JPH01189496A - Loop tube heat transfer device - Google Patents

Abstract

PURPOSE:To expand the applicability range and diversify the fields of application by producing as an internal pressure differential between the heat-absorbing and heat-releasing sections, which is indispensable to spontaneous circulation of a heat-carrying fluid, a pressure differential between the equilibrium hydrogen pressure of a hydrogen-occluded alloy generated by a high temperature at the heat-absorbing section and that generated by a low temperature at the heat-releasing section. CONSTITUTION:The heat-carrying fluid employed is a fluid obtained by mixing hydrogen gas with a designated fluid in the liquid state which consists of a fluid forming a disperse system with addition of a designated finely pulverized hydrogen-occluded alloy. This heat- carrying fluid is given, despite changes in phase, an internal pressure differential due to equilibrium hydrogen pressure between the heat-absorbing and heat-releasing sections; the release of hydrogen produces pressure waves so that a pressure chamber formed by a circulation direction control means 2 develops breathing and the circulation direction control means 2 itself a vibration between opening and closure, thus the heat-carrying fluid 4 gaining a vigorous propulsive force enabling it to circulate through a loop type conduit. Carried by the circulating flow, the hydrogen-occluded powder alloy, as it passes the heat-absorbing section 1-H, releases hydrogen and simultaneously absorbs a quantity of heat as latent heat, whereas, as it passes the heat-releasing section 1-C, it absorbs hydrogen and simultaneously releases a quantity of heat as latent heat. The circulating fluid absorbs also sensible heat at the heat-absorbing section 1-H and releases sensible heat at the heat-releasing section 1-C.

Description

DETAILED DESCRIPTION OF THE INVENTION A.6 OBJECTS OF THE INVENTION [Field of Industrial Application] The present invention relates to a novel structure for improving the performance of loop tube heat pipes and similar heat transfer devices. The present invention also relates to the structure of a heat transfer device that effectively utilizes the temperature-equilibrium hydrogen pressure characteristics and heat absorption and heat radiation characteristics of a hydrogen storage alloy.

[Prior art]

The inventor has published a "loop type thin tube heat pipe" in Japanese Patent Application No. 155747/1982, and also in Japanese Patent Application No. 266265/1982.
In this issue, we proposed a ``heat transfer device'' and are putting it into practical use. All of them are shown in the partially cross-sectional diagram shown in FIG.
Both ends of the pipe itself having a curved pipe part are connected to each other to form a loop pipe type container l, and at least one part of the container has a heat receiving part 1-H, and at least one other part has a heat dissipating part. A section 1-C is provided, which are configured to receive and radiate heat by heating means H and cooling means C, respectively, and a predetermined amount of a predetermined heat transfer fluid 4 is sealed in the container. The heat transfer fluid 4 circulates spontaneously in a certain direction due to the interaction of the temperature difference between the circulation direction regulating means 2 provided at at least one location in the loop-shaped flow path and the heat receiving/radiating section. They are common in that they are heat transfer devices that transport heat from 1-H to heat radiating section 1-C. Furthermore, they are also common in that, in principle, at least a portion of the heat transfer fluid circulates while undergoing a phase change between gas and liquid. If the circulation direction regulating means in such a heat transfer device is a check valve, vibration of the valve body is controlled by electromagnetic means or magnetic means inside the container or around the container in the area indicated by the broken line 3 in the figure. They are also common in that their performance can be improved by controlling them. Heat transfer in such a heat transfer device is carried out by the circulation of a heat carrier fluid, which is a heat carrier.The principle of generating the circulation flow is as follows. Met.

(a) The inside of the loop tube type container can be considered to be divided into a plurality of pressure chambers by the plurality of circulation direction regulating means. The evaporation and condensation rates and the resulting saturated vapor pressures of the heat transfer fluid (at least a portion of which is a two-phase condensable fluid) in each pressure chamber are not equal. Furthermore, the amount of latent heat and sensible heat transferred and received on the inner wall surface of the container and the resulting temperature changes are also uneven. These inequalities cause differences in the total pressure within each pressure chamber. This pressure difference causes the circulation direction regulating means to open and close. - Once the opening/closing operation occurs, the steam in one pressure chamber is adiabatically expanded, the steam in the other pressure chamber is adiabatically compressed, and a sudden change in temperature and internal pressure occurs in the side pressure chamber. Such an operation successively spreads to the pressure chambers on the downstream side, and each pressure chamber spontaneously generates a breathing action and an opening/closing vibration action of the circulation direction regulating means.

This breathing action provides a directional driving force to the heat transfer fluid.

(b) The nucleate boiling that occurs in each heat receiving section includes both evaporation and bumping, and bumping generates pressure waves (or shock waves) in the heat transfer fluid. This pressure wave instantaneously closes the upstream circulation direction regulating means and instantaneously opens the downstream circulation direction regulating means. This rapid opening/closing further generates secondary pressure waves, which circulate at high speed within the loop tube type container while sequentially spreading to the downstream pressure chamber. Since such pressure waves are generated randomly and continuously in each heat-receiving section, the circulation direction regulating means continues to open and close in a vibrating state, thereby providing a driving force to the heat-carrying fluid. Such opening/closing vibration of the circulation direction regulating means due to pressure waves occurs even if the circulation direction regulating means is disposed at only one location.

(c) The condensable fluid is vaporized in the heat receiving section to generate a high saturated vapor pressure, and condensed and liquefied in the heat radiating section to generate a low saturated vapor pressure. Therefore, this pressure difference provides a driving force to the heat transfer fluid from the heat receiving section to the heat radiating section. On the other hand, since the movement of the heat transfer fluid is regulated by the circulation direction regulating means, it can only move downstream in the regulated direction. That is, the heat transfer fluid within the loop tube type container is circulated from the heat receiving section to the heat radiating section located downstream thereof. This effect works in the same way even if there is only one circulation direction regulating means provided in the loop tube type container, and even if there are many heat receiving and radiating parts provided in the loop. In this case, even if the heat radiating section is located close to the upstream side of the heat receiving section, the heat transfer fluid cannot flow backwards and is propelled toward the far downstream heat radiating section. The circulating flow generated by such a difference in internal pressure between the heat receiving and discharging parts is the basis of the operation of the loop tube type heat transfer device.

(d) Due to the above actions, strong inertia is imparted to the heat transfer fluid once circulation has started, and as a result, an expansion part and a compression part are created at the upstream and downstream ends of the pressure chamber when the circulation direction regulating means is opened and closed. It amplifies the opening/closing vibration and strengthens the circulation propulsion force.

The circulating flow of the heat transfer fluid that naturally occurs as described above is caused by (a), (b), and (c) any of the driving factors, but basically the circulation direction regulating means (in the case of a check valve, the valve It is generated by the opening/closing vibration of the body. In other words, in order to generate a strong propulsive force, it is necessary to close, and in order to obtain a sufficient flow rate from the propulsive force, it is necessary to open, and opening and closing vibration is an essential condition for generating circulating flow. . In order for the circulation flow to continue even while the valve is closed, the fluid within the pressure chamber must be in a gas-liquid two-phase state or in a vacuum foam mixture state, and the cushioning action of these smooths out the opening and closing vibrations.

There are various types of circulation direction regulating means 2, some of which are shown in FIG. 2(a) (t+). (A) is a normal ball valve type check valve, 2-1 is a valve seat, 2-2 is a spherical valve body, and 2-3 is a stopper/pa. This type is reliable in reverse action, and by using ferromagnetic material for the valve seat and valve body, the valve body can be moved from the outside by electromagnetic means or magnetic means.
There is an advantage that the opening/closing vibration of -2 can be controlled. However, it is necessary to pay attention to the occurrence of failures due to wear of the valve body 2-2 and stopper 2-3 over many years. In (b), the fluid resistance is close to zero against the flow in the direction of gradual cross-section reduction of the circulation direction regulating nozzle 2-4, and large fluid resistance is exhibited against the flow with rapid cross-section reduction in the opposite direction. The circulation direction is regulated in the direction of the arrow.

In this case, there is no wear part, so even if the heat transfer fluid is a fine powder dispersed liquid, it has the advantage of guaranteeing a long life.
Although there is an advantage that the flow velocity can be increased due to the inertia of the circulating fluid, there is a disadvantage that the initial propulsive force is weak because the check force is weak. In the case of (II), the above-mentioned valve body opening/closing vibration action can be considered to be caused by the fluid at the tip of the circulation direction regulating nozzle 2-4 producing vibration similar to that of the valve body.

[Problem that the invention seeks to solve]

Patent Application No. 155747/1982 and Patent Application No. 2662/1982
In the loop tube type heat transfer device according to No. 65, heat transfer is carried out by spontaneously circulating the heat transfer fluid sealed in the container as described above, but its operation has the following problems. there were.

(a) Operation is difficult when the temperature of the heat receiving part is low and when the heat input is small.

If the loop tube container is a thin tube, the pressure loss inside the tube is large, so it is necessary to increase the internal pressure of the container. Similarly, if the water level in the heat receiving section is significantly higher than the water level in the heat dissipating section, it is necessary to overcome gravity and circulate the heat transfer fluid. Therefore, it is necessary to increase the internal pressure of the container. If the circulation direction regulating means is a check valve type and the valve body has a large mass or a large specific gravity, it is necessary to increase the internal pressure of the container in order to provide sufficient opening/closing vibration. Similarly, when the distance between the heat receiving part and the heat radiating part is long, it is necessary to increase the container internal pressure. In these cases, if the temperature of the heat receiving part is low or the heat input is small, the internal pressure of the container will be insufficient and operation will be difficult. - As an example, actual measurement when the heat transfer fluid is pure water when the inner diameter is 2fl, the total length is 20m, and each turn has a length of lOOmmO heat receiving section and heat dissipating section in a 20-turn meandering loop tube type heat transfer device. The results show that the heat input is less than 50W.
Difficulty in operation was observed when the heat receiving part temperature was below 50°C, and when the heat transfer fluid was Freon 11, it was found to be difficult to operate when the heat input was below 30 W and the heat receiving part temperature was below 40°C.

(b) The temperature difference between the heat receiving part and the heat radiating part is large compared to a conventional heat pipe.

In order to provide a circulation propulsion force to the heat transfer fluid, it is necessary not only to simply increase the internal pressure of the container, but also to create an internal pressure difference between the heat receiving and radiating parts, and for this purpose, a temperature difference between the heat receiving and radiating parts is required.

This temperature difference is necessarily greater than the temperature difference required to move the working fluid vapor in a conventional heat pipe. Even when the heat input is large, this temperature difference does not need to increase in proportion to the heat input, and may be increased by a relatively small amount. Therefore, the thermal resistance of the loop tube type heat transfer device during heat transfer is larger than that of the conventional heat pipe in the small input and low IjL region (bad <).
, it has the characteristics of being smaller (better) than conventional heat pipes in large input and high temperature regions.

The actual measured value of the above-mentioned meandering loop type heat transfer device with an inner diameter of 2 mm is a heat input of 5 when the temperature of the heat dissipation part is 18°C and the heat transfer fluid is pure water.
Thermal resistance at 0W heat receiving part temperature 50℃ is 0.64℃/W
and 0.04℃/W at tsoow, 78℃
Met. Similarly, in the case of Freon 11, 30W, 40℃
The thermal resistance at 1500W is 0.73'C/W.
, 0.045"c/W at 85℃.On the other hand, in the case of a conventional heat pipe with an inner diameter of 9 mm and the same cross-sectional area as 20 heat receiving parts with an inner diameter of 21 mm, the pure water working fluid was 50 W.
, the thermal resistance at 40°C is 0.44°C/W, and 15
It was 0.068°C/W at 00W and 120"C. Similarly, the thermal resistance at 30W and 35°C of Freon 11 working fluid was 0.57°C/W, and 0.092°C/W at 100OW and 110°C. Met.

The present invention solves the above-mentioned problems (a) and (b), improves the low-temperature performance of the loop tube heat transfer device, and reduces the temperature difference between the heat receiving and radiating parts.

9. Structure of the Invention [Means for Solving the Problems] The means for solving the problems in the present invention lies in the effective use of the characteristics of the hydrogen storage alloy. The characteristics used are the temperature dependence of equilibrium hydrogen pressure and the heat absorption and release characteristics during hydrogen absorption and release.
It is a characteristic.

In the present invention, as a means to effectively utilize these two characteristics, a means for regulating the circulation direction of the heat transfer fluid is provided by a high equilibrium hydrogen pressure when hydrogen is released due to the high temperature of the heat receiving part and a low equilibrium hydrogen pressure when hydrogen is absorbed by the heat dissipating part. Gives 11 points of momentum in the direction of regulation,
A circulating flow is generated naturally in the heat transfer fluid, or a circulating force of the heat transfer fluid is assisted. In addition, the heat receiving ability is assisted by the heat absorption characteristic when hydrogen is released in the heat receiving section, and the heat radiating ability is assisted by the heat radiating characteristic when hydrogen is absorbed in the heat radiating section.

There are two types of application methods for the above-mentioned utilization methods: a method in which equilibrium hydrogen pressure is generated in the fine powder of hydrogen storage alloy that is dispersed in the heat transfer fluid and circulated in the loop pipe container, and There is a method in which equilibrium hydrogen pressure is generated in a hydrogen storage alloy layer formed on the wall surface.

[For production]

Conventional condensable fluids, when used as heat transfer fluids or mixed with heat transfer fluids, have a limited operating temperature range due to their inherent boiling points. Also, there is a large difference in performance depending on the saturated vapor pressure within the operating temperature range. On the other hand, when hydrogen storage alloys are used in the manner described above, the operating temperature range can be freely selected from a wide range of 120°C to 400°C, depending on the types and proportions of the components. . Further, the equilibrium hydrogen pressure generated within the temperature range can be selected from a high pressure of several tens of atmospheres to a low pressure of 0.5 atmospheres.

Therefore, the loop tube type heat transfer device according to the present invention cannot achieve sufficient performance with conventional heat pipes or conventional loop tube type heat transfer devices. and temperature range from 250℃ to 300℃・
, it complements them to enable high-performance heat transfer. Furthermore, since it becomes easy to provide a sufficiently large internal pressure difference between the heat receiving and dissipating parts, it becomes easy to provide a loop tube type heat transfer device with an inner diameter of 1 mm or less, which has been difficult to achieve in the past. Furthermore, even with the same inner diameter, it is possible to provide a loop tube type heat transfer device in which the distance between the heat receiving and radiating parts is sufficiently increased compared to the conventional one. In addition, since a sufficient internal pressure difference between the heat receiving and dissipating parts can increase the circulation flow rate of the heat transfer fluid, it is possible to construct a loop tube type heat transfer device with a larger capacity and lower thermal resistance than before even if the inner diameter is the same. . Another noteworthy feature is that by selecting an alloy with a steep temperature-equilibrium hydrogen pressure curve, a sufficient internal pressure difference can be obtained even when the temperature difference between the heat receiving and dissipating parts is small, and good performance can be achieved. A loop tube type heat transfer device can be provided.

Hydrogen storage alloys absorb a large amount of heat when releasing hydrogen, and release a large amount of heat when absorbing hydrogen, so in addition to the heat transport ability of sensible heat due to the circulation of the heat transfer fluid, it is possible to absorb and release latent heat by absorbing and releasing hydrogen. The loop tube type heat transfer device according to the present invention provides an extremely high overall heat transfer capability and can solve all of the problems of the prior art.

〔Example〕

First Embodiment In the first embodiment, a mixed fluid of gaseous hydrogen and a predetermined liquid fluid is used as the predetermined heat transfer fluid in the basic structure of the present invention, and the predetermined liquid fluid is a predetermined hydrogen storage alloy. It is characterized by being a fluid containing dispersed fine powder. This application does not require any modifications to the loop tube container. Furthermore, it is essential that the liquid fluid and the hydrogen storage alloy are mutually stable in the presence of atomic active hydrogen released from the hydrogen storage alloy.

For example, hentane (C9H12), hexane (c6111
4) Liquid methane series hydrocarbons such as heptane (C7HI6) are chemically extremely stable, satisfy the above essential conditions for almost all hydrogen storage alloys, and have appropriate physical properties as heat transfer fluids. are doing. Therefore, by selecting a combination with an appropriate hydrogen storage alloy, it is possible to formulate a heat transfer fluid that generates an equilibrium hydrogen pressure suitable for the structure and application conditions of the loop tube type heat transfer device.

The gaseous hydrogen mixed into the heat transfer fluid does not necessarily need to be specifically injected into the container, and may be released from the hydrogen storage alloy. Such surplus hydrogen imparts elastic expansion and compressibility to the heat transfer fluid, thereby facilitating the opening and closing vibration of the circulation direction regulating means and smoothing the circulation by utilizing the inertia of the heat transfer fluid.

In this embodiment, the hydrogen released from the alloy powder is reabsorbed by the cooling effect of the heat dissipation section through circulation and is not consumed. Hydrogen is only used by its equilibrium hydrogen pressure and latent heat during release and inhalation. Therefore, only a small amount of fine powder is needed.

Additionally, hydrogen storage alloys generally have the property of being pulverized due to expansion and contraction during hydrogen absorption and release, which poses a problem in molding, and a decrease in thermal conductivity due to pulverization is also an important problem when using hydrogen storage alloys. was. However, in this example, the pulverization of the alloy improves the dispersibility within the heat transfer fluid, and also improves the heat transfer between the heat transfer fluid and the fine powder (hydrogen storage alloy), and the loop tube type The performance of the heat transfer device will be improved.

Although the heat transfer fluid in this example does not necessarily have to be a condensable two-phase fluid, the boiling condensation of the two-phase fluid in the heat receiving and radiating section stirs the heat transfer fluid and improves the dispersion of the hydrogen storage alloy powder. In addition, there is an effect that the latent heat of the fluid can be used in combination.

Regardless of whether the heat transfer fluid undergoes a phase change or not, the heat transfer fluid in this embodiment generates an internal pressure difference due to the equilibrium hydrogen pressure between the heat receiving and dissipating parts, generates a pressure wave due to hydrogen release, and the pressure formed by the circulation direction regulating means. The chamber generates a breathing action, and the circulation direction regulating means generates opening/closing vibrations, whereby the heat transfer fluid obtains a strong circulation propulsion force and spontaneously circulates within the loop-shaped channel. Due to the circulating flow, the hydrogen storage alloy powder releases hydrogen every time it reaches the heat receiving part 1-H in the loop tube heat transfer device illustrated in FIG.
Each time it reaches c, it absorbs hydrogen and at the same time releases heat as latent heat. The circulating flow also absorbs the sensible heat of the heat receiving part 1-11,
The sensible heat is also released in the heat radiation section 1-C. That is, the heat transfer fluid according to this embodiment is specially adapted to the working fluid of the "loop type capillary heat pipe" in No. 62-155747 and the patent application No. 62
It exhibits exactly the same behavior as the heat transfer fluid of the "heat transfer device" in No.-266265. Therefore, the heat transfer device according to this embodiment uses a heat transfer fluid that circulates according to the same principle as the heat transfer fluid wi ring principle (a), (b), (c), and (d) in the above-mentioned [prior art]. be activated. Other effects in this example are as described in [Effects].

In this embodiment, the heat transfer fluid is circulated by dispersing the fine alloy powder as shown in FIG.
This may accelerate the wear of the stopper 2-3.
As the circulation direction regulating means, 2-4 in Fig. 2 (0) is used.
It is desirable to use a circulation direction regulating nozzle such as .

Second Embodiment In this embodiment, as illustrated in FIG.
The heat receiving section 1-H and the heat dissipating section 1-C provided in the
A heating means 6 and a cooling means 7 are attached to each of the heat receiving part 1-Hc and the heat radiating part ICh, and at every predetermined time, one of them is used as the heat receiving part and the other is used as the heat radiating part. The container 1 in the heat receiving section and the heat dissipating section which operate alternately is characterized by being formed into a double tube structure with a hydrogen storage alloy layer 5 as an inner wall. The heat transfer fluid in this case may be a gas or a liquid, and in the case of a liquid, it may be either one that takes only a liquid phase in the operating temperature range or one that undergoes a two-phase gas-liquid phase change. However, these gases and liquids are either only hydrogen or a mixed fluid of hydrogen and other fluids. Also, as in the first embodiment, the essential condition is that the heat transfer fluid is mutually stable with the hydrogen storage alloy in the presence of atomic active hydrogen released from the hydrogen storage alloy. Unlike the first embodiment, the alloy forming the hydrogen storage alloy layer 5 can be any hydrogen storage alloy depending on the selection of the heat transfer fluid, but the pulverization effect of the alloy cannot be ignored. . Therefore, although not specified in this embodiment, it is a matter of course that countermeasures against the pulverization effect should be taken. An example of this is a method in which a hydrogen storage alloy is formed into suitable powder particles, subjected to electroless copper plating, and then integrally molded under pressure to form a double-pipe structure container.

In the loop tube heat transfer device configured as described above, if the heat transfer fluid is mixed with a condensable two-phase fluid, a circulating flow will naturally occur spontaneously, but even if the heat transfer fluid is a gas,
Even in a liquid phase fluid, a circulating flow is generated spontaneously and acts as a heat transfer device.

The driving force is the hydrogen storage alloy layer 5- in the heat receiving part in Fig. 3.
High equilibrium hydrogen pressure generated in 1 and heat dissipation hydrogen storage alloy layer 5
-2 due to the pressure difference with the low equilibrium hydrogen pressure that occurs. The circulation direction is the direction regulated by the circulation direction regulating means 2 as shown by the arrow, and the other circulating flow generation principles are the same as described in (a), (b), (c), and (d) of [Prior Art]. By principle. The hydrogen generated at 5-1 is absorbed at 5-2, and its propulsive force causes all the heat transfer fluid inside the loop pipe container to circulate in the direction regulated by the circulation direction regulating means 2.

At the start of operation of the loop tube type heat transfer device, the hydrogen storage alloy layer 5-1 is heated by the heating means 6-1, the cooling means 7-1 is stopped, and the container 1-H9 in this part operates as a heat receiving section. do. The other hydrogen storage alloy layer 5-2 is cooled by the cooling means 7-2, the heating means 6-2 is stopped, and the container 1-01 in this portion operates as a heat radiating section.

When the hydrogen desorption ability of the hydrogen storage alloy layer 5-1 decreases and the hydrogen absorption ability of the hydrogen storage alloy 5-2 decreases, the above
The operations of Hc and ICh can be changed as a heat radiating section and a heat receiving section, respectively. The conversion is such that the heating means 6-1 stops, the cooling means 7-1 starts operating, and the cooling means 7-
This is done by stopping the heating means 6-2 and starting the operation of the heating means 6-2. As a result, the equilibrium hydrogen pressure in the hydrogen storage alloy layer 5-2 increases, hydrogen is released, and the hydrogen storage alloy N5-
The equilibrium hydrogen pressure at 1 decreases and hydrogen is absorbed. Therefore, the released hydrogen flows from 5-2 to 5-1. The circulation direction in this case is the direction regulated by the circulation direction regulating means, and the circulation direction of the heat transfer fluid does not change even if the operation of the heat receiving and radiating section is changed. This point is a unique function of the heat transfer device according to the present invention, and due to this property, by repeating the above-mentioned exchange of the heat receiving and radiating portion at predetermined intervals, the heat transfer fluid of the heat transfer device according to the present invention can be changed. continues to circulate in a given direction,
The amount of heat received from the heating means H is continuously transported to the cooling means C.

Heating means 6-1, 6-2 and cooling means 7 in this embodiment
-1.7-2 can be made smaller and simpler by using a Peltier element to serve as a heating means and a cooling means in a single element. That is, an electronic heating/cooling element using the Peltier effect can change the mode to heating or cooling simply by reversing the direction of the applied DC current. Furthermore, since the element is small and has a small heat capacity, the response to mode switching is also good.

In this embodiment, the container parts 1-H6 and ICh, which alternately act as heat receiving and dissipating parts, operate as a set of temperature difference-driven fluid pumps, and as in the first embodiment, the pumping action is determined by the selection of the hydrogen storage alloy. operates at any temperature level and even at very low temperature levels. Furthermore, it can be operated even when the temperature difference between the heat receiving and dissipating parts is small. If the heat transfer fluid is circulated at a sufficient flow rate by the pumping action, the other heat receiving section 1-H and heat dissipating section 1-C will have a small temperature difference between them even if their own temperature levels are low. They also work well and can exchange heat with each other over a wide temperature range. In addition, in Fig. 3, heat receiving and dissipating parts I that operate alternately
Hc, L Cb are the group of heat receiving parts 1-H and the heat radiating part 1
-C at the farthest mutual positions of the loop pipes, but even if they are installed adjacent or close to each other, their effects are the same, and the circulation direction of the heat transfer fluid is also the same. The flow velocity also does not change, and this feature is due to the action of the circulation direction regulating means.

C.9 Effects of the Invention The loop tube type heat transfer device according to the present invention can sufficiently increase the internal pressure difference between the heat receiving and dissipating parts by selecting the hydrogen storage alloy, so there is no need for assistance from an intermediate heat receiving and dissipating part. To enable long-distance heat transport and to facilitate the construction of a long heat transfer device with an inner diameter of one thread or less, which was previously difficult. Furthermore, the present invention provides a heat transfer device that operates in a temperature range in which a high-performance heat transfer device has not been available in the past, particularly in the temperature range of -20°C to 40°C and 250°C to 300°C. Furthermore, the present invention also provides a heat transfer device that operates with an extremely small temperature difference between heat receiving and radiating parts. As a result, the range of application and fields of use of the loop-type thin tube heat vibrator and the loop-tube type heat transfer device can be greatly expanded.

[Brief explanation of the drawing]

FIG. 1 is a partially sectional perspective view of a loop tube type heat transfer device. FIG. 2 is a sectional view showing the circulation direction regulating means. FIG. 3 is a partially sectional perspective view of the second embodiment. H... Heating means, C... Cooling means, 1-H... Heat receiving section, t-C... Heat radiating section, l... Loop pipe type container, 2... Circulation direction regulating means, 2-1... Valve seat, 2
-2... Valve body, 2-3... Stopper, 2-4...
Circulation direction regulating nozzle, 4... Heat transfer fluid, 5... Hydrogen storage alloy layer, 6... Heating means, 7... Cooling means. Patent applicant Actronics Co., Ltd. Haka 1 person (loop ¥ type c (?, construction, pickle) (a) (b) Figure 2 (Aki 4'l + fnΦ) 1 cover) Figure 3

Claims (3)

[Claims] (1) Both ends of the pipe itself having a bent pipe part are connected to each other to form a loop pipe type container, and at least one part of the container has a heat receiving part, and at least one other part has a heat radiating part. A predetermined amount of a predetermined heat transfer fluid is sealed in the container, and the heat transfer fluid is received by a circulation direction regulating means provided at at least one location in the loop-shaped flow path. In a heat transfer device that transports heat from a heat receiving part to a heat radiating part while spontaneously circulating in a certain direction due to the interaction of temperature differences between heat radiating parts, the heat transfer fluid is gaseous hydrogen or a combination of gaseous hydrogen and active hydrogen. Most or part of the internal pressure difference between the heat receiving and dissipating parts required for spontaneous circulation of the heat transfer fluid is caused by at least one fluid on the loop pipe. It is given by the pressure difference between the equilibrium hydrogen pressure of the hydrogen storage alloy generated by the high temperature of one heat receiving part and the equilibrium hydrogen pressure of the hydrogen storage alloy generated by the low temperature of at least one other heat radiating part of the loop pipe. A loop tube type heat transfer device characterized by: (2) The predetermined heat transfer fluid is a mixed fluid of gaseous hydrogen and a predetermined liquid fluid, and the predetermined liquid fluid is a fluid in which fine powder of a predetermined hydrogen storage alloy is dispersed and mixed. A loop tube type heat transfer device according to claim 1. (3) Each of the heat receiving parts and the heat radiating part provided in the container is provided in multiple places, and each of the heat receiving part and the heat radiating part at least one of them has a heating means and a cooling means. are installed together, and the structure is such that one of them operates alternately as a heat receiving section and the other as a heat radiating section at predetermined time intervals, and the containers in the heat receiving section and the heat radiating section that operate alternately contain hydrogen. 2. The loop tube type heat transfer device according to claim 1, wherein the loop tube type heat transfer device is formed in a double tube structure having an inner wall made of a storage alloy layer.