that it can be expanded to two columns. Reference numeral 16 denotes a fluid inflow pipe (outflow pipe).

FIG. 2A shows the header used in this apparatus, and FIG.
Is a modified header used in the apparatus, FIG. 3a is an assembly view of a brazing joint between the evaporator and the header used in the apparatus,
Fig. 3b is a sectional view of the brazing joint between the evaporating section and the header used in the present apparatus, Fig. 3c is a sectional view showing the lower header and the core of the flat tube connecting section used in the present apparatus, and Fig. 4a is used in the present apparatus. FIG. 4B is a perspective view showing an evaporating portion and an extended surface fin having an H-shaped core for liquid pumping therein, in which there is a groove for removing external condensed water, and FIG. Fig. 5a is a perspective view showing an evaporator having an I-shaped core for liquid pumping and a fin for an extended surface, and Fig. 5a is a cross-sectional view of an evaporator multi-channel flat tube having an internal dividing fin used in the present apparatus. 5b is a side view of the external expansion surface fin brazed to the flat tube used in the present apparatus, FIG.
c is a development view of the extended surface fins of the present apparatus, and FIG. 6 shows the multi-channel flat tubes and brazed fins used in the present apparatus.

The flat tube 11 is inserted into the side hole 19 and brazed 22 is formed. Inside this flat tube,
Multi-channels (FIGS. 7a, 7b, 7c, 7d) of various polygonal shapes such as squares or circles are formed and interconnected, and various cores (17a, 17b) are provided inside each channel. , 17c) are inserted and serve to capillary pump the liquid.

FIG. 3C shows a structure in which the liquid inserted in the core inserted into the flat tube and the lower header is pumped through the core. Outside the flat tube, a central condensed water discharge groove 23 and a double-sided condensed water discharge groove 23a formed at the center and on both sides are formed at the center of the outer surface of the flat tube.

A central condensed water discharge hole 24 is formed at the center of the OLF fin.

A large number of side holes 19 are formed in the header 13, and the surface of the header is coated with a coating material 13a for aluminum welding.

The device of the present invention will be described in more detail. The present invention constitutes a heat transfer device that transmits heat while the phase of a working fluid changes in one loop. A) A connection pipe (header) for fluid (liquid and gas) is connected and installed so as to be located at both ends. An OLF fin having a strip formed by cutting the main flow gas so as to have an impact angle β is provided at an upper portion thereof, and is inserted into each side hole formed on one side surface of the fluid supply header and assembled. A fluid supply flat tube; b) a header for adjusting the number of fluid supply cores arranged in the channels inside the flat tube according to the heat load capacity, adjusting the pressure loss of the steam flow, and simultaneously adjusting and connecting the number thereof; c. The upper portion is inserted into each side hole formed on one side surface of the header of the fluid supply connection pipe to close and support the end of the header of the fluid supply flat tubes stacked vertically continuously. An evaporator, comprising a heat exchanger support frame installed at two lower locations, and a porous plug provided at the lower end to prevent vapor backflow and to function as a fluid diode; and d) substantially the evaporator and the evaporator A condensing section of the same shape but without condensed water discharge grooves outside the flat tube and no core inside the flat tube channel; and e) the outer diameter of the steam pipe of the loop heat transfer device compared to the outer diameter of the heat pipe having the same heat capacity. Can be considerably smaller,
The heat loss of the loop heat transfer device is much smaller than that of the heat pipe, but when the heat loss in the heat insulation part increases, the heat potential decreases, and the heat pipe is sufficiently insulated to reduce the heat loss. F) It is composed of a liquid tube that is sufficiently supercooled so as not to cause boiling at the inlet of the evaporating section, and is connected to each other.

The fluid supply core is a vortex vapor backflow prevention core.

After the heat is released on both sides of the condensing section,
It is condensed and returns to the evaporator bottom header through the liquid pipe (ie, liquid reflux pipe). In this process, a meandering structure in which the degree of supercooling is further reduced by external condensed water is also possible.

The steam pipe and the liquid pipe of the loop heat transfer device are separated into two, the steam pipe is maintained at a higher temperature than the liquid pipe, and the liquid working fluid always moves to the liquid pipe by the vapor pressure of the steam pipe. To

This is a two-phase loop heat transfer device composed of a core that can be spontaneously restarted whenever a thermal load acts even after a complete stop.

In the apparatus of the present invention, the condensing section, the liquid pipe and the vapor pipe have no wick, and only the evaporating section has a wick.

FIG. 7A is a multi-channel flat tube used in this apparatus and its sectional structure, FIG. 7B is a multi-channel flat tube used in this apparatus and its cross-sectional structure, and FIG. 7C is a multi-channel flat used in this apparatus. FIG. 7d shows a multi-channel flat tube and its cross-sectional structure used in the present apparatus, and FIG. 7e shows a backflow prevention fluid diode used in the present apparatus for plugging the lower end of the vapor flow path of the evaporator. .

In the evaporating section, the internal flow path of the flat tube divided by the multi-channel wall 11a of the flat tube for fluid supply and the multi-channel dividing wall (fin) 11b of the flat tube for fluid supply has a capillary pumping core. 17a, 17b,
17c, and the vapor passages 14, 14a, 14b of the evaporating section.
Are formed, a capillary pumping core 17, a vapor-lock prevention interval 17 d, a backflow prevention fluid diode (a vapor backflow prevention plug at the lower end of the evaporator) 17 e.
Is formed.

The capillary pumping core 17 includes an axially twisted knitting core 17a, a core 17b using a porous material,
A core 17c using a mesh is used.

The structure of the axially twisted knitting core 17a can be considered to be such that the center is replaced with a spring by an electric wire composed of a hair braided with several strands or an uncovered twisted wire.

That is, the evaporating section structure inside the flat tube composed of the multiple channels is such that the evaporating portion is formed by flat tubes installed in parallel instead of a single circular tube in the loop heat pipe, and the cross section of the flow channel is circular. , An ellipse, a quadrangle, and a right quadrangle.

Further, the evaporation channel structure inside the flat tube is as follows:
An evaporator is formed in a flat tube installed in parallel with the loop heat pipe, and the walls between the multiple channels are divided walls.If the external heat load is large, the vapor evaporated from the liquid flows into a passage without a core at the top. Thus, the pressure difference between the steam flow pressure loss and the steam flow pipe is reduced, so that the operation flexibility due to the load fluctuation can be enhanced.

Further, since the specific volume of the liquid at the time of evaporation increases by several hundred times to 1,000 times or more, the number of vapor flow tubes not including the core for capillary pumping is sufficiently increased from the number of vapor flow tubes including the core to increase the liquid flow. There is a feature that can balance the steam flow with the steam.

In the above case, in the case of a flat tube in which the evaporator is installed vertically, the capillary pumping structure is constructed such that heat is supplied to both sides of the evaporator and H is inclined into a hollow polygonal face or a dividing wall in each channel. The core of the mold has a core structure of a porous material, and the steam flowing through the evaporating section has a structure in which a desirable positive (+) temperature gradient is formed.

In the above, in the case of a flat tube in which the evaporating section is installed horizontally, the capillary pumping structure is provided with heat on both sides of the evaporating section, and the core of the I-shaped belt can be inclined to the divided wall of each channel. Has a core structure of a porous material, and the vapor flowing through the evaporating section has a structure in which a desirable positive (+) temperature gradient is formed.

The axial torsion knitting core structure is a structure in which a spring in which a fine wire is inserted into each channel is torsionally knitted in the axial direction while being supported in the radial direction.

The mesh core structure is a core structure in which a screen mesh is inserted in each channel.

The core structure has a porous structure at the lower end of the vapor flow path so as to prevent the backflow of vapor generated downstream of the liquid / vapor interface at the liquid / vapor interface even when the external heat load is extremely large in the flat tube evaporator. The structure is such that a plug made of a substance is installed and the function of the fluid diode is exhibited in the heat transfer loop.

FIG. 8 shows the shapes of the fins (a, b, c, d, e, f, g, h) having the collision angles used in the present apparatus. By cutting into a pattern, discrete effects (discrete ef)
Fact) to enhance heat transfer. Here, h indicates the shape of the fin in which the louver pitch gradually increases or decreases in the downstream direction so that even when the external air flow used in the present device is at a low speed, it flows in the louver direction.

Reference numeral 12a denotes an OLF fin strip, 12b to 12d denote various shapes of the OLF fin strip, 12e and 12f denote holes formed in the OLF fin in various shapes such as a square, a right angle, a circle, an ellipse, and a hexagon. , 12
g is a projection formed on the OLF fins for promoting flow disturbance and heat transfer, and 12h is a non-equidistant strip for guiding the boundary layer flow of the OLF fin phase in the low-speed flow region.

FIG. 10 is a sectional view showing a multi-channel micro fin flat tube for promoting evaporation (or condensation) having split fins used in the present apparatus. The evaporating (or condensing) flow channel structure inside the flat tube has an evaporating portion (or condensing portion) formed in a flat tube installed in parallel with a loop heat pipe, and a multi-channel wall has a shape of a fine groove or a micro fin.

The following are some preferred embodiments using the multi-channel loop heat transfer device of the present invention.

FIG. 11A is a view showing an embodiment of a mobile cooling / dehumidifying material thermal air conditioner using the apparatus of the present invention, and FIG. 11B is another example of a mobile cooling / humidifying material thermal air conditioner using the device of the present invention. FIG. 11c shows another embodiment of a mobile cooling dehumidifier thermal air conditioner using the apparatus of the present invention. This configuration is similar to a mobile dehumidifier thermal cooler, except that an evaporator is installed at the location of the refrigeration (ice or phase change material capsule) box for lowering the temperature and to supply a low-temperature refrigerant to the evaporator. In addition, a small air conditioning system consisting of a compressor and a condenser is additionally installed.

The evaporator of the small air-conditioning system is installed between the evaporator and the condenser. When the air circulation path is viewed, the temperature of the external air drops through the evaporator, and then the evaporator of the small air-conditioner is set. After passing through the condenser, the temperature further decreases and is cooled and dehumidified to form low-temperature and high-humidity air. And the comfortable air passes through a path blown into the room by a fan driven by a motor provided in advance. At this time, the dehumidified water is temporarily stored and discharged to a water storage tank installed at a lower portion.

The arrangement of the evaporator and the condenser of the small air conditioning system and the arrangement of the evaporator and the condenser of the heat transfer device can be appropriately changed as required.

Further, the conditions of the small air-conditioning system, including the amount of charged refrigerant, can be adjusted and applied for purposes such as dehumidification and drying.

FIG. 12A is a view showing an embodiment of a movable dehumidifier thermal cooler using the apparatus of the present invention, and FIG. 12B is another embodiment of a movable dehumidifier thermal cooler using the apparatus of the present invention. Fig. 12c is another embodiment of the movable dehumidifier thermal cooler using the apparatus of the present invention. Fig. 12d is the other of the movable dehumidifier thermal cooler using the apparatus of the present invention. FIG. This configuration consists of an outer case, suction and discharge ports for connecting the case and the outside air, a fan for blowing air and a motor for driving it, a refrigeration (ice or phase change material capsule) box for lowering the temperature, and storing and discharging dehumidified water. The water storage tank is provided with the apparatus of the present invention.

A number of refrigeration (ice or phase-change substance capsule) boxes are installed between the evaporating section and the condensing section. When looking at the circulation path of the air, after the temperature of the external air drops through the evaporating section, After passing through a refrigerated (ice or phase change material capsule) box, the air becomes lower and humid as it goes down. Such air is driven by a motor provided in advance after the humidity becomes lower through a condenser. It goes through the path blown out by the fan. At this time, the dehumidified water is temporarily stored and discharged to a water storage tank installed at a lower portion.

The arrangement of the evaporating section and the condensing section can be made different from each other as required.

The problem with the conventional cooler is that, by forcibly convection the pad immersed in water with a blower fan, the temperature of the blown air decreases due to residual heat of evaporation of water, but 90% of the relative humidity is reduced by the evaporated water. The above humid air is transmitted to the user as it is, and the skin becomes sticky and uncomfortable, and there is a disadvantage that the coolness is reduced by half.

As an apparatus utilizing such an apparatus of the present invention, a mobile air conditioner, a mobile dehumidifier, a mobile dryer, an exhaust gas residual heat recovery device, a white smoke prevention device, and the like can be used.

The present invention is not limited to the specific preferred embodiments described above, and does not depart from the gist of the present invention as claimed in the appended claims, and any person having ordinary knowledge in the technical field to which the present invention belongs can be used in various forms. Of course, it is possible to implement various transformations,
Such modifications fall within the scope of the appended claims.

[0064]

As described above, the high-efficiency multi-channel loop heat transfer device of the present invention has a flat tube structure as compared with a heat pipe having the same vertical diameter, so that the flow pressure loss can be remarkably reduced and the high-efficiency OLF is realized. It has a fin structure.

Such a decrease in flow pressure loss can be achieved by increasing the flow rate under the same pressure drop condition. However, in the high efficiency multi-channel loop heat transfer device of the present invention, the fins in the evaporating section and the condensing section are reduced by increasing the flow rate. There is an advantage that the heat transfer efficiency due to the dimensional discrete effect can be significantly improved.

In the conventional heat pipe, the heat loss due to the flowing direction of the vapor and the liquid in the evaporating section, the heat insulating section, and the condensing section is considerably larger than the outer diameter of the heat pipe. Such heat loss
Although the steam pipe must be sufficiently insulated in order to exhibit the best performance by reducing the latent heat, in the loop heat transfer device of the present invention, since the steam pipe and the liquid pipe are separated, the heat is There is an advantage that the loss can be significantly reduced.

In the conventional heat pipe, the temperature is reduced due to conduction through the wall / core structure in the heated evaporating section, and the temperature is also reduced through the refluxed condensed working fluid. That is, the internal temperature drop in the normal state caused by heat transfer in most heat pipes is a decrease in fluid conduction, and the heat flux in the evaporating section is mainly limited by boiling at the core / liquid interface. In the loop heat transfer device using the flat tubes according to the present invention, since the heat is transmitted by direct conduction and convection due to the flow of the steam at the liquid / steam interface through the wall of the evaporator, the steam and the liquid are greatly suppressed. Since it circulates through two different pipes, unlike a heat pipe, there is an advantage that the amount of evaporation and condensation can be increased and the amount of heat power transmitted can be increased.

In the conventional heat pipe, two-phase flows occur in opposite directions in one pipe, and the distribution of liquid is greatly affected by the gravitational effect. The loop heat transfer device of the present invention has the advantages that the pressure loss is greatly reduced by providing the same flow direction because the phase is separated into two phases irrespective of the gravity state, and the heat transfer capability is greatly improved. is there.

When the flat tube is installed not only in the vertical direction but also in the horizontal direction, the core to be inserted therein has a core structure made of a porous material of an I-shaped belt which can be inclined to each channel dividing wall. Thus, there is an advantage that it can easily cope with a change in the installation direction.

Finally, the present invention does not require a fluid storage container, a complicated starting process, a control device, a pump, and other devices necessary for starting and operating the conventional heat pipe, and the heat load after the complete stop is eliminated. When it is used, it has the advantage that it will always start to operate again spontaneously, and its expected effect when used in a cooler and a mobile air conditioner, a dehumidifier, a dryer, an exhaust gas residual heat recovery device, a white smoke prevention device, etc. large.

[Brief description of the drawings]

FIG. 1a is a schematic front view of an evaporator of the apparatus of the present invention.

FIG. 1b is a schematic plan view of an evaporator of the apparatus of the present invention.

FIG. 1c is a schematic bottom view of the evaporator of the apparatus of the present invention.

FIG. 2a is a header used in the device.

FIG. 2b is a modified header used in the device.

FIG. 3a is an assembly diagram of a brazing joint between an evaporating section and a header used in the present apparatus.

FIG. 3b is a sectional view of the brazing joint between the evaporating section and the header used in the present apparatus.

FIG. 3c is a cross-sectional view showing a core of a lower header and a flat tube connecting portion used in the apparatus of the present invention.

FIG. 4a shows an external condensed water removal groove used in the present apparatus;
It is the perspective view which showed the evaporating part which has the H-shaped core for liquid pumping inside, and the fin for expansion surfaces.

FIG. 4b is the external condensate removal groove used in the device,
It is the perspective view which showed the evaporating part which has the I-shaped core for liquid pumping inside, and the fin for expansion surfaces.

FIG. 5a is a cross-sectional view of an evaporating section multi-channel flat tube provided with internal dividing fins used in the present apparatus.

FIG. 5b is a side view of the externally extended surface fins brazed to the flat tubes used in the device.

FIG. 5c is an exploded view of the extended surface fin of the device.

FIG. 6 is a multi-channel flat tube and brazed fins used in the present apparatus.

FIG. 7a is a multi-channel flat tube used in the present apparatus and a sectional structural view thereof.

FIG. 7b is a diagram showing a multi-channel flat tube used in the present apparatus and its sectional structure.

FIG. 7c is a multi-channel flat tube used in the present apparatus and a sectional structural view thereof.

FIG. 7d is a diagram showing a multi-channel flat tube used in the present apparatus and its cross-sectional structure.

FIG. 7e is a backflow preventing fluidic diode used in the present device for a plug at the lower end of the vapor flow path of the evaporator.

FIG. 8 shows the shapes (a, b, c, d, e, f, g, h) of fins having a collision angle used in the present device.

FIG. 9a is a schematic front view showing a brazed joint assembly between a two-row air material hot part steam condensing part and a header of the apparatus of the present invention.

FIG. 9b is a schematic plan view showing a brazed joint assembly between a two-row air material hot part steam condensing part and a header of the apparatus of the present invention.

FIG. 9c is a schematic bottom view showing the brazing connection assembly between the two-row air material hot part vapor condensing part and the header of the apparatus of the present invention.

FIG. 10 is a cross-sectional view showing a flat tube of a heat transfer promoting multi-channel micro fin provided with a split fin used in the present apparatus.

FIG. 11a is an embodiment of a mobile cooling dehumidifier thermal air conditioner using the apparatus of the present invention.

FIG. 11b is still another embodiment of a mobile cooling dehumidifier thermal air conditioner using the apparatus of the present invention.

FIG. 11c is still another embodiment of a mobile cooling dehumidifier thermal air conditioner using the apparatus of the present invention.

FIG. 12a is an embodiment of a mobile cooling / dehumidifying material hot air cooler using the apparatus of the present invention.

FIG. 12b is still another embodiment of the movable dehumidifier hot-air cooler using the apparatus of the present invention.

FIG. 12c is still another embodiment of the movable dehumidifier hot-air cooler using the apparatus of the present invention.

FIG. 12d is yet another embodiment of a mobile dehumidifier hot air cooler using the apparatus of the present invention.

[Explanation of symbols]

11 Flat tube for fluid supply 11a Multi-channel wall of flat tube for fluid supply 11b Multi-channel partition wall (fin) for flat tube for fluid supply 11c Multi-channel partition wall for flat tube for fluid supply 11d Multi-channel of flat tube for fluid supply Micro fins processed on divided wall surface 12 Collision angle β (−90 ° ≦ β
≦ 90 °), OLF fins having an inclination angle γ 12a OLF fin strips 12b to 12d Various shapes of OLF fin strips 12e to 12f Perforations of OLF fins 12g Projections for flow disturbance and heat transfer promotion on OLF fins 12h Low speed Non-equidistant strip for boundary layer flow guidance of OLF fin in flow area 13 (for fluid supply) Header 13a Coating material for aluminum brazing 14 Steam flow path inside spring including capillary pumping core 14a Does not include capillary pumping core Vapor flow path 14b in the evaporator 14b Vapor flow path in the evaporator that easily induces vapor flow by eliminating the pressure difference caused by the difference in the amount of evaporation 15 End cap for fixing U-shaped support frame and closing end of header 16 Fluid inflow (outflow) Pipe 17 Capillary pumping core 17a Twisted in axial direction Core 17b Core made of porous material 17c Core made of mesh 17d Vapor lock prevention interval 17e Backflow prevention fluid diode (bottom plug of vapor flow path in evaporation section) 18 Micro groove or micro fin 19 Flat header insertion header Side hole 21 U-shaped heat exchanger support frame 22 Brazing 23 Central condensate discharge groove of flat tube 23a Condensate discharge groove on both sides of flat tube 24 Central condensate discharge hole of OLF fin

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Kim Hyo-Bon South Korea Apartment No. 1-902 Sok Sangchong Dong Jongsol Apartment, Korea (72) Inventor Kim Chang-Jun, Seoul, Korea・ National University Professor Apartment Ka-dong-206 (No address) (72) Inventor Li Jun-Sik South Korea Seoul, Yancheong Shin-Jung 1 Dong Mok Tong apartment 1024-1405 (No address)

Claims (16)

[Claims] 1. A heat transfer device for transmitting heat while changing the phase of a working fluid from one loop, wherein a strip which is cut outside so as to have a collision angle β with a main flowing gas is formed. OLF fins are provided, and the inside is divided into multiple channels, the structure of the evaporation flow path for liquid capillary pumping and the transfer of evaporated vapor. A flat tube for fluid supply to be inserted is provided with an evaporating unit and a condensing unit which are connected in parallel, and each of the evaporating unit and the condensing unit is connected with a steam pipe and a liquid pipe to form an internal heat source. The heat transfer medium forms a closed circuit, and high efficiency fins are used outside the heat transfer device to improve the heat transfer promotion effect through eddy motion and boundary layer destruction. Transmission apparatus. 2. The structure of the evaporating section is inserted into each side hole formed in one side of the header of the fluid supply connection pipe, and the vertically connected fluid supply flat tubes are vertically stacked. The upper and lower 2
It consists of a heat exchanger support frame installed in two places, the lower end of the wick is always immersed in the liquid of the lower header, pumps the liquid through the capillary of the wick, prevents the backflow of vapor at the lower end, and performs the liquid diode function The high efficiency multi-channel loop heat transfer device according to claim 1, wherein a plug made of a porous material is provided. 3. The structure of the condensing part has almost the same shape as that of the evaporating part, but has no condensed water discharge groove at the outside of the flat tube and at the center of the fin, and the inside of the flat tube has a multi-channel wall. 2. The high-efficiency multi-channel loop heat transfer device according to claim 1, wherein the heat transfer device has no core inside. 4. When the header is formed by arranging fluid pumping cores in channels inside a flat tube according to a heat load capacity,
2. The high-efficiency multi-channel loop heat transfer device according to claim 1, wherein the number is adjusted to adjust the pressure loss of the steam flow. 5. The high-efficiency multi-channel loop heat transfer device according to claim 1, wherein the steam pipe has an outer diameter smaller than an outer diameter of a heat pipe having the same heat transfer capacity and is insulated. . 6. The high-efficiency multi-channel loop heat transfer device according to claim 1, wherein the liquid tube is capable of being supercooled so that boiling does not occur at an inlet of an evaporator. 7. A cross section of the evaporation channel structure inside the flat tube comprising the multi-channel is circular, elliptical, square, rectangular,
1 selected from the group consisting of polygons such as hexagons
The high efficiency multi-channel loop heat transfer device according to claim 1, wherein the heat transfer device has two cross-sectional shapes. 8. The multi-channel evaporating flow path structure is generated without forming a vapor film at the liquid / vapor interface even when the external heat load is large, divided into multi-channel dividing walls. 2. The high-efficiency multi-channel loop heat transfer device according to claim 1, wherein the vapor of the vapor film is formed so as not to flow into an adjacent coreless vapor flow channel to generate vapor lock. 9. The high-efficiency multi-channel loop heat transfer device according to claim 1, wherein the surface structure of the multi-channel wall of the evaporating and condensing flow path is selected from a shape of a fine groove or a micro fin. . 10. The structure of the evaporating flow path for performing the capillary pumping is as follows. In a flat tube which is supplied with heat on both side surfaces of the evaporating portion and is installed vertically, each channel has an H-shaped core structure,
The high-efficiency multi-channel loop heat transfer device according to claim 1, wherein a desirable positive (+) temperature gradient is formed in the steam flowing through the evaporator. 11. The structure of the evaporating flow path for performing the capillary pumping is not limited to the case where heat is supplied to both sides of the evaporating section and the evaporating section is installed so as to be vertically inclined. And an I-shaped core structure to provide a capillary pumping force that is insensitive to the direction of the evaporator, so that a desired positive (+) temperature gradient is formed in the vapor flowing through the evaporator. The high-efficiency multi-channel loop heat transfer device according to claim 1. 12. The core structure according to claim 1, wherein a spring (helical wire) capable of reducing a supporting force in a radial direction is inserted into a center of each channel, and the thin wire is twisted in an axial direction. The high-efficiency multi-channel loop heat transfer device according to claim 1, characterized in that: 13. The high-efficiency multi-channel loop heat transfer device according to claim 1, wherein the core structure has a core structure in which screen meshes woven with fine wires are stacked in several layers in each channel. 14. The wick structure prevents the backflow of vapor generated at the liquid / vapor interface at the lower end of the flat tube evaporator even when the external heat load is extremely large, and functions as a fluid diode in a heat transfer loop. The high-efficiency multi-channel loop heat transfer device according to claim 1, wherein the heat transfer device has a structure that is exhibited. 15. The liquid pipe is configured to reduce the degree of supercooling by using external condensed water cooled and dehumidified by an evaporator (a refrigeration box in the case of a cooler) after heat is released from both sides of the condenser. The high efficiency multi-channel loop heat transfer device according to claim 1, wherein the heat transfer device has a meandering structure. 16. The loop heat transfer device separated into two steam pipes and a liquid pipe, wherein the steam pipe having an outer diameter larger than the liquid pipe is maintained at a higher temperature than the liquid pipe, and the liquid working fluid is always in the steam pipe. The liquid flow tube is moved by the vapor pressure of the liquid, and when a thermal load is applied even after a complete stop, the flow does not always flow in the reverse direction, and the operation automatically starts again. The high-efficiency multi-channel loop heat transfer device according to claim 1.