JPS6017211A - Thermosyphon type generator - Google Patents

Abstract

PURPOSE:To aim at reduction in an auxiliary power ratio and the miniaturization and capacity improvement of a regenerator, by setting up several units of circulating jet pumps inside an evaporating part of a vertical thermosyphon type enclosed vessel, while installing a turbine and a generator outside the said vessel. CONSTITUTION:One heat pipe vessel 4 is divided into three parts, i.e., the lower part is set down to an evaporating part 4a, the intermediate plate to an insulating part 4b and the upper part to a condensing part 4c, respectively, while a generator 18 is installed in the upper part of the vessel 4 via a small-sized radial turbine 7 and a transfer mechanism 8. When the evaporating part 4a is heated with a heater A, a steam ascending current C is produced whereby working medium steam is made into adiabatic expansion inside the turbine 7, rotating the generator 18, and thus outputted. Afterward, the steam is condensed into liquefaction by radiation B, forming a descending current D, and the same action takes place again. A jet pump 14c forcedly circulates a low boiling point medium. Thus, an auxiliary power ratio in a pump is reducible and what is more, the miniaturization and capacity improvement of a regenerator both are well promoted.

Description

[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a siphon-type generator, and in particular, to a siphon-type generator, in which a plurality of jet pumps are installed inside a gravity-type heat pipe structure filled with two different working fluids. , promotes stirring and mixing when two media come into contact, and also installs a turbine and generator externally to make the heat converter smaller and simpler, and is suitable for obtaining high efficiency performance. Concerning thermosiphon generators.

[Background of the invention]

A conventional gravity type heat pipe will be explained with reference to FIG. The gravity heat pipe consists of a simple combination of a pipe 1 and a working fluid 2 that is sealed after the inside of the pipe is evacuated.First, the working fluid 2 is boiled in the heating section 1a, and the generated steam is sent to the heat dissipation section IC. After condensing, it returns to the heating section under the action of gravity. By repeating the circulation of the working fluid 2 as described above, a large amount of heat can be transferred effectively and continuously. However, in the case of the thermosiphon type, the heating part 1a is moved downward in order to maintain this circulation. Postural constraints are imposed to ensure that Furthermore, in order to promote circulation, quicks that provide capillary action may be formed within the pipe, but in the case of this structure, the presence or absence of quicks has little effect. In the case of the thermosiphon type heat pipe of this device, it is used as an air-air exhaust heat recovery heat exchanger for industrial equipment, and is used only as a heat transfer device that utilizes the phase change of the working fluid 2. ing. Furthermore, when factory waste heat or the like is used as the amount of external heating, there is a possibility that unstable flow may occur when the working fluid 2 boils due to large temperature fluctuations.

Further, a single-component heat pipe type heat engine will be explained with reference to FIG. The entire inner surface of the container 4 constituting the heat pipe is covered with the wick 5, and the lower end is formed into the evaporating section 4a, and the upper end section is formed into the condensing section 4C. A working substance whose state changes between a liquid phase and a gas phase is contained in the container 4. Furthermore, a turbine 7 is provided in the middle part 6a of the heat insulating flow path 6 of the heat insulating part 4b between the evaporating part 4a and the condensing part 4C, and its rotating shaft 8
is connected to the output extraction transmission mechanism IO via the bearing 9.

When heat Affi is applied to the evaporation section 4a, the substance inside the wick 5 evaporates and flows through the adiabatic channel 6 in the direction of the arrow, and the intermediate section 6a
When passing through, the turbine 7 is rotated by the energy, the rotating shaft 8 is rotated, and the energy is taken out to the outside by the transmission mechanism IO. The feature of this device is that a turbine 7 is installed in the movement path of the working substance in the heat pipe container 4, and the energy retained in the working substance is extracted, giving the heat pipe the function of a heat engine. However, in this structure, since the turbine 7 is installed inside the heat insulating part 4b of the heat pipe, by offsetting the insulating part 4bl from the heating part 4a and the condensing part 4C, it is possible to use a normal pipe from the viewpoint of manufacturing the heat pipe. This makes it impossible, and there are difficulties in simplifying the structure. Since the turbine 7 is still built into the heat vibrator,
It is difficult to seal the pipe and the rotating shaft 8, and there is also a heat exchange section that evaporates and condenses the operating substance and a turbine 7 that extracts the output.
It is not possible to manufacture the components of the section independently. Due to these effects, when considering the heat pipe as a single unit,
There is a disadvantage that the heat transfer area and the dimensions of the heat insulating part are increased, and the overall dimensions are enlarged. In addition, in the case of the heat pipe of this method, the effect of Quick 5 cannot be expected to be so great because it is dominated by the action of gravity.

Further, a natural circulation type power generation plant that utilizes the difference between medium and low temperatures will be explained with reference to FIG. This power generation plant has a conventional Rankine cycle for thermal power generation, and uses an intermediate heat medium and a low boiling point medium as working media to form a mixed medium by dissolving them into each other. First, the low boiling point medium in the preheater 21 is preheated by external heating A, and then flashed to the gas-liquid separator 23 of the natural circulation boiler, and then flushed to the evaporator 23 by external heating Δ.
The enclosed mixed medium forms a natural circulation flow through the riser and downcomer pipes. On the other hand, the generated low-boiling medium steam is sent into the turbine 7, where it undergoes adiabatic expansion to rotate the turbine 7, and the generator 18 generates an output via the transmission mechanism 8fI. Thereafter, the expanded low-boiling medium vapor is condensed and liquefied in the condenser 24, and the low-boiling medium liquid is sent to the preheater 21 again as a compressed liquid by the pump 25. The components of this power plant are preheater 21. If the heat exchanger consisting of the evaporator 22 and condenser 24 is not a shell tube heat exchanger or multiple evaporative riser tubes, the length and number of riser tubes and tubes will increase as heat transfer tubes. The disadvantage is that the heat exchanger is large. Moreover, since a soluble intermediate heat medium and a low boiling point medium are used as the working medium, the boiling heat transfer coefficient within the tube is poor in the evaporative riser tube. Furthermore, the structure of the evaporator 22 for generating steam is a natural circulation boiler, but since the poise 25 is used to circulate the low boiling point medium after condensation, the evaporator 22, which is the heating source A, is Including the blower, the pump for cooling fluid when exchanging heat in the condenser 24, etc., the in-house labor rate is about 30 inches, which causes a decline in the performance of the power plant, power plant, and runt.

[Purpose of the invention]

The purpose of the present invention is to reduce the in-house labor rate, downsize the heat exchanger, and improve performance in a power generation system by evaporating in the lower part and condensing in the upper part, and forcing circulation by suction using a jet pump with low power consumption. The purpose of the present invention is to provide a high-efficiency thermosiphon generator for small to medium capacity that generates electricity using a thermosiphon structure using a thermosiphon structure.

[Summary of the invention]

The present invention integrates heat exchangers such as a preheater, evaporator, and condenser, which were conventionally separated, with a thermosiphon type heat pipe structure, and configures the heat exchanger as a single tube. Try to make the container smaller. In addition, by using a non-soluble intermediate heat medium and a low boiling point medium as the working medium instead of the conventional two soluble media, the low boiling point medium is passed from the jet pump nozzle tip to the evaporation section at the bottom of the heat pipe. By dispersing the liquid in the heating medium as fine droplets, the contact heat transfer area is expanded during mixing of the two media during stirring, and direct contact boiling heat transfer without walls generates steam, resulting in evaporation. The heat transfer area of the part is small and the heat transfer performance is improved. In the condenser at the top of the heat pipe, the low-boiling medium vapor from the turbine is ejected into the cooling medium liquid of the same composition, and here again, by direct contact condensation heat transfer without walls,
Since it is condensed and liquefied, heat transfer performance is improved due to the small heat transfer area of the condensing part.

Therefore, the heat transfer coefficient inside the heat pipe improves due to direct contact heat transfer in both the evaporation section and the condensation section, so if the heating source and heat radiation source are the same as before, even if the heat transfer coefficient outside the tube is the same, The overall heat transfer coefficient becomes high in both cases.

Therefore, when producing the same output as a conventional power plant, the heat transfer area becomes smaller due to the improved heat exchange performance.

Additionally, in order to reduce the labor rate within the plant, a jet pump with low power consumption was installed in the evaporation section of the power generation plant, and a stable circulation flow of the working medium was achieved using only the condensing heat circulation force by utilizing the head differential pressure caused by the gravitational effect. can be formed.

[Embodiments of the invention]

An embodiment of the present invention will be described below with reference to FIG. The basic structure of the thermosiphon generator that achieves the power generation method of the present invention is that the inside of one heat pipe 4 is divided into three parts: the lower part is the evaporator part 4a, the middle part is the heat insulating part 4b, and the upper part is the condensing part. 4C, with a small radial turbine 7 and a generator 18t installed via a transmission mechanism 8 above the container 4.

Therefore, the operating principle of this power generation system is that when the evaporator 4a is heated A, the working medium sealed in the container boils and evaporates to generate an upward steam flow C, which causes the inside of the heat insulating cap 4b covered with the heat insulating material 28 to rise. The working medium steam expands adiabatically within the turbine 7, rotates the generator 18, and outputs an output. After that, the steam is condensed and liquefied by heat radiation B in the condensing section 4C and flows downward D't
l-form and do the same thing again.

Here, the heat exchanger, which is an improvement on the enlargement of conventional power generation plants, can be made extremely small by being formed with a single pipe, and can be installed at the appropriate time as a small to medium capacity power generation plant. By mass-producing a large number of power plants, it is also possible to expand to large-capacity power plants according to specifications.

Next, a circulation mechanism for the working medium sealed in the container 4 will be explained with reference to FIG. First, as a working medium to be sealed, in order to prevent steam explosion and unstable flow due to external heat source fluctuations,
Use intermediate heat medium and low boiling point medium. These two media can be both soluble and non-soluble. The pressure above the free liquid level in the lower evaporation section is determined by the saturated vapor pressure Pv of the low boiling point medium and intermediate heat medium and the water head pressure γmLh up to the free liquid level.
It is expressed as the sum of

PP8=Pv+rmLh However, rmf′i is the specific weight in a two-medium two-phase state, and the pressure above the condensed liquid level in the upper condensing section is the sum of the saturated condensation pressure Pf and the water head pressure up to the free liquid level rfLf. It is expressed as

Pc=Pf+γfL1 However, γf is the specific weight of the condensate.

If the above pressure balance satisfies the following equation, when the low boiling point medium is ejected from the nozzle of the jet pump, the heat medium is sucked up, stable forced circulation of the two mediums is performed, and electricity is generated.

Pc>P+e Therefore, in order to achieve the above principle industrially,
The pressure chambers inside the vessel, i.e. the high-pressure and low-pressure chambers before and after the turbine, are provided and require a possible insulation structure, in particular to avoid heat exchange between the generated steam stream C and the condensate stream. For this purpose, regarding the internal structure of this power generation flint,
An example thereof will be explained with reference to FIG.

The internal structure of the thermosiphon generator that achieves the power generation method of the present invention includes an evaporating section 4a, a heat insulating section 4b, and a condensing section 4.
A heat medium 11 and a low-boiling point medium liquid 12 that do not melt into each other are sealed in a container 4 made of C, and a turbine 7, a rotating shaft 8, and a generator 18f are installed as a power generation mechanism on the top of the container 4. . In order to partition the heat medium 11 and the low boiling point medium liquid 12, the internal structure of the container 4 includes an evaporation rising pipe 14 equipped with a jet pump 14c and a low boiling point medium down pipe 13a in the evaporation section 4a, and is heat-insulated. The inside of the heat insulating part 4b kept warm by the material 19 is further insulated, r@i 3
A low-boiling point medium vapor riser pipe 16a and a low-boiling point medium vapor high-pressure side vessel 16b'i covered with a gas pipe are installed. Also, the condensing section 4
Inside C, a low-boiling point medium vapor low-pressure side vessel 17 is provided with a turbine inlet pipe 16c for low-boiling point medium vapor covered with insulation @16e, a turbine exhaust pipe 16d for low-boiling point medium vapor, and a large number of low-boiling point medium vapor jet holes 17a. Built-in. Considering the installation of the main container 4, the evaporating section 4a and the heat insulating section 4b are
A joint with an evaporator section 4"ir is connected between the condensing section 4C and a heat insulating section 4b, and a condensing section mounting joint 4e'f is connected between the condensing section 4C and the heat insulating section 4b to facilitate installation in an external duct.

The operation of the thermosiphon generator will be explained based on this basic structure. When the evaporator section 4a at the lower part of the container 4 is placed in a heat flow duct at a medium to low temperature and the evaporator section joint 4d is connected and heated A, the amount of heat is transferred to the inside through the entire evaporator section 4a, and the jet pump 14C sucks the heat medium. The heat medium 11 sucked through the tube 14d is heated within the evaporation riser tube 14. The heat medium 11 in the evaporative riser pipe 14 is characterized in that it alleviates temperature fluctuations in the amount of heat applied from the outside and has a heat storage effect while the device is in operation. Then, the low boiling point medium liquid 1 is injected from the nozzle 151 in the heget pump 14c in the heat medium ii in the evaporation riser pipe 14 which is heated A from the outside.
2 is by direct contact boiling heat transfer with the preheated heat medium 11)
It is boiled and vaporized, and rises in the evaporation riser pipe 14 as a two-phase upward flow E of heat medium and low boiling point medium vapor, producing a bubble pump effect. Then, the heat medium 11 and the low boiling point medium vapor 12b undergo gas-liquid separation at the exit of the evaporation riser pipe 14, and the generated vapor 12b is sent to the upper part, and the heat medium 11 after evaporation exchange is used for the evaporation riser pipe 14 and the low boiling point medium. It descends between the downcomers 13a. At this time, even if the unboiled portion of the low-boiling medium liquid 12 is included in the heat medium downward flow F due to insufficient heat from the outside, it does not affect the essential circulating flow. Therefore, once the container 4 is heated A from the outside, a stable circulating flow is formed in the evaporator 4a by the jet pump 14c and the bubble pump in the evaporator riser pipe 14.

On the other hand, the generated low boiling point medium steam 12b rises in the low boiling point medium steam riser pipe 16a inside the heat insulating part 4b covered with the heat insulating material 19, is temporarily stored in the low boiling point medium steam high pressure side container 16b, and flows into the turbine. It is introduced into the turbine 7 through the pipe 16c, where it undergoes adiabatic expansion, rotates the turbine 7, and generates electricity in the generator 8 through the rotating shaft 8. Here, it is more efficient to use a radial O inflow turbine for the turbine 7 than an axial flow turbine.

On the other hand, the adiabatically expanded low boiling point medium vapor 12b passes through the turbine exhaust pipe 16d' and is stored in the low boiling point medium vapor low pressure side container 17, and flows into the low boiling point medium liquid 12 from the low boiling point medium vapor jet hole 17a as steam bubbles 12a. Direct contact condensation of the same components is performed in the low boiling point medium liquid 12 condensed in the tube by ejecting and using the outside of the condensing section 4C as a heat dissipation port.

As a result, due to the water head difference and saturated condensation pressure of the condensed and liquefied low boiling point medium liquid 12, the low boiling point medium liquid 12 is again transferred to the nozzle 1.
It ejects from 5a and repeats the same action. Therefore, the evaporation section 4a' of the main container 4! r Heating A from the outside, and low boiling point medium liquid 12 from the nozzle 15a of the jet pump 14c.
is injected into the evaporation riser pipe 14, and the micronized low-boiling medium droplets come into direct contact with the preheated heating medium 11, boiling and vaporizing, and the flow of the heating medium 11 is accelerated by the bubble pump effect. . In addition, after generating electricity by rotating the turbine 7 with the generated steam 12b, the low-boiling point medium steam 12b is condensed and liquefied when the condensing part 40 of the main container 4 is opened from the outside to radiate heat. It is an integrated emission system. Therefore, a conventional heat exchanger or preheater,
In addition to preventing the evaporator and condenser from becoming larger, spherical low-boiling medium droplets or vapor bubbles are ejected, so the heat transfer area is large, and new heat transfer surfaces are always formed. As a result, highly efficient heat transfer performance can be obtained. Therefore, by using this device, the heat exchanger, that is, the steam generator and condenser, in a general power generation system can be downsized and simplified in structure. Additionally, installation, piping, etc. are simplified, making it possible to integrate the system, making it an optimal power generation system for small to medium capacity power generation. In addition, jet pumps with low power consumption are used for boosting pressure, and bubble pumps with natural circulation force are used to mix two media and have a stirring effect.
It has the effect of improving heat transfer performance and reducing the labor rate of pumps, etc. by about 6 inches.

Next, the principle of the jet pump 14C used in this apparatus will be explained using FIG. 7. First, nozzle 15 a outlet 1
Considering the ztO standard, if the pressure balance shown in Fig. 5 is TI C > P h, the refrigerant head Lf,
When a pressure liquid with a flow rate Gf is injected from the nozzle 15a, the pressure at the tip of the nozzle 15a becomes low, and the heat medium 11 with a flow rate of JtlGIl is sucked up, both media are mixed at the throat, and the pressure is decelerated and increased in the tiff user 14b to increase the discharge water head. I-1d is obtained.

Here, the efficiency ηj of the jet pump can be roughly calculated using the following equation.

At this time, care must be taken to prevent cavitation from occurring due to a pressure drop due to the suction height of the heat medium 11 and the velocity head of the total flow rate (Gf+Gh) passing through the throat portion, or a pressure drop near the exit cross section of the nozzle 15a.

Next, the arrangement state of the evaporation riser pipe 14 of this device is shown in Fig. 8(a).
Explain using. FIG. 8(a) shows a cross-sectional view taken along A- in FIG. The evaporation riser tubes 14 can be arranged uniformly along the periphery of the inside of the container 4 as shown in FIG. 8(a), or by installing a large number of them inside as shown in FIG. The evaporation riser pipe 14 is used to convey the amount well.
A good heat conductive agent 20 is embedded between the two, which has the effect of increasing the number of generated steam.

From the above viewpoint, the results of examining the heat transfer performance of one evaporative riser tube 14 will be explained using FIG. 9. As a sample, water was used as the heat medium 11, Freon atiS was used as the low boiling point medium 12, and the respective flow rates were iGw.

Gf, and the heat transfer performance for both medium flow rate ratio G' = Gw/Gf is shown in No. 9). Here, the average volumetric heat transmission coefficient KV is defined as the heat transfer performance as follows.

However, Q is the amount of heat exchanged between the two media, ■ is the body that contributes to heat exchange ff (=, a "H), and ΔTtv is the logarithmic average temperature difference between the two media. According to this, the low boiling point medium is transferred from the riser pipe. If it boils completely to 100% before it flows out, it will flow out as the weight flow rate ratio G' increases, so the latent heat transfer will decrease accordingly, and the average volumetric heat transfer coefficient Kv will also decrease.

In this case, the inflow velocity W in the evaporation riser 14 with respect to the heat flux q8 of the heat medium 11 and the low boiling point medium 12 calculated from the idea of natural circulation flow. The relationship between the height H and the steam volume fraction FS will be explained with reference to FIG. 1O when the height H is used as a parameter. From this result, in order to keep the steam volume ratio Fs from 0.4 to 0.7 in order to prevent burn-out of the tube wall, the inflow velocity w is slightly smaller, but the appropriate heat flux Q is required.
It can be seen that m is 5 to 25 KW/mt.

Next, when a jet pump is used as in the present invention, a forced circulation flow is formed, which intensifies stirring and mixing. In this case, as shown in Fig. 11, the Nutsselt number Nu (=T) of the dimensionless number dα, which represents the heat transfer performance of forced convection heat transfer, is approximately 1.6 times that of forced convection heat transfer around a solid sphere. indicates the value of However, the above values only deal with the heat transfer coefficient outside the droplet.

Based on the above structure, the relationship between the circulating flow rate G and the effective output is shown in FIG. If the circulation flow rate G is increased, the mixing and agitation of the two media in the evaporator riser will be promoted, and if the amount of generated steam Gv, that is, the adiabatic heat drop Δh is constant, the theoretical thermal efficiency η
increases, but the power consumption Lp of the pump increases accordingly.
As a result, the final effective output is the highest in the case of a jet pump as shown in FIG. 12.

Next, another actual case will be explained with reference to FIG. This 7th stem removes the heat insulation part in Fig. 6 and connects the condenser 23 to the top.
, evaporation riser pipe 14 to the lower part, downcomer pipe 13a for low boiling point medium,
An evaporator consisting of a heat medium container 22 is provided, and a turbine 7 and a generator 18 are installed in the middle thereof, and the operating principle is the same as that in FIG. 6.

As described above, if a plurality of small and medium capacity generators are installed, the total capacity can be increased to 46'i[. Figure 14 (a
) If generators of the same performance are arranged in a triangular arrangement in the heating duct 24, or if the heating source is large as shown in Fig. Install a large-capacity, large-diameter generator to
As the temperature level decreases downward in the heating flow,
Another option is to install one that generates a small amount of electricity.

Furthermore, if a thermosiphon type heat pipe is considered as a heat exchanger, the outer tube of the container 4, as well as the evaporating section 4a and the condensing section 4C, are used in which the fluids used for heating A and heat dissipation B are contaminated. For example, the heating side includes factory waste heat and geothermal water, and the heat radiation side includes industrial water and cooling air. Therefore, in order to improve the extra-tubular heat transfer coefficient on the outside of the cylindrical container 4, if the outside of the container 4 has a fine structure, the thermal resistance due to dirt will increase, so a high-fin tube 4a as shown in FIG. If the heat transfer area is increased by using a disk fin 4ac like the one using the fin 4ac or the one using the disk fin 4ac (in Fig. 15), evaporation@4aJ? Pipe length of condensing section 4C? Can be set to a minimum. Furthermore, the inner surface of the condensing part 4C has acute-angled fins 4f as shown in FIG. 16(a) and an inner grooved pipe 4g as shown in FIG.
It is possible to use

Therefore, since the power generation amount per unit of this thermal siphon type generator is small, multiple systems are installed horizontally as shown in Fig. 1417, and the evaporation part 4a at the bottom of the container 4 is connected to the waste heat duct which is the heating source. 24, and the condensing section 4C at the top of the container is installed in the cooling fluid duct 26, and by connecting a large number of these turbines 7, it is possible to increase the total power generation amount. Figure 18 shows a case where geothermal heat or other metal is used as a heating source.

〔Effect of the invention〕

As is clear from the above description, according to the present invention, a power generation plant using a thermosiphon heat pipe and a radial turbine provided with an internal pressure chamber, a steam riser pipe, a condensate flow downcomer, etc., and an insulating partition, etc. The heat transfer area can be reduced to approximately 1/2 by integrating the evaporator and condenser, and the condensing section is installed above the evaporating section to forcefully circulate the low-boiling point medium using water head pressure. By using a jet pump with low power consumption, the pump labor rate can be reduced by approximately 6 cm.
Furthermore, by sealing an insoluble intermediate heat medium and a low boiling point medium inside the container, the heat transfer coefficient within the tube due to direct contact boiling and condensation heat transfer between the two media in the evaporation section and the condensation section is approximately 1.5.
The heat transfer coefficient, which represents the heat transfer performance of both, is improved. By changing the power generation capacity of one of the above-mentioned pygros diameters, heights, turbine containers, etc. and combining them, a plant with a final power generation output can be easily achieved in accordance with the specifications.

[Brief explanation of the drawing]

Figure 1 is a vertical cross-sectional view of a conventional gravity heat pipe, Figure 2 is a vertical cross-sectional view of a conventional heat pipe type heat engine, Figure 3 is a system schematic diagram of a conventional natural circulation power generation plant, and Figure 4 is a vertical cross-sectional view of a conventional gravity heat pipe. is a longitudinal cross-sectional view of the thermosiphon-type generator of the present invention, FIG. 5 is an explanatory diagram of the pressure balance of the thermosiphon-type generator of the present invention, and FIG. 6 is a longitudinal cross-section of the internal structure of the thermosiphon-type heat pipe of the present invention. A top view, FIG. 7 is a principle diagram of the jet pump used in the present invention, and FIG.
- A cross-sectional view, FIG. 8(b) is a cross-sectional view of another embodiment,
Figure 9(a) is a vertical cross-sectional view of one evaporative riser pipe (in Figure 9)
is a graph of the average volumetric heat transfer coefficient Kv against the weight flow rate ratio G' of the low boiling point medium and the heat medium in one evaporative riser pipe, the first
The O diagram is a graph of the riser inflow velocity W0 and the vapor volume fraction Fs with respect to the heating flux q in the evaporation section, the ixi diagram is a diagram of the relationship between the Nutsselt number and the Reynolds number, and Figure 12 is a graph of the effective output with respect to the circulating flow rate G. Relationship diagram of pump power consumption Lp,
Figure 13 shows another embodiment in which the evaporation section and the condensation section are disconnected! 7
14(a) is a cross-sectional view when a large number of generators of the same diameter are arranged, and FIG. 14(b) is a cross-sectional view when a large number of generators of different diameters are arranged. Figure 15 (a
) is a partial vertical sectional view when Haiphong tubes are used for the evaporating section and condensing section outer tube, and FIG. 15(b) is a partial vertical sectional view when disc fins are used for the evaporating section and condensing section outer tube. Fig. 16(a) is a longitudinal cross-sectional view when acute-angled fins are used on the inner surface of the condensing section, Fig. 16 (a) is a longitudinal cross-sectional view when an internally grooved tube is used on the inner surface of the condensing section, and Fig. 17 is a longitudinal cross-sectional view when an acute-angled fin is used on the inner surface of the condensing section. FIG. 18 is a longitudinal cross-sectional view of a system in which a large number of the devices of the invention are installed in an air supply duct and a cooling fluid duct, as another embodiment, the devices of the invention are buried in geothermal heat and installed in large numbers in a cooling fluid duct. FIG. 1...Pipe, Ia...Heating part, lb...Insulating part, Ic...Maki-netsu part, 4d...Joint with evaporation part, 4e
...Condensing part mounting joint, 4f...Acute angle fin mechanism, 4
g...Inner grooved pipe, 5...Wick, 6...Insulated flow path, 6a...Insulated flow path middle section, 7...Turbine,
8... Rotating shaft, 9... Bearing, 10... Transmission mechanism,
11... Heat medium, 12... Low boiling point medium liquid, 18...
・Power generation i, +9...insulating material, 20...good thermal conductive agent,
21...Low boiling point medium vapor ejection mechanism, 26...Cooling fluid duct), 26a...Cooling fluid inlet, 26b...
・Cooling fluid outlet, 27...Cooling fluid, Figure 4-Figure 5 Tsuru q Figure 11 Figure 120 'l Self-determination 7 Fit amount Q Loading rate X Figure 15 ((lL) (b) Diagram 1G (α) (b) Diagram 1”7

Claims (1)

[Claims] 1. The working medium is sealed in a vertical thermosiphon type airtight container, the upper part is a condenser, the middle part is a heat insulating part, the lower part is an evaporator part, several jet pumps for circulation are installed in the evaporator part, and the container is heated. A thermosiphon generator characterized by having a turbine and generator installed externally.