JP3147352B2 - Heat dissipation system and heat engine using the same - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial application field) The present invention relates to a geothermal system that cools a heating element such as an electronic element, which is a main component of an electronic device, and generates electric power using underground geothermal energy. The present invention relates to a heat dissipation system that can be used for power generation and the like and a heat engine using the same.

(Prior art) As a conventional heat radiation system of this kind, for example, FIG.
There is one as shown in FIG. First, in FIG. 11, a radiator 107 having a plurality of radiating fins 105 is bonded to the other surface of the circuit board 103 on which the electronic element 101 is mounted on one surface. Then, the heat generated in the electronic element 101 is conducted from the circuit board 103 to the radiator 107, and is radiated to the outside from the radiating fins 105 to cool the electronic element 101 and the circuit board 103.

However, in such a structure of the heat dissipation system, the heat resistance due to the adhesion between the circuit board 103 and the heat dissipation body 107 is large, and it is difficult to efficiently dissipate the heat from the heat dissipation fins 105. In addition, when the electronic element 101 and the like are locally heated, there is a problem that sufficient heat radiation cannot be performed because heat is mainly conducted to a plurality of local radiation fins 105.

On the other hand, in the heat dissipation system of FIG. 12, a container-like heat pipe 109 is fixed on the circuit board 103, and the circuit board 103
An evaporation chamber 111 is defined above. And this evaporation chamber 111
A refrigerant 113 is accommodated on the circuit board 103 side at the bottom of the heat pipe 109, and a plurality of radiating fins 115 are provided on the outer surface of the heat pipe 109. Therefore, in this conventional example, heat generated in the electronic element 101 is absorbed by the refrigerant 113. And refrigerant 113
Is evaporated by heat absorption, is cooled on the upper side of the heat pipe 109 by heat radiation of the radiation fins 115, is condensed and liquefied, and drops again on the bottom of the evaporation chamber 111. Therefore, the thermal resistance does not increase as in the conventional example of FIG. 11, and even if there is local heating in the electronic element 101 and the like, the evaporation of the refrigerant 113 is accelerated in response thereto, and the electronic element 101 and Circuit board 10
The cooling of 3 can be sufficiently performed as compared with the conventional example of FIG.

By the way, in the conventional example of FIG. 12, a fan propeller 117 may be provided to further enhance the cooling effect, and forcible cooling may be performed by the cooling air of the fan propeller 117. However, in this case, a drive motor 119 for driving the fan propeller 117 is required, and in addition to controlling the cooling air generated by the fan propeller 117 according to a change in the heat generation temperature of the electronic element 101, the heat generation temperature of the electronic element 101, etc. A sensor that detects the driving motor based on this sensor
A control device or the like for controlling 119 was required, and there was a risk of cost increase.

In order to solve such a problem, the present applicant has already proposed a new heat dissipation system as shown in FIG. FIG. 13 is a conceptual view.
Turbine propeller 123 rotatably supported via 21
However, the refrigerant is rotated by the evaporative flow of the refrigerant 113, and the rotation of the inner magnet 125, which rotates integrally with the turbine propeller 123, rotates the outer magnet 127 magnetically coupled to the inner magnet 125. The rotation of the outer magnet 127 causes a bearing outside the heat pipe 109.
A fan propeller 131 rotatably supported via 129 is rotated. Therefore, without requiring an external drive source such as a drive motor, the fan propeller 131 can be rotated and efficient heat radiation can be performed, and the refrigerant 113 according to the heat generation state of the electronic element 101 and the like can be obtained. Of the fan propeller 131 can be automatically controlled without the need for a control device or the like, and the radiation efficiency can be improved while suppressing an increase in cost.

However, even in such an improved heat dissipation system, when the fan propeller 131 is used for cooling electronic devices or the like because of a low rotation speed, the cooling efficiency is poor,
When used for geothermal power generation and the like, it is relatively difficult to obtain a heat engine having low power generation efficiency and practical energy conversion efficiency.

(Problems to be Solved by the Invention) As described above, the conventional heat engine does not satisfy the energy conversion efficiency of practical heat dissipation or power generation in terms of heat radiation efficiency and power generation efficiency.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a practical heat radiation system that further improves energy conversion efficiency such as heat radiation efficiency or power generation efficiency while suppressing cost increase, and uses the same. To provide a heat engine.

[Configuration of the invention]

(Means for Solving the Problems) According to the present invention, an evaporating chamber in which a refrigerant that absorbs heat and evaporates from a heating element is accommodated, and a turbine blade chamber into which a vapor flow of the refrigerant evaporated from the evaporating chamber is guided. A guide passage that guides the evaporative flow from the evaporation chamber to the turbine blade chamber; an ejection port provided at one end of the guide passage to eject the steam flow into the turbine blade chamber; A turbine blade rotatably supported by the steam flow and rotatably supported by the steam flow, a fan blade rotatably supported so as to rotate in accordance with the rotation of the turbine blade, and provided outside the turbine blade chamber; A return flow path connecting the turbine blade chamber and the evaporation chamber for returning the steam flow after rotating the turbine blade to the evaporation chamber, wherein the return flow path is formed by a flexible pipe Did And a heat engine using the same.

(Operation) According to the present invention, since the height of the condensed liquid surface is adjustable, the efficiency of the refrigerant can be increased by increasing the height of the condensed liquid surface to promote the evaporation of the refrigerant.

(Example) Hereinafter, an example of a heat dissipation system according to the present invention will be described with reference to the drawings.

Prior to the description of embodiments of the present invention, a reference example of the present invention will be described. 1 and 2 show a first embodiment of the present invention, and are a longitudinal sectional view and a transverse sectional view taken along line AA, respectively.

In FIGS. 1 and 2, a circuit board 32 on which an electronic element 31 as a heating element is attached is a main component of an electronic device, and a housing 1 for forming a heat pipe is provided on the circuit board 32, for example. It is fixed by bolts 33.

The inside of the housing 1 is partitioned into an evaporation chamber 2 and a turbine blade chamber 5 by a heat insulating material 4. The bottom of the evaporation chamber 2 is formed by a circuit board 32, and the refrigerant 3 contained in the evaporation chamber 2 is in contact with the circuit board 32. The refrigerant 3 absorbs heat from the circuit board 32 side and evaporates, and is a refrigerant such as water or freon put in the decompressed evaporation chamber 2. This evaporation chamber 1
A jet port 6 of the evaporated refrigerant is formed at a connection portion between the nozzle and the turbine blade chamber 5. In this embodiment, a nozzle 7 is connected to a tip of the jet port 6. The nozzle 7 is provided to protrude into the turbine blade chamber 5.

On the other hand, a turbine blade 8 is supported in the turbine blade chamber 5 by a turbine shaft 9. One end (lower end) of the turbine shaft 9 is rotatably supported by the heat insulating material 4 by, for example, a non-magnetic conical bearing 10, and the other end (upper end) is provided with an inner magnet 13 described later.

A return flow path from the turbine blade chamber 5 for cooling and condensing the refrigerant 3 evaporated in the evaporation chamber 2 and returning to the evaporation chamber 2.
11 are formed. The return flow path 11 is connected to the evaporation chamber 2 and forms a closed loop with the turbine blade chamber 5.

A cooling means 12 for heat exchange for cooling and condensing the steam is provided in the return flow path 11. The cooling means 12 may be a radiating fin or a water cooling means for actively cooling.

By providing the cooling means 12, the process of evaporating and condensing the refrigerant 3 is smoothly performed. If this cooling means 12 is not provided, the condensing means will be described later.
When the cooling power is insufficient, the vapor may be saturated in the return flow path 11 and the evaporation of the refrigerant 3 may not be promoted. Therefore, the vapor in the return flow path 11 is forcibly cooled by the cooling means 12 and condensed to promote the evaporation of the refrigerant 3.

An outer magnet 14 is provided on the outer side of the housing 1 so as to face the inner magnet 13 provided at the upper end of the turbine shaft 9 with the return flow path 11 interposed therebetween. Fan blades 16 are rotatably supported.

Next, the operation of the heat dissipation system thus configured according to the reference example of the present invention will be described.

The refrigerant 3 absorbed and heated by the heat generated by the electronic element 31 becomes a vapor flow and rises in the evaporation chamber 2. The vaporization chamber 2 in the present invention has a sectional shape in which the vapor flow path gradually narrows gradually or gradually from the lower part of the vaporization chamber 2 toward the jet port 6, where the vapor flow is accelerated. . The steam flow accelerated in the evaporation chamber 2 is further accelerated by a nozzle 7 provided at the tip of the jet port 6 and jetted toward the turbine blade 8. This jetted steam flow causes the turbine blades 8 to rotate vigorously.

Then, the steam flow passes through the return flow path 11 connected above the turbine blade chamber 5, and is cooled and condensed by the heat exchange cooling means 12 provided on the way, and is condensed by gravity.
11 and returns to the lower part of the evaporation chamber 2. By repeating this process, the turbine blade 8 rotates.

On the other hand, the rotation of the turbine blade 8 rotates the inner magnet 13 via the turbine shaft 9. The rotation of the inner magnet 13 causes the outer magnet 14 provided outside the housing 1 to rotate. The rotation of the outer magnet 14 causes the fan blades 16 to rotate via the support shaft 15, and the fan blades 16 generate cooling air to cool the electronic element 31 and the turbine blade chamber 5.
The rotation of the inner magnet 13 and the outer magnet 14 is allowed by the non-magnetic bearings 17 and 18.

The ratio of the size of the bottom of the evaporating chamber 2 to the size of the jet port 6 is, for example, about 100: 6, but this is not limited to this, because it has a width depending on various conditions.

In such a heat dissipation system, the ejection port 6 provided in the evaporating chamber 2 is formed to be sufficiently small, and therefore has sufficient energy to rotate the turbine blade 8. The turbine blade 8 also uses an impeller to rotate most efficiently by the jet flow.

Further, the jet flow is changed by the nozzle 7 at the tip to the turbine blade 8.
Since the guide pressure is increased to the optimum position and the jet pressure is increased, the rotational force of the turbine blade 8 can be sufficiently increased, whereby the fan blade 16 can also obtain a sufficient rotational force.

By the rotation of the fan blades 16, wind for cooling the housing 1 is generated, and the outer wall surface of the housing 1 is cooled. When the outer wall surface of the casing 1 is forcibly cooled in this way, the heat radiation from the casing 1 is promoted, and the heat in the vaporization chamber 2 is efficiently radiated to the outside through the casing 1 to cool the electronic element 31. Can be performed effectively.

Further, the return flow path 11 is formed in the evaporating chamber 2 so that the return flow of the condensed and liquid refrigerant does not hinder the rotation of the turbine blade 8.
Since it is formed separately, the energy of rotation of the turbine blades 8 and thus the fan blades 16 can be used effectively.

On the other hand, when the heat generated by the electronic element 31 increases, the evaporation of the refrigerant 3 is accelerated accordingly. Therefore, fan blades
The rotation of the fan 16 becomes faster, and the fan blades 16
The cooling wind is increased. Further, when the heat generated by the electronic element 31 is not so high, the evaporation of the refrigerant 3 is also reduced, and accordingly, the cooling wind by the fan blades 16 is weakened.

Therefore, the cooling air is automatically adjusted according to the heat generation state of the electronic element 31. That is, it has an automatic cooling adjustment function.

Non-magnetic bearings are used for bearings 17 and 18 for rotatingly supporting the turbine blades 8 and the fan blades 16, respectively.
The inner magnet 13 and the outer magnet 14 are not affected at all. For this reason, no excessive force of the magnetic force acts, and a reduction in turbine efficiency and fan efficiency can be prevented as compared with when the magnetic bearing is used, so that smooth shaft rotation can be obtained. In this case, use of a conical bearing can particularly reduce rotational resistance.

Next, FIG. 3 is a cross-sectional view according to a modified example of the first reference example of the present invention. The same reference numerals are given to the same or equivalent parts as in FIG. 2, and the detailed description is omitted. This modified example is different from the aforementioned reference example in that a plurality of ejection ports 6 from the evaporation chamber 2 are provided.

By arranging a plurality of the jet ports 6 around the turbine blades 8 in a well-balanced manner, the rotational vibration of the turbine blades 8 can be reduced, and there is a great effect on improving the turbine efficiency and the fan efficiency.

Specifically, for example, as shown in FIG. 3, two jet ports may be provided around the turbine blade 8 with a phase shift of about 180 °, or three jet ports may be provided at an interval of about 120 °.

Similarly, four or more ejection ports 6 may be provided at substantially equal intervals. Then, similarly to the previous embodiment, a nozzle 7 is provided at the injection port 6 to guide the steam to the optimum position of the turbine blade 8.

Next, examples of the present invention will be described. FIG.
FIG. 2 is a longitudinal sectional view according to the embodiment of the present invention, in which the same or equivalent parts as those in FIG. This embodiment is different from the above-described reference example of the present invention in that a part of a pipe forming the return flow path 11 is a flexible pipe 19. As a result, the arrangement of the return flow path can be freely set, and the degree of freedom of mounting is remarkably improved. Further, it is possible to flexibly cope with a case where the condensed liquid level H fluctuates due to a usage state such as a change in the structure of the evaporating chamber 2 or the turbine blade chamber 5 or an amount of the refrigerant.

Next, a second embodiment of the present invention will be described. FIG. 5 shows a second reference example of the present invention, in which the same reference numerals are given to the same or equivalent parts as in FIG. 1, and detailed description is omitted. This reference example differs from the preceding reference example in that the injection port 6 of the evaporation chamber is formed in advance at an optimum position for rotating the turbine blade 8 and the nozzle 7 is omitted. Also, a return flow path 11 is formed inside the casing 1 separately from the evaporation chamber 2 and the refrigerant 3 accumulated in the turbine blade chamber 5 is formed.
, That is, a liquid pool return flow path 19 is formed.

Here, the reason why the liquid pool return flow path 19 is provided will be described. The possibility that the steam jetted into the turbine blade chamber 5 is condensed and liquefied because the periphery of the turbine blade chamber 5 is covered with the heat insulating material 4. Although there is almost no case, in consideration of the case where the refrigerant 3 is slightly liquefied and accumulated in the turbine blade chamber 5 for a long-time use, or because the heat insulating material 4 is not provided,
In the case where the refrigerant 3 accumulates in the turbine blade chamber 5, a liquid reservoir return flow path 19 for the refrigerant 3 is provided on the way through a one-way valve 20 such as a check valve. By providing the liquid reservoir return flow path 19 in this way, the refrigerant 3 does not accumulate in the turbine blade chamber 5 even when used for a long time, and the rotation of the turbine blade 8 is not adversely affected.

FIG. 6 shows a modification of the second embodiment of the present invention. The difference from the configuration of FIG. 5 is that a liquid pool return flow path 19 is provided outside the heat insulating material 4. In this case, the same operation and effect as those of the second reference example can be obtained, and the heat insulating effect of the heat insulating material 4 is not adversely affected. In this modification, if the return flow path 11 is formed of a flexible pipe or the like, the same operation and effect as those of the embodiment of the present invention described with reference to FIG. 4 can be obtained.

Next, a second embodiment of the present invention will be described. FIG. 7 is a schematic longitudinal sectional view showing a second embodiment of the present invention.

7 is basically different from the above-described embodiment and the reference example in that the evaporating chamber 2 and the turbine blade chamber 5 are independently separated and connected to each other by a flexible pipe 21.

In FIG. 7, the same parts as those in FIG. 1 or the parts equivalent thereto are denoted by the same reference numerals, and the detailed description is omitted.

An evaporation chamber 2 is formed in the housing 1a, and a refrigerant 3 is sealed therein. This housing 1a is, for example, an electronic element as a heating element.
It is fixed to a circuit board 32 to which 31 is attached.

On the other hand, a turbine blade chamber 5 in which the turbine blades 8 are arranged is formed in the housing 1b.

The evaporating chamber 2 and the turbine blade chamber 5 are connected by a flexible pipe 21 made of, for example, Teflon, and the refrigerant 3 evaporated in the evaporating chamber 2 becomes a vapor flow and flows through the flexible pipe 21.

In this embodiment, the flexible pipe 21 is
Two nozzles 7 formed at the tips of two jet ports 6 provided in the turbine blade chamber 5 by splitting into two pipes 21a and 21b.
The steam flow is accelerated and ejected from the.

In such a configuration, the evaporating chamber 2 and the turbine blade chamber 5 are separated via the flexible pipe 21, so that their respective locations can be freely set, and the degree of freedom in mounting is greatly improved.

Also, in order to improve the cooling efficiency of the electronic element 31, the electronic element 31 and the fan blade 16 can be arranged close to each other so that the cooling air from the fan blade 16 can directly cool the electronic element 31, and the cooling efficiency is Dramatically improved.

In this embodiment, the return flow path 11 also serves as the liquid pool return flow path 19. That is, the return passage 11 is connected to the concave portion 5a formed in the lower part of the turbine blade chamber 5,
The refrigerant 3, which has been condensed and liquefied in the steam flow ejected from the nozzle 7 as a gas-liquid two-phase flow or in the turbine blade chamber, accumulates in the recess 5 a, and this liquid is returned through the return passage 11. I have. This configuration has a simple configuration because it is not necessary to newly provide the liquid pool return flow path 19.

Further, in this embodiment, if the return flow path 11 is formed of a flexible pipe or the like, the same operation and effect as those of the embodiment of the present invention described with reference to FIG. 4 can be obtained.

FIG. 8 is a schematic vertical sectional view showing a third embodiment of the present invention, in which the same or corresponding parts as those in FIGS. 1 and 7 are denoted by the same reference numerals and detailed description thereof will be omitted. Omitted.

The most characteristic part of this embodiment is, for example, a shape memory alloy or a metal alloy so as to open and close at a predetermined set temperature in the middle of the flexible pipe 21 connecting the evaporating chamber 2 and the turbine blade chamber 5 or in the middle of the return passage 11. That is, valves 22 and 23 made of a shape memory resin are provided.

Next, the reason for providing the valves 22 and 23 will be described. As described above, evaporation of the refrigerant 3 → rotation of the fan blades 16 →
It is the flow during steady operation that the process of condensation of the refrigerant 3 is performed smoothly. Actually, the cycle is stopped and started alternately by the heat generated by the electronic element 31. The problem here is during startup. When the refrigerant 3 evaporates, the evaporating chamber 2 and the turbine blade chamber 5 have the same pressure if there is nothing to interrupt. That is, since there is no condensation of the refrigerant 4, the vapor does not circulate. In this case, the turbine blades 8 and the fan blades 16 cannot be rotated, so that cooling air cannot be generated. Therefore, there is a possibility that the electronic element 31 cannot be cooled, and there is a possibility that it is necessary to cool the electronic element 31 in some form at the time of the initial startup. Therefore, in the present embodiment, a valve 22 using, for example, a shape memory alloy that opens and closes at an arbitrary set temperature in the middle of the evaporation-side flexible pipe 21, Valve using memory alloy
23 will be provided. Here, the valve 23 is provided with a check valve. Looking at the flow, the valves 22 and 23 are closed until the steam temperature reaches a certain temperature. As the temperature increases, the pressure in the evaporation chamber 3 increases, and a pressure difference from the turbine chamber 2 is created. When the temperature reaches an arbitrary set temperature, the valve 22 opens and the steam flows to the turbine blade chamber 5, and the turbine blades 8 and the fin blades 16 are rotated to generate cooling air and start. Then, when the flow becomes steady, the check valve of the valve 23 opens to create a stable flow.

The refrigerant 3 in the evaporation chamber 2 that has been heated by the heat generated by the electronic element 31 rises as a vapor flow. But,
Turbine chamber 5 damped by valves 22 and 23
Don't go inside. Eventually, the temperature rises and the valves 22 and 23 open. At this time, since the valve 23 has a check valve, it does not flow backward from the pipe of the return flow path 11. The steam blows out from the nozzle 7 in the turbine blade chamber 5 through the flexible pipe 21 on the evaporation side. The blown steam flow rotates the turbine blades 8, rotates the fan blades 16 via the inner magnet 13 and the outer magnet 14, and generates cooling air. And
Cooling the turbine chamber 5 and the cooling means 12 as a heat exchanger,
The vapor stream condenses to create a unidirectional flow. As a result, the flow of the valve 23 in a certain direction from the turbine blade chamber 5 to the evaporating chamber 2 is formed to form an open closed loop. And this process is repeated.

As described above, the flexible pipe 21 connecting the evaporating chamber 2 and the turbine blade chamber 5 and the variable-length pipe (for example, the flexible pipe) forming the return flow path 11 are provided with a valve 22 that opens and closes at a predetermined set temperature in the middle thereof. The provision of the check valve 23 allows the initial start to be performed smoothly, and has a great effect particularly in the case where the heat generation is not constant and the start and stop cycles are performed frequently.

Next, FIG. 9 is a schematic configuration diagram showing a modification of the third embodiment of the present invention.

This configuration differs from the configuration shown in FIG. 8 in that the position where the fan blades 16 are mounted can be adjusted according to the installation location.

In FIG. 9, a bevel gear 24, a shaft 2
6, the fan blade 16 is rotatably supported via a bevel gear 25 and a shaft 27, and the fan blade 16 is a heat exchanger as a cooling means.
The heat exchanger 12 is arranged in the vicinity of the heat exchanger 12 so as to be cooled by cooling air. That is, the rotational force of the turbine blade is transmitted to the fan blade via the power transmission means including the bevel gear and the shaft, thereby enabling the fan blade to be disposed at an arbitrary position.

By separating the steam chamber 2 from the turbine blade chamber 5 and arranging the fan blades 16 at an arbitrary position via the power transmission means in this manner, the degree of freedom in design and arrangement is greatly improved. , Its industrial effect is great.

Next, FIG. 10 shows an embodiment in which the heat engine device of the present invention is applied to a geothermal power generation device.

In a conventional geothermal power generation device, steam is collected from an underground steam well via a pipe, a turbine is driven by the steam, a generator connected to the turbine is rotated to generate power, and the turbine is driven. The steam is condensed in a condenser and a part is used as cooling water for the condenser, and the surplus water is discharged to a river or returned to an underground by a pouring pit.

However, in the geothermal power generation device according to the present invention, the cooling is heated by the underground heat source to evaporate, the turbine is driven by this steam flow, and then the steam is condensed and circulated.

As a heat source for the geothermal power generation of the present invention, high-temperature steam and hot water heated by underground magma and the like which have been conventionally used do not contain hot water or water, but are not heated underground. Dry high-temperature rocks are used.

As an example of the geothermal power generation device shown in FIG. 10, the basic configuration of the heat engine device shown in FIG. 7 is adopted.
The same reference numerals are given to the same portions or the portions equivalent to those in FIG. 7, and the detailed description is omitted.

An evaporation chamber 2 is formed in the housing 1a, and a refrigerant 3 is sealed therein. This casing 1a is buried underground and absorbs heat from the underground heat source to evaporate the refrigerant 3 as described above.

On the other hand, the housing 1b is disposed, for example, on the ground, and has a turbine chamber 5 formed therein. A turbine blade 8 rotatably supported by a turbine shaft 9 is provided in the turbine chamber 5.
And the turbine shaft 9 is coaxially connected to the shaft of the generator 29. That is, the power generator 29 is also housed in the housing 1b, is directly connected to the turbine shaft 9, and rotates with high efficiency with the rotation of the turbine blade 8. In addition,
The generator 29 may be provided outside the housing 1b.

The underground evaporating chamber 2 and the above-ground turbine chamber 5 are connected by a pipe 21, and the refrigerant 3 evaporated in the evaporating chamber 2 turns into a vapor flow, flows through the pipe 21, and is injected into the turbine chamber 5. It is jetted at high speed from a nozzle 7 formed at the tip of the outlet 6.

 With this high-speed steam flow, efficient power generation can be performed.

Even in such a geothermal power generation device, it is clear that efficient operation can be performed because all the functions and effects of the heat engine device applied to the above heat radiation system can be obtained. The following operation and effects can be obtained as compared with the conventional geothermal power generation device.

In the conventional geothermal power generator, i) Among the components contained in the steam, Ca, Si, etc. adhere to the turbine to form a scale, the turbine blades become unbalanced, and finally, the turbine is damaged. Ii) Some of the water generated by condensation of steam in the condenser is cooled by the cooling tower for use as cooling water.
At that time, non-condensable gas such as SO ₂ may be released to the atmosphere and cause pollution.iii) Since the steam is taken out to the outside, the underground source may be depleted in a short period of time. iv) An injection pit is required to reduce condensate spill water to the underground, which requires large-scale equipment.

And so on.

However, according to the geothermal power generation device of the present invention, the evaporating chamber 2
The refrigerant 3 evaporated in the inside becomes a steam flow, and the steam is sent from the pipe 21 into the turbine chamber 5 and spouted from the jet port 6 at a high speed.
The steam after the turbine drive is condensed and returned to the evaporation chamber 2 by the return flow path 11, and only the heat is extracted from the underground heat source. I) No scale is attached to the turbine, and There is no risk of turbine damage, and the stability and reliability of the facility are improved. II) Non-condensable gas such as SO ₂ is not released to the atmosphere, preventing pollution. III) Extracting heat flow Therefore, there is no danger that the underground heat source will be depleted in a short period of time. IV) There is no need for a pouring pit for returning surplus water to the underground, so equipment is simple and inexpensive. The effect can be obtained.

In the above embodiment, the configuration shown in FIG. 7 is used as a geothermal power generation device, but it is a matter of course that another embodiment configuration may be applied to a geothermal power generation device.

The present invention is not limited to the above embodiment. For example, the shape of the evaporation chamber 2 is such that the steam flow path is narrow, for example, smoothly or stepwise from the bottom toward the ejection port 6, and the shape is not limited. Further, a cooling fin can be provided on the outer surface of the housing 1 or 1b to increase the cooling efficiency.

The means for coupling the turbine blades and the fin blades is not limited to magnetic coupling.

Further, the application of the heat engine of the present invention is not limited to the above-described heat radiation system and geothermal power generation device, but can be variously applied as a device for converting thermal energy into electricity or kinetic energy.

In addition, various modifications can be made without departing from the spirit of the present invention.

〔The invention's effect〕

As described above in detail, according to the present invention, it is possible to obtain a heat dissipation system with improved heat dissipation efficiency, a geothermal power generator with improved power generation efficiency, or a heat engine with high energy conversion efficiency while suppressing cost increase.

[Brief description of the drawings]

1 and 2 are a longitudinal sectional view and a cross-sectional view taken along line AA of a first embodiment of the heat dissipation system of the present invention, and FIG. 3 is a first sectional view of the heat dissipation system of the present invention. FIG. 4 is a longitudinal sectional view showing a first embodiment of the heat dissipation system of the present invention, and FIG. 4 is a vertical sectional view showing a second embodiment of the heat dissipation system of the present invention. FIG. 6 is a longitudinal sectional view showing a modification of the second reference example according to the heat dissipation system of the present invention, and FIG. 6 is a second embodiment according to the heat dissipation system of the present invention. FIG. 8 is a longitudinal sectional view showing an example of a heat dissipation system according to a third embodiment of the present invention, and FIG. 9 is a modified example of the third embodiment according to the heat dissipation system of the present invention. FIG. 10 is a longitudinal sectional view showing an embodiment in which the heat engine of the present invention is applied to a geothermal power generator, and FIGS.
The figure is a longitudinal sectional view showing a conventional heat dissipation system. 1, 1a, 1b ... housing, 2 ... evaporation chamber, 3 ... refrigerant, 4 ... heat insulating material, 5 ... turbine blade chamber (turbine chamber), 6 ... jet outlet, 7 ... nozzle, 8 … Turbine blade, 9… Turbine shaft, 11… Return flow path, 12… Cooling means, 13, 14… Inner magnet, outer magnet (coupling means) 16… Fan wing, 21… Flexible pipe , 22… valve, 23… valve with check function, 29 …… generator.

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Tatsuo Araki 1 Komukai Toshiba-cho, Saiwai-ku, Kawasaki City, Kanagawa Prefecture Inside the Toshiba Research Institute (72) Inventor Akira Kudo 1 Kochi Toshiba-cho, Kochi-ku, Kawasaki City, Kanagawa Prefecture (56) References JP-A-61-29200 (JP, A) JP-A-62-294705 (JP, A) JP-A-62-26306 (JP, A) JP-A-62-206205 ( JP, A) Japanese Patent Publication No. 54-26645 (JP, B1)

Claims (9)

(57) [Claims] An evaporating chamber in which a refrigerant that absorbs heat and evaporates from a heating element is accommodated; a turbine blade chamber into which a vapor flow of the refrigerant evaporated from the evaporating chamber is introduced; A guide passage that guides the evaporative flow to the blade chamber; an ejection port provided at one end of the guide passage to eject the steam flow into the turbine blade chamber; A turbine blade rotating by a steam flow, a fan blade rotatably supported so as to rotate in accordance with the rotation of the turbine blade, and a fan blade provided outside the turbine blade chamber and rotating the turbine blade. And a return flow path connecting the turbine blade chamber and the evaporation chamber for returning the steam flow to the evaporation chamber, wherein the return flow path is formed by a flexible pipe. . 2. An evaporation chamber in which a refrigerant that absorbs heat and evaporates from a heating element is accommodated, a turbine blade chamber into which a vapor flow of the refrigerant evaporated from the evaporation chamber is guided, and the turbine from the evaporation chamber. A guide passage that guides the evaporative flow to the blade chamber; an ejection port provided at one end of the guide passage to eject the steam flow into the turbine blade chamber; A turbine blade rotating by a steam flow, energy conversion means for converting kinetic energy of rotation of the turbine blade to another energy, and the steam provided outside the turbine blade chamber and rotating the turbine blade. A return flow path connecting the turbine blade chamber and the evaporation chamber for returning a flow to the evaporation chamber, wherein the return flow path is formed by a flexible pipe. organ. 3. The heat dissipation system according to claim 1, wherein said evaporating chamber and said turbine blade chamber are formed independently of each other, and said guide passage is formed by a flexible pipe. Heat engine. 4. A first valve means provided at an arbitrary set temperature provided in the middle of the guide flow path, and a non-return function capable of opening and closing at an arbitrary set temperature provided in the return flow path. 4. The heat radiating system according to claim 3, further comprising a second valve means having the second valve means. 5. The heat dissipating system according to claim 4, wherein said first and second valve means are made of a shape memory material. 6. A method according to claim 6, wherein a concave portion for storing the condensed and liquefied refrigerant is formed near the lowest position of the turbine blade chamber in the direction of gravity, and a liquid pool return flow path is formed so as to connect the concave portion to the evaporation chamber. The heat dissipation system according to claim 1 or the heat engine according to claim 2. 7. The heat radiating system according to claim 6, wherein the return flow path also functions as the liquid pool return flow path. 8. The heat dissipation system according to claim 1, further comprising power transmission means for transmitting a rotational force generated according to the rotation of the turbine blade to the fan blade. Heat engine. 9. The heat engine according to claim 1, wherein at least one of the evaporation chamber and the turbine blade chamber is covered with a heat insulating material.