JP3713633B2 - Closed temperature control system - Google Patents

Description

[0001]
[Industrial application fields]
The present invention relates to the structure of a temperature control device for heat exchanger applications, and in particular, forms a closed loop system of a heat transfer fluid circulation path by connecting a heat receiving heat exchanger, a waste heat heat exchanger, and them. In a closed temperature control system comprising five components: a connecting pipe, a heat medium fluid circulation means, and a two-phase condensable heat medium fluid forced circulation type loop type thin pipe heat pipe. The present invention relates to a structure of a closed temperature control system in which a porous flat tube is effectively used.
[0002]
[Prior art]
Along with the progress of high-density packaging of recent devices and high performance of semiconductor elements, it is becoming more difficult to cool the devices corresponding to these devices, and it is becoming difficult to cope with cooling by forced air cooling. As a countermeasure, temperature control of a heating element using a water cooling method has been frequently used. The water-cooling method has a large heat capacity and large heat transfer coefficient, so the cooling efficiency is high. Compared with the forced air cooling method, the cooling performance is improved tenfold, and the cooling device is greatly reduced in size. there were. There is also an advantage that the cooling performance can be freely controlled by adjusting the flow rate of the cooling water.
[0003]
However, the air cooling method is very easy to apply and exhaust heat treatment, whereas the water cooling method (1) reduces the reliability of the applied equipment due to corrosion, rusting, etc. of the object to be cooled and the pipeline. (2) The pipeline may be blocked due to the occurrence of scale. (3) Freeze at low temperatures. (4) Condensation occurs in the cooling pipe due to ambient temperature and humidity. (5) In the case of water leakage, there is a risk of short circuit or leakage of electric circuits. (6) The degree of freedom in designing the equipment for water supply / drainage pipe arrangement is reduced. (7) Mobility and portability of applicable equipment are poor. (8) Problems often occur in wastewater treatment. Many problems occurred.
[0004]
Closed liquid cooling systems are frequently used as a solution to these problems. This system uses the heat-receiving heat exchanger as the first component, the exhaust heat exchanger as the second component, and connects them in a loop to form a circulation path for the refrigerant liquid The pipeline is the third component, the refrigerant liquid forced circulation pump is the fourth component, the four components are the main components, and the object to be cooled depends on the refrigerant liquid receiving and radiating cycle. Cooling. A closed liquid cooling system can solve most of the problems of conventional water cooling systems by appropriate selection of accessory components and refrigerant liquid. In other words, the adoption of the closed liquid cooling system improves the mobility, portability, installation, etc. while maintaining the advantages of the water cooling method, and solves most of the major problems such as environmental problems and wastewater treatment problems. there were.
[0005]
However, the price for this is extremely large, and the heat exchanger for receiving heat of the first component is miniaturized and improved in the same way as water cooling. However, as a second component, a large air-cooled heat exchanger for exhaust heat and As a fourth component, a powerful large-scale circulation pump is newly required. Further, essential accessory components such as a liquid quality maintenance device, a refrigerant liquid replenishing tank, a drain pad, and various safety measures are required. In this case, an ultrapure water production device, a filtration device, and a PH check device in the case of antifreeze liquid are also required. As a result, a large problem such as an increase is added. In addition, for many years, it is unavoidable that water leaks from many connections of pipes connecting various accessory components such as a circulation pump, and that water droplets are generated due to condensation. There were also problems in that the atmosphere inside the body deteriorated, the device casing could not be hermetically sealed, and a drain pad had to be provided. An even greater problem is that despite the efficient cooling of the object to be cooled by the main heat-receiving heat exchanger, it is ultimately necessary to dissipate the amount of heat into the atmosphere using a large heat exchanger for exhaust heat. This is a fateful defect. In terms of heat balance, the amount of heat absorbed by the heat receiving heat exchanger and the amount of heat thrown away by the exhaust heat exchanger are almost equal except for heat dissipation from the surface of the equipment housing. Even if the exchanger is adopted, the total volume of the device casing is not reduced in size and weight, but rather increased in size and weight.
[0006]
The inventor invented Japanese Patent Application No. 6-210339 (closed system temperature control device) in order to solve the above problems of the closed liquid cooling system. This system constitutes a forced circulation cycle in which bubbles and droplets of a two-phase condensable heat transfer fluid are alternately arranged and circulated as a fifth component in the four components of a conventional closed liquid cooling system. This is a closed temperature control system to which a component as a loop-type meandering capillary heat pipe of a heat-receiving / radiating part separation type that controls the temperature of the temperature-controlled substance by the phase change of the medium fluid and the heat capacity of the medium medium is added. The first, second, third, and fourth components of this system are not much different from those of the conventional liquid-cooled closed system, but the difference from the conventional system is the fifth essential component. As a whole, the system is configured as a serpentine capillary heat pipe with a separate heat receiving and radiating portion. That is, the fifth component is added as a heat pipe container in which all of the heat medium fluid flow path is hermetically sealed, and this container is evacuated to a high vacuum and then has an internal volume. Thus, a two-phase condensable fluid of a predetermined ratio is sealed to form a heat pipe, and the entire system is configured as a loop-type meandering tube heat pipe with a heat radiating / separating part separated.
[0007]
FIG. 10 shows one explanatory view of an application example of such a closed system temperature control apparatus according to Japanese Patent Application No. 6-210339. H is a heat exchanger for receiving heat, H-1 is a heat exchanger for receiving heat, C is a heat exchanger for exhaust heat, and C-1 is a heat exchanger for exhaust heat. Reference numeral 1-1 denotes a meandering long thin tube constituting the heat receiving heat exchanging portion H-1, and u-6 to u-10 are unit thin tube units. 1-2 is a meandering long thin tube constituting the heat exchanging part C-1 for exhaust heat, and u-1 to u-5 are unit thin tube units thereof. 7-n is a heating element, and is cooled by heat exchange with the two-phase condensable heat transfer fluid L that has been liquefied and circulated in the unit capillary units u-1 to u-5 via the cold plate 10. . Reference numeral 3 denotes a connecting pipe, which includes a high temperature connecting pipe 3-1 from which the heat transfer fluid flows out from the heat receiving heat exchange section and a low temperature connecting pipe 3-2 from which the heat transfer fluid flows out from the exhaust heat exchanging section. 4 is a forced circulation pump, which is a complete seal type. Reference numeral 5 denotes an inflow side header and an outflow side header of the heat exchange unit. The heat transfer fluid L circulating in the meandering long thin tube 1-2 of the heat exchange unit C-1 for exhaust heat is heat-exchanged with the convection of the gas phase heat transfer fluid A for the amount of heat conveyed from the heat exchange unit 1 for heat reception. Heat is exhausted to the outside of the device casing 15 through the wind tunnel 14. The heat receiving heat exchanger H, the high temperature connecting pipe 3-1, the exhaust heat heat exchanger C, the low temperature connecting pipe 3-2 and the forced circulation pump 4 disposed in the pipe line are connected in a highly airtight manner. A loop-shaped heat medium fluid circulation channel is formed, and this circulation channel is formed as a high vacuum heat pipe container, and a predetermined amount of a predetermined two-phase condensable hydraulic fluid is enclosed to separate the heat receiving and radiating unit The meandering capillary tube heat pipe is constructed. The closed system temperature control apparatus configured as described above has an extremely excellent temperature control function.
[0008]
The difference between this system and the closed liquid cooling system is that both the heat receiving heat exchanger and the exhaust heat heat exchanger are composed of meandering narrow tubes having an inner diameter of 4 mm or less, and means for circulating the heat transfer fluid. As a loop type meandering capillary heat pipe to which Japanese Patent Application No. 2-319461 or No. 6-3354 is applied, this loop type meandering capillary heat pipe is disclosed in Japanese Patent Application Laid-Open No. 4-52495 (loop type capillary) Heat pipe) It is configured as a heat receiving / radiating part separation type heat pipe for application, and as a heat medium fluid circulation auxiliary means for the heat receiving / radiating part separation type thin tube heat pipe which also has a heat medium fluid circulation function. A fully-sealed forced circulation pump 4 represented by an electromagnetic fluid pump is used.
[0009]
The loop-type meandering tube heat pipe is an external energy source due to the axial vibration and circulation of the vapor bubbles and fluid droplets of the two-phase condensable heat transfer fluid generated by nucleate boiling in the heat receiving part of the two-phase condensable heat transfer fluid. Transport the amount of heat by themselves without the need for help. However, when configured as a heat receiving / dissipating part separated heat pipe, unlike the ordinary loop-type meandering capillary heat pipe, there are basically only two reciprocating pipes connecting the heat receiving / dissipating parts, or a multiple of them. The number of pipes, the circulation flow rate of the heat transfer fluid in the heat pipe itself circulates very little, and the connection distance becomes longer. The axial vibration energy and the circulating thrust of are significantly attenuated. For these reasons, the heat-transfer capability of the loop-type meandering capillary heat pipe with the heat receiving / separating part separation type is drastically reduced as compared with a normal loop-type meandering-tubular heat pipe. In this system, the problem of the reduction in the amount of heat transport is solved by providing a fluid pump for forced circulation in the loop to circulate the heat transfer fluid at a high speed. The point that the fluid pump can be applied in spite of being a heat pipe is due to the unique function of a thin tube heat pipe in which the working fluid circulates in a state where high pressure bubbles and droplets are alternately arranged, This is an important feature of the loop type meandering capillary heat pipe. Since this system is a heat pipe, the amount of circulating heat transfer fluid can be reduced to about one-fourth that of the conventional refrigerant liquid circulation system, so the forced circulation fluid pump can be downsized. Therefore, the energy consumption for that purpose can be extremely reduced.
[0010]
If the circulation flow rate of the heat transfer fluid is sufficiently large and sufficiently high, this means not only compensates for the fact that the heat transport capacity of the heat receiving / separating part separation type heat pipe is lower than that of the meandering capillary heat pipe, The heat transport capability can be greatly increased as compared with the case of using the meandering loop type thin tube heat pipe method or the case of the heat receiving / radiating part separation type heat pipe using the normal refrigerant liquid forced circulation method. This increase in heat transport capacity is not simply due to the increase in the circulation speed of high-pressure vapor bubbles and fluid droplets in the loop-type meandering capillaries, but two-phase condensation in the heat-receiving portion capillaries of the medium fluid. When the heat transfer fluid moves at high speed, the internal pressure on the inner surface of the heat receiving section narrow tube drops, and this greatly increases the amount of heat medium fluid vapor bubbles generated, and therefore the amount of condensation in the heat dissipation section also increases dramatically, and the heat transfer fluid as a whole. This is due to the drastic increase in the amount of latent heat transport.
[0011]
The effect of this system configured as described above is to solve all the problems of the closed liquid cooling system. The air cooling heat exchanger, which is the biggest factor that makes it difficult to reduce the size and weight, is greatly reduced in size, and the refrigerant It is possible to reduce the liquid circulation pump to a fraction of the size, omit additional devices such as pure water production equipment, filter, refrigerant liquid replenishment tank, drain pad, etc., and keep the atmosphere inside the housing low in humidity and clean. To. More importantly, because the entire system is a heat pipe, it is extremely reliable and requires no maintenance over the years.
Another feature of this system is that the heat transport capacity is not determined by the temperature difference as in normal heat pipes, but the heat transport capacity is freely controlled by controlling the circulation speed and circulation rate of the heat transfer fluid. There is a point that the body temperature can be freely controlled.
[0012]
[Problems to be solved by the invention]
Japanese Patent Application No. 6-233939 (closed system temperature control device) as described above has extremely high performance and has solved all the conventional problems, but there are various difficulties in increasing the capacity of the system. As long as serpentine tubules are used as the basic constituent material, the cost has increased significantly, which has been a major problem.
[0013]
That is, when configuring a large capacity system such as several tens of kilowatts, it is necessary to increase the number of meandering turns of the unit thin tube unit in the heat exchange part, or further increase the number of unit thin tube units to be increased. Therefore, a large number of headers are required, and the number of interconnecting portions of the heat receiving heat exchanger, the exhaust heat heat exchanger, and the headers and connecting pipes connecting between the heat exchangers and the connecting pipes are greatly increased, resulting in a complicated piping configuration. It was unavoidable. This complicated piping configuration completely sealed all of the connecting parts, making welding connection work extremely difficult to maintain the reliability of the system, and greatly increasing the manufacturing cost of the entire system. . Furthermore, the number of thin tubes and the number of meanders increase drastically as a whole, and therefore the time required for the meander bending process of the thin tubes increases drastically. In the present situation, meandering bending of thin tubes has to depend on manual work, and it is difficult to shorten the processing time, which makes the production cost of the entire system more and more expensive.
[0014]
Also, the increase in the total length of the narrow tube and the increase in the total number of meanders increase the pressure loss of the heat transfer fluid in the narrow tube, which increases the size of the heat transfer fluid circulating pump and increases the size of the entire system. And increased energy loss for system operation.
[0015]
If the heat exchanger is a forced air cooling heat exchanger, the large number of meandering tube groups in the heat exchanger greatly increases the pressure loss outside the tube, which increases the size of the fan for convection generation and noise. It was also a problem to increase.
[0016]
As a further major problem, due to intensifying competition for cost reduction in the industry in recent years, demands for reducing manufacturing costs are beginning to become strict even for the closed system temperature control device despite its excellent function. In addition, this industry demand for cost reduction is not related to the capacity of the system, and some cost reduction measures are required even for a system with a small capacity. In particular, it is extremely difficult to automate the meandering and bending of the meandering tubules. At present, it is necessary to rely on manual work, which occupies most of the manufacturing cost, and the reduction of the machining time is a major issue.
[0017]
[Means for solving the problems]
Recent advances in light metal press extrusion technology are remarkable, and it is becoming easier to produce a porous flat tube with a large number of through-holes inside a thin and wide ribbon-shaped plate. The extrusion technology is still advancing, but at present, it is possible to produce a porous flat tube with a thickness of 1.3 mm, a width of 50 mm, an inner diameter of the through-hole of 0.7 mm, and a number of 49 pores. . Such a porous flat tube can be easily configured as a desired thin and wide large flat plate by connecting a predetermined number of predetermined lengths in parallel and parallel on the same plane. Also, a long ribbon-like porous flat tube having a thickness of 1.3 mm, a width of 19 mm, an inner diameter of the through-hole of 0.6 mm, and 21 pores can be manufactured. Such a ribbon-like long porous flat tube can be easily formed into a desired meandering shape or a helical shape. FIG. 1 is a perspective view showing the structure of such a porous flat tube. Reference numeral 1 is a porous flat tube, and the current technology has a thickness of 1.3 mm and a width of about 50 mm, but the length can be manufactured to several hundred US. 2-n is a through-hole group, and the fluid diameter of each pore can be reduced to about 0.5 mm.
[0018]
The inner diameters of these through-holes are all equal to or less than 2 mm in fluid diameter, satisfying the necessary conditions for a meandering capillary tube heat pipe. That is, in such a narrow through-hole, when configured as a meandering capillary heat pipe, no matter how small the amount of sealed working fluid, the working fluid always flows in the pores during operation of the heat pipe. When filling and blocking, vapor bubbles and droplets are alternately arranged, and when the hydraulic fluid moves or generates vibrations, it moves continuously as it is regardless of the moving speed and the magnitude of vibration. And can vibrate.
[0019]
In the closed temperature control system of the present invention, the heat exchange part of the heat exchanger is configured by effectively using the porous flat tube having a large number of small through-holes as described above as means for solving the problems. That is, the basic structure of the present invention is that the heat receiving heat exchanger is the first component, the exhaust heat exchanger is the second component, and they are connected to form a closed loop of the circulation path of the heat transfer fluid. The connection tube forming the system is the third component, the heat medium fluid circulation means is the fourth component, and the configuration of the two-phase condensable heat medium fluid forced circulation type loop type thin tube heat pipe is the fifth. A porous material having a small-diameter through-hole group in the heat exchange part of either or both of the first and second components in this closed temperature control system. A flat tube is configured to be used effectively. The basic structure of the closed temperature control system of the present invention will be described below.
[0020]
The heat exchange part of at least one of the first and second constituent elements is a porous flat tube made of a light metal with good thermal conductivity having a through-hole group with a fluid diameter of 4 mm or less. It is configured as the main material, and the inside diameter of the through-hole is maintained in a predetermined holding posture, and even if the flow rate of the heat transfer fluid circulating through it is very small, the fluid movement Regardless of the conditions, the surface tension always fills and closes the pores, and the diameter is reduced until reaching the diameter that moves in the pores as they are.
[0021]
In the case of a relatively large diameter pore having an inner diameter of 4 mm or more, the condensed working fluid or the non-gas phase working fluid flows down the pipe along the inner wall of the pipe against the circulating flow of the gas phase working liquid, and the heat exchanger is low. It stays in the water level and makes the circulation of the gas-phase hydraulic fluid and the pressure in the pipe unstable, thereby reducing the performance. On the other hand, in the pores applied to the present invention having a sufficiently small diameter, bubbles and droplets are alternately arranged in every part thereof, and the evaporation and condensation of the working liquid only causes expansion and contraction of the bubbles. The liquid phase hydraulic fluid does not flow down to the low water level and does not stagnate, and even if the hydraulic fluid circulates, the state of the fluid remains maintained, so the pressure distribution in the pipe is always uniform, Both the hydraulic fluid (droplet group) and the gas phase hydraulic fluid (bubble group) are circulated stably. That is, the porous flat tube when applied instead of the meandering capillary tube operates in the same manner as the meandering thin tube, and therefore the porous flat tube having a large number of through-holes operates as a large number of parallel meandering narrow tubes, so the number is much smaller. Or the length can be substituted.
[0022]
Both ends of the flat tube group forming the heat exchanging portion are connected to each other by a header, and an extension portion of each header is airtightly connected to a connecting pipe line of a third component.
[0023]
The forced circulation airtight pump, which is the fourth component, is a part where the connection pipe line in the circulation path of the heat transfer fluid connects between the exhaust heat exchanger outlet and the heat exchanger inlet. It is arrange | positioned and it arrange | positions so that a working fluid may circulate from the heat exchanger for waste heat toward the heat exchanger for heat receiving. This forced circulation airtight pump is a pump having a structure capable of maintaining a high degree of airtightness between the heat medium fluid circulation passage and the outside of the circulation system over a period longer than a period required for the system.
[0024]
All the connections in the closed loop circulation system of the heat transfer fluid formed including all of these four components are connected in a completely airtight manner, so that the entire circulation flow path is formed as an integral sealed container. After the container is evacuated to high vacuum, a predetermined proportion of the two-phase condensable hydraulic fluid with respect to its total volume is enclosed and sealed, and the fifth component, the two-phase condensable heat transfer fluid forced It is characterized by being configured as a circulation type loop type thin tube heat pipe.
[0025]
The separated heat receiving / radiating section loop type meandering capillary heat pipe configured when the present invention is applied is completely different in operation and configuration from the conventional heat receiving / radiating section separated heat pipe. The conventional heat receiving / radiating part separation type heat pipe illustrated in FIG. 11 feeds the condensed working fluid L into the steam generator (heat absorber) e, the condenser (heat radiator) c, and the steam generator e of the working fluid. The basic structure is a hydraulic fluid circulation pump 14 and a refrigerant liquid pipeline 3-2 and a vapor pipeline 3-1 which are connected to form a loop. The hydraulic fluid circulation is a liquid phase operation. The liquid L and the gas phase working liquid V are separately circulated. That is, the working fluid moving in the steam pipe 3-1 from the steam generator (heat absorber) e to the condenser (heat radiator) c in the loop connection pipe is a gas phase (steam) and is saturated. Has vapor pressure. The working fluid moving in the refrigerant liquid conduit 3-2 from the condenser (heat radiator) c to the steam generator (heat absorber) e is in a liquid phase and generally has a gravity siphon action. Further, since the vapor pressure is generated in the steam generator (heat absorber) e, the hydraulic fluid cannot be supplied into the steam generator e without the pressure input by the hydraulic fluid circulation pump 14. In the figure, A is a forced convection of the gas phase heat transfer fluid, and H is a heating means. At first glance, the heat transport of such a conventional heat receiving / dissipating part separation type heat pipe seems to be performed by the liquid phase hydraulic fluid circulation by the pump, but the heat transport capacity is the vapor pressure in the steam generator e. It depends on the amount of steam generated and depends on the negative pressure (suction force) due to the steam condensation of the condenser c. Even if the liquid-phase working fluid circulation amount supplied to the steam generator e by the pump exceeds the steam generation capacity of the steam generator e or exceeds the steam condensation capacity of the condenser (radiator) c, the heat of the heat pipe The transport performance is rather degraded. The amount of heat is ultimately transferred only by the phase change of the working fluid, that is, by the latent heat transport of the working fluid, and the sensible heat is not transported by the heat capacity of the fluid circulation. As another difference, in order to prevent pressure loss, in the conventional normal heat receiving / radiating part separation type heat pipe, the condenser c, the refrigerant liquid line 3-2, the steam generator e, and the steam line 3- No capillary is used for 1. Therefore, in the case of convection receiving and radiating, it is necessary to attach various fin groups to the receiving and radiating part.
[0026]
On the other hand, in the loop-type thin tube heat pipe of the heat receiving / separating part separation type configured when the present invention is applied, all of the heat exchange part is composed of meandering pores formed by through-holes of a porous flat tube. In the two-phase heat transfer fluid in the pores, the liquid phase working fluid (droplet) and the gas phase working fluid (vapor bubble) are alternately separated and arranged in all parts, and the pipe is always The state in which the inside of the road is filled and closed is maintained, and in that state, it vibrates in the axial direction and circulates in a predetermined direction, and the amount of heat moves from the high temperature part toward the low temperature part. During this time, the vapor bubbles shrink or disappear with heat dissipation and circulate while liquefying, but are replenished by the pressure vapor bubbles generated one after another at the heat receiving portion, and do not become only the liquid phase. In this heat pipe, the heat quantity is transported in combination with latent heat transport due to the phase change of the gas phase fluid and sensible heat transport due to the heat capacity of the liquid phase fluid. Further, the working fluid of the meandering pore heat pipe of the present invention in which pressure bubbles and droplets are alternately arranged is completely different from a normal heat pipe in that it can be forcedly circulated by a liquid pump. Furthermore, in the meandering pore heat pipe, the porous flat tube itself acts as a heat receiving and radiating fin, so that it can be sufficiently applied as a convection heat radiating portion even when no fin group is attached. Therefore, the heat receiving / dissipating part separation type loop type meandering pore heat pipe (flat tube heat pipe) constructed by applying the present invention is different from the conventional heat receiving / dissipating part separation type heat pipe as described above. It is essentially different in all respects such as configuration, operating principle, and action.
[0027]
The basic configuration of the closed system temperature control apparatus of the present invention having such a novel configuration will be described with reference to FIG. The figure is a perspective view for explaining the basic structure of the system of the present invention. As shown in the figure, the basic structure of the present invention is a heat receiving heat exchanger H that is a first component, a heat exchanger C for exhaust heat that is a second component, and these are connected in a closed loop and in an airtight manner. The connection pipe 3 that is the third component, the forced circulation pump 4 that is the fourth component for circulating the working fluid in the loop, and the loop-shaped pipe line that is not shown in the figure, It is exhausted to a high vacuum to become a heat pipe container, and the container is filled with a predetermined amount of two-phase condensable hydraulic fluid less than its inner volume, and the two-phase condensable heat medium fluid forced circulation type loop type It consists of five components, the fifth component of being configured as a pore heat pipe.
[0028]
The feature of the present invention resides in that the heat exchanging portion of the heat exchanger, which is the first and second constituent elements of these constituent elements, is configured by effectively using a porous flat tube. In FIG. 2, the porous flat tubes are arranged in parallel in a flat plate shape in the heat receiving heat exchanging portion H-1 and are effectively used as the flat parallel porous flat tube 1-1. In the heat exchanging part C-1 for exhaust heat, a large number of units in which the porous flat tubes are meandered are arranged in parallel and effectively used as a group of meandering porous flat tube units 1-3. This method of application is merely an example, and various application modes can be considered.
The operation of the system of FIG. 2 is exactly the same as that of Japanese Patent Application No. 6-210339 (closed system temperature control device), and in the heat receiving heat exchanger H, a high-temperature working fluid that absorbs the heat quantity of the heating element 7-n is generated. In a gas phase rich state in which vapor bubbles and droplets are alternately distributed, the header 5 is connected to the heat exchanger C for exhaust heat through the connection pipe 3, and the heat amount of the working fluid in the convection air A by the cooling fan 8. The heat is exhausted and changed into a liquid-phase rich low-temperature working fluid, which is returned to the heat-receiving heat exchanger H by the forced circulation pump 4 through the header 5 and the connecting pipe 3 (not shown) to form a circulation cycle. Yes. The forced circulation pump 4 maintains a high degree of airtightness with respect to the outside of the circulation system, and can be maintained so as not to impair the function as a heat pipe for many years.
[0029]
[Action]
The configuration of the present invention as described above has the same effect as that of Japanese Patent Application No. 6-210339. In addition, the effective use of the porous flat tube is a closed system temperature control device as described in the following items. Demonstrate the effect.
(1) The application of the porous flat tube has the effect of simplifying the configuration of the heat exchange part, achieving a reduction in size and weight, and reducing the pressure loss of the heat transfer fluid for convective heat exchange to improve the function. In these, one of the porous flat tubes has a surface area several times larger than that of the thin tube and has 10 or more through-holes, so that one of the tubes is provided with several or more of the thin tube heat pipes. This is because the use length of the porous flat tube can achieve its purpose in a fraction of the time.
(2) Various fin groups can be easily mounted on both flat surfaces of the porous flat tube heat pipe. It makes it possible to increase the convective heat exchange performance of the outer surface several times. This makes it possible to exhibit heat exchange performance several times that of a thin tube heat pipe in which fins cannot be mounted, or to reduce the size and weight by a fraction.
(3) Despite the fact that a porous flat tube exhibits a high performance several times or more as a heat pipe compared to a thin tube, the unit price per length does not reach 1.5 times. This, combined with the fact that the necessary length is reduced to a fraction as described above, reduces the material cost of the heat exchanging part to less than a fraction.
(4) In the case of using meandering, the required length is reduced to a fraction and the configuration is further simplified, so that the molding and assembly costs are reduced to a fraction.
[0030]
【Example】
First Embodiment FIG. 3 is a perspective view showing a first embodiment of the closed system temperature control apparatus of the present invention. In this embodiment, the heat receiving heat exchanging portion H-1 or the exhaust heat exchanging portion C-1 in the basic structure of the present invention as illustrated in FIG. And it is the structure comprised by arranging and arrange | positioning so that it may become flat form as a whole. In the figure, the flat parallel porous flat tube group 1-1 is formed by arranging and arranging the porous flat tubes 1-n in parallel and parallel and in a flat plate shape as a whole. The porous flat tube group 1-1 is arranged in parallel at a predetermined interval in the figure, but this enhances the internal pressure strength of the header 5 that collects the working fluid that circulates in the porous flat tube 1-n. If the header is sufficiently thick, or if it is made of a metal material that is sufficiently strong in terms of strength, the porous flat tubes 1-n are densely arranged. It may be arranged in parallel. In the heat exchanger of this embodiment, heat is exchanged in the plane of the flat parallel porous flat tube group 1-1. In that case, there are many examples in which a heat generating element is directly mounted on the flat surface to exchange heat with heat by intermetallic heat conduction, or a liquid cooling jacket is attached to exchange heat with exhaust heat. Another feature of this embodiment is that the header 5 can have a relatively small diameter.
[0031]
Second Embodiment FIG. 4 is a partial perspective view showing a second embodiment of the closed system temperature control device of the present invention. In this embodiment, the heat receiving heat exchanging portion H-1 or the exhaust heat exchanging portion C-1 in the basic structure of the present invention as illustrated in FIG. And it is the structure comprised by arrange | positioning the plane side facing each other, It is characterized by the above-mentioned. In the illustrated example, a large number of porous flat tubes 1-n having a predetermined length are perpendicular to the axial directions of the headers 5-1, 5-2 at both ends of the porous flat tubes 1-n. Are joined together. Accordingly, a large number of porous flat tubes 1-n are arranged in parallel and parallel, and their plane sides are opposed to each other. Although this structure has a problem that the header 5 has to have a relatively large diameter, a larger number of porous flat tubes 1-n can be arranged in the same area to exhibit higher heat exchange performance. There are advantages. This heat exchanging part is mainly used for convection heat exchange, and particularly used for air cooling heat exchange. In many cases, the convection flow direction is usually used in a flow parallel to the surface of the porous flat tube 1-n. In a special case, the end face of the porous flat tube 1-n is arranged at a predetermined angle with respect to the axial direction of the headers 5-1, 5-2. May be arranged in In that case, the flow direction of the convection is applied by giving a flow parallel to the plane formed by the porous flat tube group and orthogonal to each porous flat tube.
[0032]
Third Embodiment FIG. 5 is a perspective view showing a third embodiment of the closed system temperature control device of the present invention. In this embodiment, the heat receiving heat exchanging section H-1 or the exhaust heat exchanging section C-1 in the basic structure of the present invention as illustrated in FIG. 2 performs a predetermined number of reciprocating meanders for a predetermined distance. A large number of unit units 1-3 each having a repeating meandering porous flat tube as a unit unit 1-3 are arranged in parallel at a predetermined interval. FIG. 5 is a perspective view of the unit unit 1-3. In the basic structure of FIG. 2, a state in which a plurality of unit units 1-3 are arranged in parallel is shown. Reference numeral 6 in FIG. 5 denotes a partition plate for efficiently flowing the convection flow of the convection heat exchange into the unit unit 1-3. FIG. 5 shows an example in which both ends of the porous flat tube 1 of the unit unit 1-3 are connected to the headers 5-1 and 5-2 at a position penetrating the partition plate 6. This connection position is illustrated in FIG. It is not limited by 5. Although this embodiment is mainly used for convection heat exchange, the present embodiment has an advantage that it can be applied regardless of the direction of the convection flow. That is, when the convection is a flow parallel to the partition plate 6 in FIG. 5, the flow may be parallel to the upright surface of the porous flat tube 1 or may be flow perpendicular to the upright surface of the porous flat tube 1. The flow may be in a direction having an inclination angle on the upright surface. Further, as an important advantage, as shown in FIG. 2, the porous material flows into the row group of the meandering porous flat tube unit units 1-3 from all directions along the partition plate 6, and changes the flow direction at the center to stand upright. It may be a flow that flows in the direction of the tip along the group of flat tubes 1 and is discharged from the tip portion, and conversely, the porous flat tubes that flow up from the tip portion of the group of porous flat tubes 1 and stand upright It may be a flow that flows toward the partition plate 6 along one group, collides with the partition plate 6, changes the flow direction, and is discharged in all directions along the partition plate 6. In the case of such a flow, empirical data has been obtained that improves the heat exchange performance by several tens of percent. As another feature of the present embodiment, there is an advantage that the meandering inversion distance of the meandering porous flat tube unit unit 1-3 can be made sufficiently long to improve the heat exchange performance. In the example of FIG. 5, this means that the height of the unit unit 1-3 can be made sufficiently high. In the case where the conventional meandering capillary heat pipe is configured as in this embodiment, the practical limit is about 250 mm because each capillary is too flexible. In the case of the present embodiment, since the strength of the porous flat tube is large, it can be practically used even at a height of 500 mm, and if it is necessary to further increase the strength of the meandering porous flat tube unit group, appropriate reinforcement is required. It is easy to take measures.
[0033]
[Fourth Embodiment] FIG. 6 is a sectional view showing a fourth embodiment of the closed system temperature control apparatus of the present invention. This embodiment is a forced circulation pump that is the fourth component of the basic structure of the present invention as illustrated in FIG. 2, and its driven part is in the circulation channel of the heat transfer fluid that is the third component. The drive unit is arranged outside the circulation flow path, and the two are separated completely and hermetically, and the drive force between the two is transmitted by electromagnetic means or ultrasonic vibration means. It is configured to be transmitted. The cross-sectional view of FIG. 6 shows an example thereof, 3 is a connecting pipe, 9 is a cylinder, and these are circulation flow paths for liquid phase heat transfer fluid (working fluid) L. A hollow vibrator (driven portion) 11 is inserted into the cylinder in a sliding state, and the hollow portion serves as a flow path for the liquid phase heat transfer fluid. Check valves are respectively provided at both ends of the hollow portion, and both check valves restrict the flow in the same direction. Reference numerals 10-1 and 10-2 are oscillation coils that electromagnetically vibrate the hollow vibrator in the front-rear direction of the flow direction of the liquid-phase heat transfer fluid. The vibration of the vibrator operates as two fluid pumps in series by the interaction between the provided check valve and the front and rear gaps of the cylinder. The airtightness of such a pump is perfect and guarantees the degree of vacuum as a heat pipe of the closed system of the present invention to the limit of the mechanical life of the pump. FIG. 6 shows an example in which a driving unit and a driven unit, which are held completely airtight with each other, are electromagnetically coupled to each other, and several examples of other structures are put into practical use. More recently, an ultrasonically coupled drive device has also been proposed.
[0034]
Fifth Embodiment FIGS. 7 and 8 are schematic side views showing a fifth embodiment of the closed system temperature control apparatus of the present invention. Although it is extremely difficult to attach a fin group to a meandering capillary heat pipe, the fin group can be easily attached to a porous flat tube heat pipe. In particular, as shown in the second embodiment of FIG. 4 and the third embodiment of FIG. 5, when there are portions in which the planes of the porous flat tubes are opposed and arranged in parallel, by mounting a common fin group on both the opposed surfaces. The heat exchange performance can be greatly increased. FIGS. 7 and 8 of the fifth embodiment are a common fin group in which ultrathin metal tapes meandering into the porous flat tubes 1-n and 1-3 of the second embodiment of FIG. 4 and the third embodiment of FIG. 13 is installed. The high density common fin group 13 can be mounted at a low cost because all the fin groups can be mounted together by brazing in the furnace in one step. In addition, since it is a common phy group, heat is supplied from both sides, so it is an important feature that fin efficiency is high and therefore high performance. Further, this fin group is characterized by its extremely light weight.
[0035]
[Sixth Embodiment] FIG. 9 is an explanatory view of a sixth embodiment of the closed system temperature control apparatus of the present invention and is a schematic side view. This embodiment is composed of multiple rows of meandering porous flat tube units 1-3, but in the figure, a schematic side view of the first row is shown. In this embodiment, the first component and the second component in the basic configuration are combined, and the heat receiving heat exchanging unit H-1 and the exhaust heat exchanging unit C-1 are the same. The meandering porous flat tube unit 1-3 is shared and configured as a united heat exchange section CH. A group of both terminals of a large number of combined heat exchangers CH are connected to headers 5-1 and 5-2, and each header is airtightly connected by a connecting pipe 3. A forced circulation pump 4 is mounted in an airtight manner. As a result, all of the constituent elements are formed as a loop-shaped hermetic container, and a predetermined amount of the two-phase condensable heat transfer fluid L is enclosed to constitute a meandering pore heat pipe. The two-phase condensable heat transfer fluid L is forcibly circulated in a direction from the terminal side of the heat exchanger for exhaust heat C-1 toward the terminal of the heat exchanger for heat reception H-1. In the figure, broken lines H-2 and C-2 indicate a heating means and a cooling means, respectively. The present embodiment is applied when it is not necessary to provide a distance between the heat receiving heat exchanging unit H-1 and the exhaust heat exchanging unit C-1, but compared with the basic configuration of the present system as follows. There are advantages.
(1) Since the heat receiving heat exchanging part H-1 and the exhaust heat exchanging part C-1 are directly connected, that is, connected by a large number of porous flat tubes, the two-phase condensable heat transfer fluid L meanders. The principle of the thin tube heat pipe provides a powerful circulating thrust without the help of a pump. Even if the forced circulation pump 4 is small, the temperature control performance of the entire system is strong.
(2) Since the circulation path of the two-phase condensable heat transfer fluid L can be minimized, there is very little pressure loss in the loop. From this point, the forced circulation pump 4 exhibits powerful performance even if it is downsized. .
(3) Since the overall size is reduced, the amount of the two-phase condensable heat transfer fluid L enclosed is reduced, and the burden on the forced circulation pump 4 is greatly reduced from this point.
(4) Significant downsizing and high performance are possible, contributing to the reduction in size and weight of applicable equipment.
[0036]
【The invention's effect】
One of the aluminum porous flat tubes having a large number of small through-holes in the ribbon-shaped flat tube is equivalent to several tens of thin tubes in the thin tunnel effect inside, and the heat transfer performance of the outer surface is comparable to that of the thin tubes. It is almost equal to ten, and its flexibility and flexibility are superior to those of pure copper capillaries with the same diameter as its thickness. As a result, the heat exchanging section of the simplified system has been reduced in use length of the pipe to 10% and reduced in the configuration volume to 50%. Furthermore, the unit price per length of the material is almost the same, and as a total effect of these, we succeeded in reducing the material cost of the heat exchanging part by 90%, the processing cost by 80% and the system as a whole by 70%.
[Brief description of the drawings]
FIG. 1 is a perspective view showing a structure of a porous flat tube of a constituent material of the present invention.
FIG. 2 is a perspective view showing a basic structure of a closed system temperature control device of the present invention.
FIG. 3 is a perspective view showing a first embodiment of a closed system temperature control apparatus of the present invention.
FIG. 4 is a perspective view showing a second embodiment of the closed system temperature control apparatus of the present invention.
FIG. 5 is a partial perspective view showing a third embodiment of the closed system temperature control apparatus of the present invention.
FIG. 6 is a sectional view showing a fourth embodiment of the closed system temperature control apparatus of the present invention.
FIG. 7 is a schematic side view showing an example of a fifth embodiment of the closed system temperature control apparatus of the present invention.
FIG. 8 is a schematic side view showing another example of the fifth embodiment of the closed system temperature control apparatus of the present invention.
FIG. 9 is a schematic side view of the explanatory view showing the configuration of the sixth embodiment of the closed system temperature control apparatus of the present invention;
FIG. 10 is an explanatory diagram showing a configuration of a conventional closed system temperature control device.
FIG. 11 is an explanatory diagram showing a configuration of a conventional heat receiving / dissipating part separation type heat pipe.
[Explanation of symbols]
1 porous flat tube
1-1 Flat parallel porous flat tubes
1-2 Face-to-face porous flat tube
1-3 Meander porous flat tube unit
2-n through pore group
3 Connecting pipe
3-1 Steam line
3-2 Refrigerant liquid pipeline
4 Forced circulation pump
5-1 Header
5-2 Header
6 Partition plate
7-n Heating element
8 Cooling fan
9 cylinders
10-1 Oscillation coil
10-2 Oscillation coil
11 Hollow vibrator
12-1 Check valve
12-2 Check valve
13 Common fin group
14 Wind tunnel
15 Equipment housing
21-1 Meandering long tubule
21-2 Meandering long tubule
un-unit capillary unit
A Gas phase heat transfer fluid (convection air)
L Liquid phase heat transfer fluid (condensation fluid)
C Heat exchanger for exhaust heat
C-1 Heat exchanger for exhaust heat
C-2 Cooling means
H Heat receiving heat exchanger
H-1 Heat exchanger for exhaust heat
H-2 Heating means
CH united heat exchanger
e Condenser (heat radiator)
c Steam generator (heat absorber)

Claims (7)

A closed temperature control system for controlling the temperature of a temperature controlled substance according to a circulation cycle of a heat transfer fluid, wherein a heat receiving heat exchanger for transferring heat between the temperature control object and the heat transfer fluid is exchanged. One component is a heat exchanger for exhaust heat that exchanges heat between the circulating heat transfer fluid and the external heat transfer fluid to discharge the heat to the outside of the system, and the second component, The connection pipe that forms a circulation cycle of the heat transfer fluid is used as the third component, and the heat transfer fluid is received from the heat transfer fluid outlet of the heat exchanger for exhaust heat. The forced circulation pump that circulates in the direction toward the heat transfer fluid inlet of the heat exchanger is the fourth component, and the entire heat transfer fluid circulation cycle system that includes these four components is condensed in two phases. As a heat exchanger fluid forced circulation type loop type heat pipe That that is made is in a fifth component, has these five elements as the main component, the heat exchange section of the bi-side of the first and second components, material of good thermal conductivity light metal A porous flat tube having a through-hole group as a main material, and the through-hole has a fluid diameter of 4 mm or less and is maintained in a predetermined holding posture and circulates in the heat medium Regardless of the flow rate of the fluid, regardless of the flow conditions of the fluid, the surface tension always fills and closes the pores and reaches the diameter that moves in the pores as they are. Each through-hole group of the flat tube group forming a heat exchanging portion is connected to each other by headers at both ends thereof, and the extension of each header. The part is airtightly connected to the connecting line of the third component Thus, the forced circulation pump, which is the fourth component, is arranged between the flow path connecting the third component connecting pipe between the exhaust heat heat exchanger outlet and the heat receiving heat exchanger inlet. This forced circulation pump provides a high degree of airtightness necessary to maintain the function as a heat pipe between the heat medium fluid circulation system and the outside of the circulation system for at least the years required for the system. Ri pump der structure which can be held, the heat receiving heat exchanger flat parallel perforated flat tube group are aligned so as to be flat as a whole and parallel parallel consisting of perforated flat tube is formed, The pores of the porous flat tube group communicate with a common header that collects the working fluid that circulates in the porous flat tube at each end, and the heat exchanger for exhaust heat connects the meandering porous flat tube to a predetermined distance. Is formed to repeat a predetermined number of reciprocating meanders. A closed temperature control system comprising a plurality of unit units 1-3 arranged in parallel at predetermined intervals .   2. The closed temperature according to claim 1, wherein the heat exchange part has a structure in which a large number of porous flat tubes having a predetermined length are arranged in parallel and parallel so as to form a flat plate as a whole. Control system.   2. The closed structure according to claim 1, wherein the heat exchanging portion has a structure in which a large number of porous flat tubes having a predetermined length are arranged in parallel and parallel, and the plane sides thereof are opposed to each other. Temperature control system.   The heat exchanging unit has a structure in which a large number of unit units each having a meandering porous flat tube that repeats a predetermined number of reciprocating meanders for a predetermined distance are arranged in parallel at predetermined intervals. The closed temperature control system according to claim 1.   The driven part of the forced circulation pump as the fourth component is arranged in the circulation channel of the heat transfer fluid as the third component, and the drive unit is arranged outside the circulation channel. 2 is configured to be completely hermetically isolated, and to transmit the driving force between the two by electromagnetic means or ultrasonic vibration means. The closed temperature control system described.   The predetermined portion of the straight tube portion of the porous flat tube group in the heat exchanging portion is arranged in parallel and parallel with the flat surfaces of the flat tubes facing each other. The closed temperature control system according to claim 1, wherein the fin groups are brazed, and the fin groups are meandering ultrathin metal ribbons.   The first component and the second component are combined, and the same porous flat tube group is commonly applied to both heat exchange units, and the combined heat exchange unit is circulated. The exhaust heat side header outlet and the heat receiving side header inlet of the heat medium fluid flow path are connected by a connecting pipe line and a forced circulation pump to form a closed loop system of the hydraulic fluid circulation path. Closed temperature control system as described in.

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