JP2847343B2 - Closed system temperature controller - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a structure of a temperature control device applied to a heat exchanger, and more particularly to a solid-liquid heat transfer device for transferring heat from a temperature controlled body in an equipment housing and a gas-phase heat transfer device. a gas-liquid heat exchanger for allowing forced convection heat exchange with the heat transfer fluid, and a connecting tube and completely seal pump to form a closed loop by connecting them, receiving for temperature control of the temperature control body Loop type thin tube heat with separate radiator
The present invention relates to a structure of a closed system temperature controller having a pipe application structure .

[0002]

2. Description of the Related Art In recent years, with the progress of high-density packaging and the performance of semiconductor elements, the cooling of equipment has become increasingly difficult, and cooling by forced convection air has become impossible. As a countermeasure, the temperature control of the heating element by the liquid cooling cooling method has been frequently used recently. In many cases, the cold plate has a structure in which a tunnel serving as a flow path of the refrigerant liquid is formed, or the metal plate has a structure in which a meandering thin tube is sandwiched. As the refrigerant liquid, water or an aqueous solution of ethylene glycol is often used. In these cases, since the heat capacity of the water is large and the heat transfer coefficient is large, the cooling efficiency is high, the cooling performance is improved ten times as compared with the forced convection air system, and the cooling device is significantly downsized. There were advantages. Another advantage is that the cooling performance can be freely controlled by adjusting the flow rate of the refrigerant liquid.

As described above, the liquid-cooled cooling system has an extremely high performance as compared with the air-cooled cooling system, and it has been extremely effective to make the cold plate, the cooler itself, etc. smaller and lighter with higher performance. However, in the case of the air cooling system, the treatment of exhaust heat is very simple, whereas the liquid cooling system has various problems. Taking an example in the case of water cooling, (1) the reliability of the applied equipment may be reduced due to corrosion, rust, etc. of the cooled object and the pipeline. (2) Depending on the water quality, the pipeline may be clogged due to the generation of water scale and the like. (3) There is a risk of freezing in a low-temperature environment, and there is often no problem during operation of the device. However, a troublesome problem occurs when the device is stored such as when work is stopped or during transportation. (4) When water leaks due to conductivity, electronic devices may be damaged by elements or circuits due to short-circuits, and in heavy-duty devices, there is a risk of electric shock due to electric leakage. (5) A tank as a cooling water supply source, a supply pipe, and the like are required, and a drainage pipe is required. As a result, the degree of freedom in designing the applicable equipment is reduced. Poor portability. In addition, these pipes have many connections by joints, and it is inevitable that water leaks from those joints for many years, which causes a problem of environmental deterioration in offices and factories. Sometimes. (6) Using refrigerant liquid other than water (1)-
Although it is easy to solve the problem (4), the price of the refrigerant liquid is so high that it cannot be easily discarded like water. When thrown away, a waste liquid treatment device is required from an environmental point of view. And many other problems.

As a best solution to these problems, a closed system liquid cooling system as shown in FIG. 2 is usually applied. This system is entirely housed inside the equipment housing C, and a liquid cooling heat absorber (solid-liquid heat transfer device) in which the refrigerant liquid L circulates inside to absorb and cool the heat of the cooled body 12. H and high-temperature waste liquid L of liquid-cooled heat absorber H-
An air-cooled heat exchanger (gas-liquid heat exchanger) E for cooling H and discharging heat to the outside of the equipment; and a high-temperature connecting pipe 4- which connects them in a loop to form a refrigerant liquid L circulation cycle. 1
And a low-temperature pipe line 4-2. In these pipe lines, a refrigerant liquid circulation pump 14, a refrigerant liquid quality preserving means (ultra pure water production device) 15, a refrigerant liquid supply tank 16, a drain pad 1
7, various safety devices, etc. are provided together, and all of them are stored together with the object to be cooled 12 in the same equipment housing. In the figure, Ao is forced convection outside air for heat radiation. As the refrigerant liquid L, an insulating refrigerant liquid, ultrapure water, antifreeze liquid with anti-corrosion measures, or the like is applied according to the use of the system. In some cases, a refrigerator is used instead of the air-cooled heat exchanger E. However, these require a compressor, a condenser, etc., consume a lot of energy for their operation, and further cool their waste heat. Since it requires an air cooling device, it is applied to a large scale case. The closed system liquid cooling device can solve most of the problems of the conventional liquid cooling system by appropriately selecting various auxiliary devices and refrigerant liquids. That is, the application of the closed system solves most of major problems such as mobility, portability, installation, work environment, wastewater treatment, safety, and the like.

[0005]

Although the present invention can be applied to both cooling and heating of a temperature-controlled body, both of them are exactly the same in principle, and for the sake of simplicity of explanation, the following will be described. Will be described with respect to the cooling system temperature control. The liquid cooling system using the closed system is extremely excellent as described above. However, the cost for this is extremely large, and although the liquid-cooled heat absorber (solid-liquid heat exchange device) H is greatly reduced in size and performance, the air-cooled heat exchanger (gas-liquid heat exchanger) E and the refrigerant liquid circulation , A liquid quality preserving device 15, a refrigerant liquid supply tank 16,
Various additional measures such as various safety measures, heat insulating means (partition wall) C-3 between the heat dissipating portion C-1 and the cooling portion C-2 of the device housing C are required, and the refrigerant liquid is water. In addition, it is necessary to additionally provide a pure water production device 15, a filtration device, and in the case of antifreeze, a PH check device, etc., and to store them, the equipment housing becomes large, the weight increases, and the maintenance cost increases. Problems were inevitably added.
In addition, over a long period of time, it is inevitable that water drops from various water treatment devices such as circulation pumps and many connecting parts of pipelines connecting them will cause dripping of water droplets due to dew condensation. In order to maintain the atmosphere inside the housing satisfactorily, the equipment housing cannot be hermetically sealed, and it is necessary to provide the drain pad 17. The most significant additional problem is that, despite the fact that the cooling target 12 is cooled by the main liquid-cooled cooler H, the heat absorbed by the liquid-cooled cooler H is ultimately reduced by the large air-cooled heat exchanger E to the atmosphere. It is necessary to throw it away. In terms of heat balance, the amount of heat absorbed by the liquid-cooled cooler H is equal to the amount of heat discarded by the air-cooled heat exchanger E. Therefore, the volume of the device housing C can be reduced in size and weight by applying the liquid-cooled heat absorber H. It was not done, but rather had to be large.

The present invention reduces these additional problems, and in particular reduces the size of the air-cooled heat exchanger E, which is the largest factor in increasing the volume, and reduces the size of the air-cooled heat exchanger E.
And the additional means such as the pure water production device 15, the filter, the coolant supply tank 16 and the drain pad 17 can be omitted or significantly reduced in size, and the atmosphere in the housing can be kept at a low humidity and clean. It is an object of the present invention to provide a heat pipe type closed system temperature control device.

[0007]

The first feature of the basic structure of the closed stem according to the present invention for solving the problems and achieving the above-mentioned object is a means for circulating a heating medium fluid. Japanese Patent Application Laid-Open No. 4-190090 (Patent No. 19)
No. 67738, loop type thin tube heat pipe) or Japanese Patent Publication No. Hei 6-3354 (Japanese Patent No. 1881122, loop type thin tube heat pipe).
No. (Micro Heat Pipe) and Japanese Patent Application No. 5-24191
Patent application No. 6-160490 (loop type meandering thin tube heat pipe) plus 4 registered patents and pending patent applications to 4 patents of patent No. 8 (patent No. 2544701). The point is that it is configured. The second feature of the basic configuration is that the loop-shaped meandering thin-tube heat pipe to which the present invention is applied is configured as a heat pipe with a separate receiving and radiating portion. A third feature of the basic configuration is that a completely sealed pump is used as a means for circulating the heat medium fluid in the heat pipe separated from the heat receiving and radiating section.
This complete seal type pump seals due to wear.
Replacement with mechanical seal pump which may impair performance
In addition, the driven part is a gas-liquid heat exchange
It is arranged in the connecting conduit connecting the
The drive unit is provided outside the connecting pipe, and the driven unit is
Is configured to be driven by electromagnetic force from the
Is completely airtightly sealed outside the closed loop
In that the electromagnetic fluid pump that is configured that are used
is there. Completely sealed type pump commonly called an electromagnetic fluid pump
In addition to the magnetic coupling type fluid pump,
There is

The loop-shaped meandering thin-tube heat pipe is formed by the axial vibration and circulating flow of the vapor bubbles and fluid droplets of the two-phase condensable heat transfer fluid generated by nucleate boiling at the heat receiving part of the two-phase condensable heat transfer fluid. Transports heat efficiently without the need for external energy. However, unlike a normal loop-type meandering thin tube heat pipe, when the heat pipe is configured as a separate heat pipe, the connecting pipe connecting between the heat receiving and radiating parts is only two reciprocating pipes, and the heat transfer fluid in the heat pipe is When the circulation flow rate circulating by itself is extremely small and the connection distance is further increased, the pressure loss in the pipe increases, and the axial vibration energy of the heat transfer fluid is greatly attenuated. For these reasons, the loop-shaped meandering thin-tube heat pipe of the separated heat-receiving / radiating portion has a drastically reduced heat transport capacity as compared with a normal loop-shaped meandering thin-tube heat pipe. In the present invention, the problem of the decrease in the amount of heat transport is solved by providing a forced circulation means (fluid pump) in the loop to forcibly circulate the heat medium fluid. The fact that the fluid pump can be applied in spite of using a heat pipe is an important feature of the loop type meandering thin tube heat pipe in which the working fluid circulates as a two-phase fluid. If the circulation flow rate of the heat medium fluid is sufficiently large and sufficiently high, this means not only compensates for the decrease in the heat transport capacity, but also depends on the ordinary meandering loop type thin tube heat pipe system or the ordinary It is possible to greatly increase the heat transport capacity as compared with the case of the heat pipe having the separated heat receiving / radiating section based on the refrigerant liquid forced circulation system. This increase in heat transfer capacity is not simply due to the increase in the circulation speed of vapor bubbles and fluid droplets in the loop-shaped meandering tubule, but also in the heat receiving portion tubule of the two-phase condensable heat transfer fluid. Due to the high-speed movement, the internal pressure on the inner surface of the heat receiving unit narrow tube drops, which drastically increases the amount of vapor bubbles generated in the heat medium fluid, and thus the amount of condensation in the heat radiating unit also increases drastically. This is due to the sharp increase.

The loop-shaped meandering thin-tube heat pipe of the separated heat-receiving / radiating section applied to the present invention is completely different in operation and configuration from the conventional heat pipe of the separated heat-receiving / radiating section type. The conventional heat pipe with separate heat receiving and radiating portions illustrated in FIG. 3 sends a condensed working fluid 1-1 into a steam generator (heat absorber) e of a working fluid, a condenser (radiator) c, and a steam generator e. The basic structure of the pump is a hydraulic fluid circulation pump 14 and a refrigerant fluid pipe 4-3 and a steam pipe 4-4 which connect them to form a loop. This cannot be called circulation of the phase working fluid. That is, from the steam generator (heat absorber) e in the loop connection pipe to the condenser (radiator)
The working fluid that moves in the steam pipeline 4-4 toward c is a gas phase (steam) and has a saturated steam pressure. The working fluid moving in the refrigerant liquid pipe line 4-3 from the condenser (radiator) c to the steam generator (heat absorber) e is a liquid phase, and generally has a gravity siphon action. Further, since a steam pressure is generated in the steam generator (heat absorber) e, the working fluid cannot be supplied into the steam generator e without the pressure input by the pump 14. In the figure, Ao forced convection outside air and Ho are heating means. At first glance, the heat transfer of such a conventional heat-dissipating-part-separated heat pipe seems to be performed by the liquid-phase working liquid circulation by a pump, but the heat transfer capacity is determined by the amount of steam generated in the steam generator e. Or the vapor condensing capacity of the condenser c. Even if the circulation amount of the liquid-phase working liquid supplied to the steam generator e by the pump exceeds the steam generating capacity of the steam generator e, the condenser (radiator)
Even if the vapor condensing capacity of c is exceeded, the heat transport performance of the heat pipe is rather deteriorated. The heat transport is ultimately performed only by the phase change of the hydraulic fluid, that is, the latent heat transport of the hydraulic fluid, and not the heat transport by the liquid circulation. Another difference is that no thin tubes are used for the refrigerant liquid line 4-3 and the vapor line 4-4 to prevent pressure loss. Therefore, it is necessary to mount various fin groups for receiving and radiating heat.

On the other hand, in the loop type meandering thin-tube heat pipe of the present invention, all of which are constituted by meandering thin tubes, and the inside of the pipe is entirely formed.
The liquid-phase working liquid (droplets) and the gas-phase working liquid (steam bubbles) are alternately arranged in a state of filling and closing the inside of the pipeline, vibrating in the axial direction by themselves while maintaining that state, and It circulates in a predetermined direction, and the amount of heat moves from the high-temperature part to the low-temperature part by itself. During this time, the vapor bubbles shrink or disappear with the release of heat, but are replenished by the pressure vapor bubbles that are successively generated in the heat receiving section.
Therefore, the transport of the heat quantity is performed not only by the latent heat transfer by the phase change of the two-phase fluid but also by the sensible heat transfer by the heat capacity of the liquid phase fluid. The working fluid of such a meandering thin tube heat pipe is completely different from a normal heat pipe in that it can be forcedly circulated by a liquid pump under pressure. Further, in the meandering thin tube heat pipe, there is no need to attach a fin group because the meandering thin tube itself acts as a radiation fin. Thus, the loop-shaped meandering thin-tube heat pipe of the separated heat-receiving / radiating section according to the present invention is different from the conventional heat-receiving / separating-portion-type heat pipe as described above in all respects in its configuration, operating principle, operation and the like. Are completely different.

The basic structure of the closed system temperature controller of the present invention to which the loop type meandering thin tube heat pipe of the novel type having a separate heat receiving / radiating section is applied will be described with reference to FIG. The figure is a schematic diagram for explaining the system, the device housing is shown in cross section, and all the thin tubes are shown in a diagram in order to avoid complicating the drawing. The drawing is an explanatory diagram of the basic structure of the present invention and also serves as an explanatory diagram of the first embodiment of the present invention. In the figure, a closed system temperature control device for a temperature controlled body 3 in an equipment casing C is a solid-liquid system that transfers heat between the temperature controlled body 3 and a two-phase condensable heat medium fluid l. A heat exchange unit H, a gas-liquid heat exchanger E for exchanging heat between the heat exchanged by the two-phase condensable heat transfer fluid 1 and the forced convection a of the outside air, and a closed loop between them. The main constituent elements are a connecting pipe 4 and a completely sealed pump 5 for forced circulation of a heat medium fluid for strongly circulating a two-phase condensable heat medium fluid 1 sealed in a loop in a predetermined direction. The solid-liquid heat exchange unit H and the gas-liquid heat exchanger E are formed of meandering long thin tubes 1-1 and 1-2, each of which is a heat receiving part of a loop-shaped meandering thin tube heat pipe of a separated heat receiving / radiating part type. And as a part corresponding to the heat radiation part,
The pump connected to each other by the high-temperature connection pipe 4-1 and the low-temperature connection pipe 4-2, and the pump disposed in the low-temperature connection pipe 4-2 has a structure capable of guaranteeing long-term reliability as a heat pipe. It is characterized in that it is applied and configured. All of these system components are stored in the equipment housing C except for the heat exchange part 2 of the gas-liquid heat exchanger E. The heat exchange part 2 is provided inside or outside the equipment housing C. The convection control means (wind tunnel) 11 is provided so as to be located in the convection.

[0012]

The structure of the present invention as described above exhibits the following functions. (1) The operation due to the configuration as the loop-type thin tube heat pipe of the separated heat receiving / radiating part. (1-1) Unlike the conventional heat pipe and the conventional heat-dissipating unit separated type heat pipe, the liquid-phase heat medium fluid and the gas-phase heat medium fluid circulate or vibrate together to perform heat transport. The sensible heat transport due to the heat capacity of the heat transfer and the latent heat transport due to the phase change of the vapor are performed together. Since the two-phase fluid working fluid in such a state can be forcedly circulated by the liquid pump, the sensible heat due to the liquid-phase heat transfer fluid is different from the transport capacity of the conventional heat pipe by only the latent heat of the heat transfer fluid. Heat transport is added, and furthermore, their heat transport capability is strongly amplified by the forced circulation of the heat transfer fluid, so that the heat transport capability becomes extremely strong. Further, the gas-liquid heat exchanger to which the loop-type thin tube heat pipe is applied does not require the installation of the fin group, and the thin group of meandering thin tubes can be directly used as a radiator.
The air-cooled heat exchanger E of the conventional closed system temperature controller illustrated in FIG. (1-2) The heat transfer capacity can be freely controlled by controlling the circulation speed and the circulation amount of the heat medium fluid, instead of the fixed heat transfer capacity due to the temperature difference as in a normal heat pipe. Therefore, it is possible to freely control the temperature of the temperature-controlled body, which is impossible with the conventional heat pipe type temperature controller. (1-3) It has been experimentally confirmed that a loop-type thin tube heat pipe (using HFC134a and chemical formula CH ₂ FCF ₃ as a working fluid) can withstand long-term continuous use for 30 years. Therefore, it is presumed that the closed system temperature control device of the present invention can withstand continuous long-term use up to the limit of the life of the completely sealed pump for circulating refrigerant liquid. This means that in the closed system temperature controller of the present invention, the liquid quality preserving means or the ultrapure water producing device 15, the refrigerant liquid supply tank 16, the drain in the conventional closed system temperature controller illustrated in FIG. It is possible to omit the pad 17 and various safety devices attached thereto, thereby simplifying the structure of an equipment housing for storing the entire system as shown in FIG. 1 and greatly reducing the size thereof. (2) Action due to application of a completely sealed pump. (2-1) Since the heat transfer fluid is not contaminated or leaked, a long life as a loop-type thin tube heat pipe is guaranteed. (2-2) Since there is no fear of leakage of the heat medium fluid, the inside of the device housing is always kept clean, so that the device housing can be made a closed type.

(3) Comprehensive operation (3-1) Since the whole system is miniaturized, the circulation path of the heat medium fluid is shortened, the amount of heat radiation leaked from the circulation path is small, and the configuration of the circulation pipeline Is simple, the heat insulating coating can be effectively and easily applied, so that the amount of leaked heat is synergistically reduced, and the cooling efficiency of the heat transfer unit and the exchange efficiency of the gas-liquid heat exchanger are improved. Further, the temperature inside the device housing is reduced, and the reliability of various components inside the housing is improved.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment FIG. 1 also serves as an explanatory diagram of a first embodiment of a closed system temperature controller according to the present invention. In the figure, the device housing C and the convection control means 11 are shown in cross section, and the internal structure of the system is schematically shown. For the sake of simplicity, the meandering long thin tubes 1-1 and 1-2 are all shown in a diagram. In FIG. 1, the portions corresponding to the calorie exchanging unit 1 and the calorie exchanging unit 2 are formed of a metal having good thermal conductivity and have a meandering long thin tube 1-1, 1-2 having an outer diameter of 5 mm or less at the maximum. The inner diameter is such that the heat medium fluid 1 flowing through it always fills and closes the inside of the tube even if the heat medium fluid 1 is very small due to the cohesive force generated by its surface tension, and the narrow tube has Regardless of the holding posture, the inside diameter is made sufficiently small so that the inside of the tube can be moved in that state. When the two-phase condensable heat medium fluid 1 is sealed after degassing the thin tube container constituted by the long thin tubes 1-1 and 1-2 thus reduced in diameter to a high vacuum, the heat medium fluid 1 Due to the surface tension, a plurality of liquid-phase heat medium fluids and a plurality of gas-phase heat medium fluids are separated and arranged alternately. The vapor-phase heat transfer fluid group has a saturated vapor pressure corresponding to the temperature, and is in a state where the pressure is always applied to the liquid-phase heat transfer fluid group and the balance is maintained.
When heat absorption or heat radiation occurs in a part of the thin tube, the balance is lost, and the liquid phase heat transfer fluid is rapidly moved and propelled toward a low temperature portion in the thin tube. In addition, the two-phase heat medium fluid 1 in the thin tube in such a state allows the circulating propulsion force and vibration energy generated by heat absorption and radiation and the circulating propulsion force applied by the pump to propagate very sensitively and efficiently over the entire length of the thin tube.

The long thin tubes 1-1 and 1-2 are meandered back and forth over a predetermined distance to form a heat exchange unit 1 and a heat exchange unit 2 each having a predetermined number of turns. The meandering long thin tubes 1-1 and 1-2 constituting the calorie exchange unit 1 and the calorie exchange unit 2 which are located at a predetermined distance from each other,
For each predetermined number of meandering turns, a unit capillary unit u
And a plurality of thin tube units u as a whole
-1, u-2, and un are aggregates. The calorie exchanging unit 1 and the calorie exchanging unit 2 composed of such a thin tube group can effectively exhibit the heat exchanging and heat exchanging functions without the need for the fin group.

The entire length of each of the meandering long thin tubes 1-1 and 1-2 constituting each of the unit thin tube units U is determined by the pressure loss of the heat medium fluid 1 circulating in the inside of the unit thin tube unit. The length is not reduced below a predetermined value. Further, both ends of each unit thin tube unit u are an inlet 6 and an outlet 7 of the two-phase condensable heat transfer fluid 1 respectively, and the heat transfer fluid inlet and outlet groups of all the unit thin tube units are The inlet header 8 and the outlet header 9 are airtightly aligned and connected to the inlet header 8 and the outlet header 9, respectively. Further, the inlet header 8 and the outlet header 9 separate the heat exchange unit 1 and the heat exchange unit 2 by a predetermined distance. High-temperature connecting pipe 4-1 and low-temperature connecting pipe 4-
2, the high-temperature connecting pipe 4-1 airtightly connects the discharge side header 9 of the calorie exchange section 1 and the inflow side header 8 of the heat exchange section 2, and the low-temperature connecting pipe 4-2 has a calorific value. The discharge side header 9 of the exchange section 2 and the inflow side header 8 of the heat transfer section 1
And a closed-loop conduit is configured as a closed container as a whole. With such a configuration, the circulating propulsion force and the vibration energy of the axial vibration applied to the two-phase condensable heat transfer fluid 1 flowing in the closed loop pipe are uniformly and reliably fed into each unit thin tube unit u. Thus, the functions of the heat transfer unit 1 and the heat exchange unit 2 are ensured.

A predetermined portion of the low-temperature connection pipe 4-2 is provided with a completely sealed pump 5 for circulating a heat medium fluid which can be operated while maintaining high airtightness and does not contaminate the heat medium fluid 1. Are arranged in an airtight manner. The closed container of the closed loop conduit including the heat exchange unit 1 and the heat exchange unit 2 configured as described above is evacuated to a high vacuum and then filled with a predetermined amount of a predetermined two-phase condensable heat transfer fluid 1 so that the entire container is sealed. The heat transfer medium 1 serving as a working fluid as a heat pipe is directed from the discharge side of the heat exchange unit 2 to the inflow side of the heat exchange unit 1 as a heat pipe. A cold plate 10 is formed by combining the heat transfer section 1 with a metal flat plate, and a temperature controlled body 3 is mounted on the cold plate by means having good thermal conductivity. Meandering long thin tube 1
-1 is constituted as a solid-liquid heat transfer device H in which heat is transferred between the two-phase condensable heat transfer medium fluid 1 circulating in the inside and the temperature-controlled body 3 via the thin-walled wall. The exchange unit 2 is configured as the heat exchange fin by directly applying the thin tube group of the meandering long thin tubes 1-2 as heat exchange fins, and is supplied from outside the system by the forced convection generating means F provided in the supply passage. The gaseous phase heat transfer medium fluid A that is sent to and discharged from the heat exchanger 2 as forced convection outside air and the two-phase condensable heat transfer medium fluid 1 that circulates in the meandering long thin tube 1-2 pass through the thin tube wall. It is configured as a gas-liquid heat exchanger E in which the amount of heat is exchanged between them. Such a loop-shaped circulation pipe of the two-phase condensable heat transfer fluid is configured as a highly reliable meandering thin-tube heat pipe, and exhibits high performance for a long period of time.

In FIG. 1, the gas-liquid heat exchanger E is shown in a plan view for simplification of the drawing, and each thin tube unit u- of each unit meandering thin tube formed by the meandering long thin tube 1-2. 1, u
Although -2, u-3,..., U-n are shown in a plan view, a large number of them are actually arranged in a row in a plan view, and as a side view of FIG. Only the first layer on the side is shown. Similarly, a large number of inlet headers 8 and outlet headers 9 are provided. Similarly, not only a single solid-liquid heat transfer device H as shown in the figure, but also a large number may be used.

Therefore, it is presumed that the closed system temperature controller of the present invention can withstand continuous long-term use up to the limit of the life of the completely sealed pump for circulating the refrigerant liquid. This means that in the closed system temperature controller according to the present invention, the liquid quality preserving means or the ultrapure water producing device 15 in the conventional closed system temperature controller illustrated in FIG.
It is possible to omit the refrigerant liquid supply tank 16, the drain pad 17, and various safety devices associated therewith,
As shown in FIG. 1, the structure of the device housing for storing the entire system is simplified, the reliability of the system is improved, and the size can be significantly reduced.

Second Embodiment In many cases, a heat-generating component is mounted in an equipment housing in addition to a temperature-controlled body targeted for a closed system. In the closed system according to the present invention, the amount of heat leaked from the pipe line is greatly reduced due to the effect of the present invention, which greatly reduces the amount of heat leaked from the pipe line of the heat medium fluid circulation system. Therefore, the influence of the amount of heat leaked and the amount of heat generated by the heating elements other than the temperature-controlled body increases, and the internal temperature of the housing greatly increases. In particular, when the casing is a hermetically sealed casing in which the inside atmosphere and the outside atmosphere are hermetically isolated, the temperature rise becomes extremely large, and it is necessary to discharge the accumulated heat to the outside of the casing. FIG. 4 shows a structure of a closed system gas-liquid heat exchanger E in such a closed housing according to a second embodiment. For the sake of simplicity, the meandering tubules are all shown in a diagram. The case C in the figure is a closed case, and the heat exchange part 2 of the gas-liquid heat exchanger E is provided in a wind tunnel 1 provided outside the case.
1 and is hermetically mounted on the housing wall. A predetermined group in the meandering thin tube group 1-2 in the heat exchange section 2 is extended in length of the thin tube, penetrates the housing wall, and is protruded into the closed housing C. The group of meandering thin tubes 1-2i is configured as a natural convection type or forced convection type internal heat exchanger Ei for cooling air in a closed casing. In the case of forced convection type, the group of internal thin tubes 1-2i is formed. Is characterized in that a forced convection generating means for sending / discharging forced convection Ai of air in the casing into / from the internal heat exchanger Ei is provided. With such a configuration, the amount of heat generated from the attached components in the closed casing C and the amount of heat leaked from the closed system are transferred to the gas-liquid heat exchanger E via the group of internal meandering long thin tubes 1-2i. Sent to
Further, the gas is discharged out of the closed casing C via the gas-liquid heat exchanger E. The retention of such heat in the closed casing C has the same effect as the reduction in the cooling efficiency of the gas-liquid heat exchanger E, and the size of the gas-liquid heat exchanger E needs to be increased. Such a closed system liquid cooling device according to the second embodiment makes it possible to completely maintain the airtightness of the housing, keep the inside of the housing C clean, and prevent the temperature inside the housing from rising. The reliability of the mounted components inside the housing C is improved.

Third Embodiment Since the closed system temperature control device according to the present invention is an application system of a loop type meandering thin tube heat pipe, it is checked in a loop by the operation principle of Japanese Patent Publication No. 6-3354, which is the basic patent. By disposing the valve, the heat medium fluid circulates in a predetermined direction by itself. In Japanese Patent Publication No. 6-3354, the number of check valves provided is small, but by increasing the number of check valves, the number of pressure chambers divided by the check valves is increased. It operates as a simple fluid pump, and the circulation driving force of the heat medium fluid becomes strong as a whole. Thus, the completely sealed pump 5 of the first embodiment shown in FIG. 1 can be omitted or an auxiliary small pump can be used. The third embodiment of the present invention will be described with reference to the perspective view of FIG. In the figure, all the thin tubes are shown in a diagram for the sake of simplicity. Each unit unit u-1 and u- of the meandering long thin tube 1-1 constituting the heat transfer unit 1 shown in FIG.
An inflow check valve V-1 is attached to a portion of each of the units 2,..., U which is close to the heat medium fluid inlet 6, or is close to each heat medium fluid inlet 6 of each unit. The inlet check valve V-1 is attached to the portion where the heat medium fluid is discharged, and the outlet check valve V-2 is also attached to the portion near each heat medium fluid outlet 7. And these check valves V
Is characterized in that the flow direction regulating direction coincides with the direction from the inlet 6 to the outlet 7 of the heat medium fluid.

In the case of such a configuration, the heat generated in the meandering long thin tube 1-1 by the heat absorption of the calorie transfer unit 1 causes the pressure generated in the axially bidirectional direction due to the nucleate boiling of the heat transfer fluid l generated in the meandering long thin tube 1-1. The waves are all converted into pressure waves in the forward direction with respect to the circulating flow by the action of the inflow check valve V-1, and all of the pressure waves become forward pressure waves and act as circulation driving forces of the heat medium fluid. In addition, vapor bubbles generated by nucleate boiling are all sources of the circulation driving force of the heat medium fluid by the action of the check valve V-1.
When the discharge check valve V-2 is additionally provided, the backflow of the heat transfer fluid caused by the instantaneous contraction of the steam bubbles due to the instantaneous temperature drop due to the adiabatic expansion when the steam bubbles are generated is prevented, and the circulation propulsion force is further enhanced. There is action.

Fourth Embodiment A fourth embodiment of the present invention will be described with reference to the perspective view of FIG. The present embodiment relates to a solid-liquid heat transfer device H having a cold plate type heat transfer unit 1. In this figure, for the sake of simplification of the drawing, the meandering long thin tube 1-1 is shown in a diagram like the other figures. In the figure, a calorie transfer unit 1 is provided with each unit thin tube unit u-1, u-2, u- of the meandering long thin tube 1-1.
,..., U-n and the linear part group of the meandering tubule forming each unit are all arranged in parallel and parallel so as to form the same plane, and the plane has good thermal conductivity. Cold metal is sandwiched between two flat metal plates 10-1 and 10-2, or embedded in a group of grooves cut into the flat metal plates 10-1 and 10-2, and bonded to form a flat cold plate as a whole. The temperature control unit 3 is bonded and mounted on a plane of the cold plate 10 by means having good heat conductivity, and is configured as a solid-liquid heat exchange device H as a whole. Features.
Even if there is some unevenness in the gap between the thin tubes in the group of straight portions of the meandering thin tubes, or even if there is some unevenness in the flow rate of the heat transfer fluid flowing through each of the thin tubes, the cold plates 10-1 and 10-2 diffuse the heat so that the cold plates 10 are not diffused. Each part of the flat surface exhibits uniform heat transfer performance. The cold plate 10 configured as described above has a large number of heating elements mounted on the same printed wiring board and having the same height, that is, when the tops of the heating elements form a plane as a whole, they are collectively mounted on the cold plate 10. This is extremely effective when cooling all at once on a flat surface, or when mounting a large number of heating elements directly on the flat surface of the cold plate 10 to cool them all at once.

Fifth Embodiment A fifth embodiment of the present invention will be described with reference to the perspective view of FIG. This embodiment also relates to a solid-liquid heat transfer device H having a cold plate type heat transfer unit 1. This figure also shows a diagram of the meandering long narrow tunnel 1-3 for simplification of the drawing. In the figure, a calorie transfer unit 1 is a meandering long thin tube 1-.
1 each unit capillary unit u-1, u-2, u-3, ...
All of the straight-line groups of the meandering tubule forming the unit, u-n and each unit are arranged in parallel and in parallel and aligned on the same plane, and have substantially the same shape as a planar body including its turn part. Is formed in a metal plate 10-1 having good heat conductivity, and is configured as a cold plate 10 as a whole. It is characterized in that the temperature-controlled body 3 is bonded and mounted on the plane 10 by means having good heat conductivity, and is constituted as a solid-liquid heat exchange device H as a whole. Since the solid-liquid heat exchange device H having such a configuration can reduce the curvature of the turn portion to a fraction of that of the thin tube bending, the pattern can be arranged at a high density. It is possible to greatly improve the heat transport performance or reduce the size of the heat transfer unit 4 as compared with the case of the example. Further, since the small-diameter tunnel 1-3 does not require the wall thickness of the tube as compared with the thin tube, the thickness of the cold plate 10 can be sufficiently reduced even with the same diameter.
Further, in the fourth embodiment, the thin tube group and the metal flat plates 10-1 and 10-1
Since the contact thermal resistance between 0 and 2 does not occur, the cold plate 10 having a high-performance heat-conducting and heat-diffusing performance can be constructed. Such a thin high-performance cold plate 10 is extremely effective when applied to high-density mounting equipment. Such a fifth embodiment contributes to the reduction in size and weight of the closed system temperature control device of the present invention.

Sixth Embodiment The present invention relates to a means for circulating a heat transfer fluid as disclosed in Japanese Patent Application No. Hei.
A high performance is achieved by applying a loop-shaped meandering thin tube heat pipe of a separated type of heat receiving and radiating portion, which is applied to Japanese Patent No. 319461 or Japanese Patent Publication No. 6-3354. However, a gas-liquid heat exchange section corresponding to a heat radiating section of a heat pipe is disclosed in Japanese Patent Application No. 4-135507.
No. (sword-shaped heat sink having l-shaped pins),
In addition, by applying and applying Japanese Patent Application No. 4-214456 (application structure of a sword mountain type heat sink), further downsizing and higher performance can be achieved. The structure of the gas-liquid heat exchanger of the sixth embodiment having such a configuration will be described with reference to FIG. FIG. 7 is a perspective view in which parts other than the heat exchange part are omitted, and is shown so that the internal state can be seen by removing a part of the convection control wind tunnel 11 and the device housing C. For the sake of simplicity of the drawing, meandering thin tubes are shown in a diagram. The groups of straight pipe sections of the meandering long thin tubes 1-2 in the heat exchange section 2 are arranged in parallel and parallel to each other and at high density, and the groups of straight pipe sections are arranged in the longitudinal direction. At a position close to one end of the tube, the plate is held upright on the plane by a predetermined flat plate-shaped holding means 2-1 and is turned at the tip of each of the tubes of this group of upright tubes. When each pair of thin tubes connected by a curved tube is regarded as a single pin, the heat exchange unit 2 as a whole is regarded as a sword mountain-shaped body formed on the plane of the holding means 2-1. The holding means 2-1 holds the group of upright tubules in the shape of a sword mountain and the two flat surfaces are formed airtight from each other. From the vicinity to a position slightly protruding from the tip of the group of upright thin tubes, A convection control wind tunnel 11 is provided so as to cover the outer circumference of the tube group, and the flow direction of the forced convection A of the vapor-phase heating medium fluid sent into the heat exchange unit 2 is entirely around the plane of the holding means 2-1. Flow from the direction along the plane of the holding means 2-1 toward the center thereof, and change the direction from the center toward the tip of the group of sword-shaped tubules, or hold from the tip of the group of sword-shaped tubules. Means 2
-1 is directed toward the plane, the flow is changed in the direction after the collision with the plane, and is directed in all directions around the plane, and is configured as a gas-liquid heat exchanger E as a whole. The heat exchanger E is air-tightly mounted on the outer wall surface of the closed casing C by the flat holding means 2-1. In the case of heat exchange in which convection perpendicular to the thin tube group flows in only one direction as in a normal radiator, the temperature of the convective heat transfer fluid rises due to heat exchange on the upstream side, and the heat exchange efficiency decreases as it goes downstream. In general, the overall heat exchange efficiency is reduced. However, in the case of the present embodiment, the flow of the convective heat transfer medium fluid flows in from all directions or is discharged in all directions, so that the heat exchange efficiency is little reduced and the heat exchange efficiency is greatly improved as a whole.

[0026]

According to the present invention, the two-phase heat medium fluid which is divided by the bubbles generated in the loop-shaped meandering thin tube heat pipe, and the bubbles and the droplets are alternately arranged and circulates by themselves is forced to generate bubbles by the fluid pump. The heat exchange capacity of the liquid-solid heat exchange unit corresponding to the heat receiving unit and the gas-liquid heat exchanger corresponding to the heat radiating unit have both greatly improved heat exchange capacity, and the entire liquid cooling circulation loop becomes a heat pipe. By this, the liquid supply tank,
The liquid quality preserving device, drain pad, and other accessories are omitted, and the whole system is further reduced in size and weight, and the structure is simplified, so that the system can be easily maintained. Since there is no liquid leakage, the inside of the device is kept clean, and the system can be stored in a completely sealed device housing.

[Brief description of the drawings]

FIG. 1 is an explanatory diagram showing a basic principle of a closed system temperature control device according to the present invention and a structure of a first embodiment.

FIG. 2 is an explanatory diagram showing a configuration of a conventional closed system liquid cooling device.

FIG. 3 is an explanatory view showing a structure of a conventional heat pipe having a separated heat receiving / radiating section.

FIG. 4 is an explanatory view showing the structure of a gas-liquid heat exchanger of a second embodiment of the closed system temperature controller according to the present invention.

FIG. 5 is a perspective view showing the structure of a solid-liquid heat transfer device of a third embodiment and a fourth embodiment of the closed system temperature controller according to the present invention.

FIG. 6 is a perspective view showing the structure of a solid-liquid calorie transfer device of a fifth embodiment of the closed system temperature controller according to the present invention.

FIG. 7 is an explanatory view showing a structure of a gas-liquid heat exchanger of a sixth embodiment of the closed system temperature controller according to the present invention.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 heat transfer section 1-1 meandering long thin tube 1-2 meandering long narrow tube 1-2i internal meandering long thin tube 1-3 meandering long narrow tunnel 2 heat quantity exchanging section 2-1 holding means 3 temperature controlled body 4 -1 Low temperature connecting pipe 4-2 High temperature connecting pipe 5 Completely sealed pump 6 Inlet 7 Outlet 8 Inlet header 9 Outlet header 10 Cold plate 10-1 Metal plate 10-2 Metal plate 11 Convection control means (wind tunnel) 11i Internal convection control means (Internal wind tunnel) Ao Forced convection outside air Ai Internal forced convection air A Gas-phase heating medium fluid C Equipment housing c Condenser (radiator) e Steam generator (heat absorber) E Gas-liquid heat exchanger Ei Internal heat exchanger F Forced convection generation means Fi Internal forced convection generation means H Solid-liquid heat transfer device (liquid-cooled heat absorber) L Refrigerant liquid 1 Two-phase condensable heat transfer fluid 1-1 Condensed working fluid 1-2 Gas Phase hydraulic fluid un single V-1 Inlet check valve V-2 Outlet check valve

Continuation of the front page (56) References JP-A-64-41792 (JP, A) JP-A-4-148189 (JP, A) JP-A-4-52495 (JP, A) JP-A-53-37938 (JP) JP-A-1-111198 (JP, A) JP-A-62-252892 (JP, A) JP-A-5-315482 (JP, A) JP-A-60-2841 (JP, U) 6-3354 (JP, B2) (58) Field surveyed (Int. Cl. ⁶ , DB name) F28D 15/02

Claims (1)

(57) [Claims] 1. A closed system temperature of a separated type of a heat receiving and radiating portion for controlling the temperature of a temperature controlled body in an equipment housing.
This system is a degree control device , and this system is a solid-liquid heat transfer device that transfers heat between the temperature controlled body and the two-phase condensable heat transfer fluid, and a heat transfer that is transferred by the two-phase condensable heat transfer fluid. A gas-liquid heat exchanger that exchanges heat with forced convection of the outside air, a connecting pipe that connects them in a closed loop, and a two-phase condensable heat transfer fluid sealed in the loop in a predetermined direction. The main component is a pump for forced circulation of the heat medium fluid that circulates through the system, and all of these system components are stored in the device housing circle in principle except for the heat exchange part of the gas-liquid heat exchanger, The heat exchange unit is disposed so as to be located in a circular portion of the device housing or in convection control means provided outside, and a portion corresponding to the heat exchange unit and the heat exchange unit is made of a metal having good heat conductivity. A long snake with a maximum outer diameter of 5 mm or less It is composed of a thin tube, and its inner diameter is always filled with the heat medium fluid flowing through it due to the cohesive force generated by its surface tension, even if the amount of sealing is very small. Regardless of the state, the inside diameter is sufficiently small so as to move inside the tube in that state, and such a long thin tube is reciprocally meandered over a predetermined distance, and a large number and a predetermined number of each are set. The meandering long thin tubes, which are configured as a calorie exchange unit and a calorie exchange unit composed of the number of meanders, and constitute a calorie exchange unit and a calorie exchange unit located at a predetermined distance, respectively, have a meandering number of times. It is formed as a unit unit for each turn and is an aggregate of a plurality of unit units as a whole, both ends of each unit unit are an inlet and an outlet of a two-phase condensable heat transfer fluid, respectively. All unit units The heat medium fluid inlet port group and the discharge port group are air-tightly connected to the inlet header and the outlet header, respectively, and the inlet header and the outlet header connect the heat transfer section and the heat exchange section with a predetermined amount. A high-temperature connecting pipe and a low-temperature connecting pipe that are connected at a distance from each other are air-tightly connected. The high-temperature connecting pipe air-tightly connects the discharge header of the heat exchange section and the inflow header of the heat exchange section. Is airtightly connected to the discharge side header of the heat exchange section and the inflow side header of the heat exchange section, is configured as a closed container of a closed lube pipeline as a whole, and a predetermined portion of the low-temperature connection pipe includes: Yes completely sealed pump for heat transfer fluid forced circulation structure without contaminating the heat transfer fluid with capable of operating while maintaining a highly airtight coupled arranged in an air-tight, the complete sealing pump Is
The driven part is connected between the solid-liquid heat exchange device and the gas-liquid heat exchanger.
It is disposed in a connecting pipe connecting between the
Is disposed outside the connecting pipe , and the driven part is
This is configured to be driven by electromagnetic force from
Is driven out of the closed loop line and completely sealed
It is characterized by being an electromagnetic fluid pump
Enclosure forming a closed loop conduit configured as described above
Tena within a predetermined amount of a given two-phase condensable heating fluid medium after evacuated to a high vacuum is sealed, 受放thermal unit separated Le overall
Yes is configured as-loop type meandering capillary tube heat pipe, two-phase condensable heating fluid medium is a hydraulic fluid in the loop meandering capillary tube heat pipe is in the direction toward the inflow side of the heat exchange portion from the discharge side of the heat exchange section It is forcibly circulated by the above-mentioned complete seal type pump, and a temperature controlled body is adhesively mounted on a predetermined portion of the heat transfer section by a predetermined means having good thermal conductivity, and circulates in the meandering thin tube. The heat exchange unit is configured as a solid-liquid heat exchange unit in which heat is exchanged between the two-phase condensable heat transfer fluid and the temperature-controlled body through the thin-wall wall. Configured as a heat exchanger,
A gas-phase heat transfer medium fluid supplied from outside the system and sent to and discharged from the heat exchanger as forced convection, and a two-phase condensable heat transfer medium fluid circulating in the meandering thin tube generate heat between the two via the thin tube wall. A closed system temperature controller configured as a gas-liquid heat exchanger to be replaced.