CN110243081A - A solar loop heat pipe system for microbial soil purification - Google Patents

Abstract

The invention provides a solar loop heat pipe system for purifying microbial soil, which comprises a solar device and a loop heat pipe device, wherein the solar device comprises a solar heat collector and a heat exchanger, the loop heat pipe comprises an evaporation end and a condensation end, the evaporation end is positioned at the upper part of the condensation end, a capillary core is arranged in a pipeline leading from the condensation end to the evaporation end, and the condensation end is arranged on the outer wall of a gas chamber; the gas chamber is arranged in soil, the loop heat pipe is an antigravity heat pipe, an outlet of the air inlet channel and an inlet of the air outlet channel are communicated with the gas chamber, heat exchange is carried out between hot air and the evaporation end in the process of introducing the hot air into the gas chamber from the air inlet channel, and the condensation end conducts the heat to the soil on the periphery of the shell. The invention combines solar energy and loop heat pipes, has extremely high heat transfer efficiency and ensures the activity of microorganisms, thereby achieving the effects of quickly purifying soil and removing pollution.

Description

A solar loop heat pipe system for microbial soil purification

technical field

The invention relates to the fields of solar energy and heat pipes, in particular to a solar loop heat pipe system for microbial soil purification.

Background technique

Heat pipe technology is a heat transfer element called "heat pipe" invented by George Grover of Los Alamos National Laboratory in the United States in 1963. It makes full use of the principle of heat conduction and phase change medium. The rapid heat transfer properties of the heat pipe quickly transfer the heat of the heating object to the heat source, and its thermal conductivity exceeds that of any known metal.

Heat pipe technology was widely used in aerospace, military and other industries before. Since it was introduced into the radiator manufacturing industry, people have changed the traditional radiator design ideas and got rid of the single heat dissipation mode that only relies on high air volume motors to obtain better heat dissipation. The use of heat pipe technology enables the radiator to obtain a satisfactory heat exchange effect, opening up a new world in the heat dissipation industry. At present, heat pipes are widely used in various heat exchange equipment, including the field of nuclear power, such as waste heat utilization of nuclear power.

With the rapid development of industrialization, the problem of soil pollution is becoming more and more serious, and it is imminent to find a green and efficient soil purification method. Since the 1980s, the soil remediation industry has gradually emerged. Liu Yangsheng, Chen Tongbin and other scholars have carried out soil remediation research work in China, proposed a method of using microorganisms to catalyze the degradation of organic pollutants, and proposed to strengthen microbial degradation by changing various environmental conditions to achieve the purpose of treatment. But there are deficiencies in this scheme: on the one hand, it fails to achieve energy conservation, and on the other hand, it is restricted by more geographical restrictions and natural conditions.

The present invention provides a solar loop heat pipe system for microbial soil purification. The extremely high heat transfer efficiency of the loop heat pipe and the precise control of soil temperature, humidity, and pH can ensure the activity of microorganisms, so as to quickly purify the soil and remove pollution. Effect. The device is driven by solar energy, and the loop heat pipe (LHP) is used to make efficient use of solar energy, maximize the heat transfer efficiency of the solar panel, and reduce the use of other energy sources.

Contents of the invention

The invention provides a solar loop heat pipe system for microbial soil purification, which uses the combination of solar energy and loop heat pipes, and utilizes the performance of the antigravity heat pipe and its expanded heat exchange area, thereby solving the technical problems arising above.

In order to achieve the above object, the technical scheme of the present invention is as follows:

A solar loop heat pipe system for microbial soil purification, comprising a solar device and a loop heat pipe device, the solar device includes a solar heat collector, a heat exchanger and a fan, the heat exchanger is connected to the solar heat collector, the The air is input by the fan into the heat exchanger, and after being heated into hot air in the heat exchanger, it enters the loop heat pipe device; the loop heat pipe device includes an air inlet channel, an air outlet channel, a loop heat pipe and a gas chamber, so The loop heat pipe includes an evaporating end and a condensing end, the evaporating end is located on the upper part of the condensing end, a capillary wick is set in the pipeline leading from the condensing end to the evaporating end, and the condensing end is set on the outer wall of the gas chamber; The gas chamber is set in the soil, the loop heat pipe is an anti-gravity heat pipe, the outlet of the air inlet channel and the inlet of the air outlet channel communicate with the gas chamber, and the process of introducing the hot air from the air inlet channel into the gas chamber The heat is exchanged with the evaporating end, and the condensing end conducts heat to the soil around the gas chamber.

Preferably, the gas chamber is a flat structure.

Preferably, the condensation end is a coil pipe located on the lower wall of the gas chamber.

Preferably, a groove is provided on the lower wall of the gas chamber, and the coil is arranged in the groove.

Preferably, the condensation end is an annular pipe wound on the outer wall of the gas chamber.

Preferably, a part or all of the capillary core is arranged at the evaporation end.

Preferably, the evaporating end includes a rising pipe, and at least a part of the rising pipe is provided with a capillary wick, so as to realize the function of an anti-gravity heat pipe; Straight fins; the air outlet channel is set between and in contact with two adjacent vertical fins; the downpipe of the heat pipe is set between two adjacent vertical fins and be in contact with two adjacent vertical fins; at least a part of the ascending section and the descending section are arranged in the air inlet channel.

Preferably, the top and bottom of the gas chamber are planar structures.

Preferably, multiple gas chambers are provided, and the gas inlet channels of the multiple gas chambers are in a parallel structure.

Preferably, the evaporating end is arranged at the inlet pipe of the gas chamber, at least a part of the evaporating end is filled with a capillary wick, a pipeline from the condensing end to the evaporating end is arranged in the center of the wicking wick, and longitudinal vertical fins are arranged around the outer wall of the evaporating end.

Preferably, the gas outlet channel is arranged between two adjacent vertical fins and is in contact with the two adjacent vertical fins.

Preferably, the condensing end pipeline flowing from the evaporating end is arranged between two adjacent vertical fins and is in contact with the two adjacent vertical fins.

There are multiple pipelines and multiple gas outlet channels, and the number of pipelines is equal to the number of gas outlet channels.

Further preferably, the pipeline is arranged between adjacent gas outlet passages, and the gas outlet passage flows between adjacent pipelines from the evaporating end to the condensing end.

Further preferably, the center of the pipe from the evaporation end to the condensation end is at the same distance from the center of the adjacent gas outlet channel; the center of the gas outlet channel is at the same distance from the center of the pipeline from the adjacent gas evaporation end to the condensation end.

Preferably, the radius of the gas outlet channel is R, the radius of the pipeline flowing from the evaporating end to the condensing end is r, and the angle between adjacent fins is A, which meets the following requirements:

Sin(A)=a*(r/R)-b*(r/R) ² -c;

a, b, c are parameters,

Among them, 1.23<a<1.24, 0.225<b<0.235, 0.0185<c<0.0195;

14°<A<30°;

0.24<r/R<0.5;

More preferably, 0.26<r/R<0.38.

Compared with the prior art, the present invention has the following advantages:

1) The present invention proposes a soil purification device with a new structure, which uses solar energy and anti-gravity heat pipes for heat exchange, and transfers the heat in the gas to the soil, through the extremely high heat transfer efficiency of the loop heat pipe and the precise control of soil temperature, Humidity, pH, to ensure the activity of microorganisms, so as to achieve the effect of quickly purifying the soil and removing pollution.

2) The present invention increases the heat exchange area and improves the heat exchange effect by winding or coiling the condensation end of the antigravity heat pipe on the outer wall of the gas chamber and enlarging the area of the gas chamber.

3) The present invention improves and designs the structure of the evaporation end of the loop heat pipe to further increase the heat transfer coefficient.

4) Through a large number of numerical simulations and experiments, the present invention optimizes the angle between the gas outlet channel of the loop heat pipe, the pipeline flowing from the evaporating end to the condensing end and adjacent fins, and further improves the heat exchange efficiency.

Description of drawings

Fig. 1 is a structural schematic diagram of the solar heat collection system of the present invention.

Fig. 2 is a schematic diagram of an embodiment of the heat pipe device of the present invention.

FIG. 3 is a bottom view of FIG. 2 .

Fig. 4 is the schematic diagram of another embodiment of heat pipe device;

Fig. 5 is a sectional view of A-A in Fig. 4 .

Fig. 6 is a structural schematic diagram of a plurality of pipelines (descending section) flowing from the evaporating end to the condensing end in the present invention.

Fig. 7 is a schematic diagram of the pipeline connection structure in which the position of the capillary core is set according to the present invention.

Fig. 8 is a schematic structural view of setting multiple gas outlet pipes.

Reference signs are as follows: 1 solar heat collector, 2 fan, 3 heat exchanger, 4 gas outlet channel, 5 gas inlet channel, 6 loop heat pipe evaporation end, 7 gas chamber, 8 loop heat pipe condensation end, 9 evaporation The end flows to the condensing end pipeline (descending section), 10 the condensing end flows to the evaporating end pipeline, 11 gas chamber inlet pipe, 12 fins, 13 capillary core, 14 high temperature molten salt tank, 15 low temperature molten salt tank.

Detailed ways

The specific embodiments of the present invention will be described in detail below in conjunction with the accompanying drawings.

In this article, if there is no special explanation, when it comes to formulas, "/" means division, and "×" and "*" mean multiplication.

The specific embodiments of the present invention will be described in detail below in conjunction with the accompanying drawings.

As shown in Figure 1, a kind of solar energy loop heat pipe system of microbial soil purification comprises solar heat collector 1, heat exchanger 3 and blower fan 2, and described heat exchanger 3 connects solar heat collector 1, and described blower fan 2 The air is input into the heat exchanger 3, and after being heated in the heat exchanger 3 into hot gas, it enters the gas inlet channel 5 of the loop heat pipe device. The heat pipe is arranged in the soil for repairing the soil.

The invention utilizes solar energy to heat the base to generate a heat source, applies solar energy to the function of soil repair, saves energy, and greatly reduces development costs.

Further preferably, a high-temperature molten salt tank 14 and a low-temperature molten salt tank 15 are respectively arranged between the solar heat collector 1 and the heat exchanger 3, and the high-temperature molten salt tank 14 is arranged upstream of the heat exchanger 3, and the low-temperature molten salt A tank 15 is provided downstream of the heat exchanger 3 . The high-temperature molten salt tank 14 and the low-temperature molten salt tank 15 are set up to store the high-temperature waste heat energy and low-temperature waste heat heat energy of solar energy, so as to satisfy heat utilization in bad weather or at night.

Referring to Figure 1, the mature solar photothermal technology is used to generate controllable high-temperature hot air, and the generated high-temperature hot air is passed to the heat pipe device buried in the soil. Thereby saving energy.

The heat pipe device includes an anti-gravity loop heat pipe, as shown in Figure 4 and Figure 5, the heat pipe includes an evaporation end 6 and a condensation end 8, the evaporation end 6 is located on the upper part of the condensation end 8, and a part of the evaporation end 6 It is arranged on the fluid ascending section, and a capillary wick 13 is arranged on at least a part of the evaporation end of the fluid ascending section, as shown in FIG. 6 .

As a preference, the evaporating end includes two parts: the pipeline from the evaporating end to the condensing end (the descending section) 9 and the ascending section. Among them, as a preference, a pipeline 10 from the condensing end to the evaporating end is provided in the ascending section.

The solar loop heat pipe system of microbial soil purification as shown in Figure 2, described loop heat pipe device comprises air inlet channel 5, air outlet channel 4, loop heat pipe and gas chamber 7, described loop heat pipe is shown in Figure 4 As shown, it includes an evaporating end 6 and a condensing end 8, the evaporating end 6 is located on the upper part of the condensing end 8, the condensing end 8 is provided with a capillary wick in the pipeline leading to the evaporating end 6, and the condensing end 8 is arranged in the gas chamber On the outer wall of the chamber; the gas chamber 7 is set in the soil, the loop heat pipe is an anti-gravity heat pipe, the outlet of the air inlet channel 5 and the inlet of the air outlet channel 4 communicate with the gas chamber 7, and the hot air During the process of introducing the air inlet channel 5 into the gas chamber 7, heat exchange is performed with the evaporation end, and the condensation end conducts heat to the soil around the gas chamber.

The invention provides a soil remediation system of a loop heat pipe with a new structure. By setting the loop heat pipe as a high-efficiency heat transfer tool, the principle is simple, the structure is compact, and the cooling efficiency is significantly improved.

Preferably, at least a part of the evaporation end 6 of the loop heat pipe is installed at the inlet of the gas chamber 7 . Preferably, the evaporation end 6 of the loop heat pipe is arranged in the inlet pipe 11 of the gas chamber. The inlet pipe 11 of the gas chamber is connected to the air inlet channel 5 .

Preferably, at least a part of the gas inlet channel 5 is arranged in the inlet pipe of the gas chamber 7 . With this arrangement, the gas in the gas inlet channel 5 can directly participate in the heat exchange of soil remediation through the inlet pipe, so that the gas can be further cooled under the joint action of the fluid and the loop heat pipe, and the heat exchange effect can be improved.

Preferably, the gas chamber 7 is made of thermally conductive material, preferably metal, such as copper and aluminum. Through the material of the gas chamber, the heat of the gas can be transferred outward through the chamber, thereby adding a heat exchange method, so that the heat of the gas is transferred to the external fluid through the loop heat pipe and the gas chamber.

Preferably, as shown in FIG. 2 , the gas chamber 7 is a flat structure. By arranging the flat tube structure, the contact area between the gas chamber and the soil can be increased.

Preferably, as shown in FIG. 3 , the gas chamber 7 has a circular structure when viewed from the bottom. By arranging a circular structure, heat can be dissipated evenly to the periphery.

Preferably, as shown in FIG. 3 , the condensation end 8 is a coil tube located on the lower wall of the gas chamber.

Preferably, there are multiple air outlet passages 4 . Through the cooperation of multiple air outlet pipes, the air can be discharged quickly.

Preferably, the inlet end of the air outlet channel 4 extends from the center of the gas chamber to the edge of the gas chamber. For example, Figure 8. Of course, Fig. 8 only shows the air outlet channel 4, and other components are not shown. By arranging the inlet end of the air outlet channel 4 at the side of the gas chamber, the gas can be forced from the side of the central flow channel, so that the gas can participate in the whole process of heat exchange and avoid short circuit of the hot air.

Preferably, as shown in FIG. 3 , a groove is provided on the lower wall of the gas chamber, and the coil is arranged in the groove. In order to facilitate the fixing of the condensing end.

Preferably, the coil structure protrudes from the center of the circular structure, extends the outer end of the circular structure, and then coils toward the center of the circular structure, as shown in FIG. 3 . With such arrangement, the heat can be dissipated from the outer end of the circular structure first, and then gradually inward. Because the diameter of the coil at the outer end is larger, more heat is needed, and because the hot air enters the gas chamber, the hot air transfers heat outward through the chamber. Relatively speaking, the heat source in the middle is the most sufficient, because the hot air enters the middle first. Through the above arrangement, the soil can be evenly heated as a whole.

Preferably, toward the radial direction along the center of the circular structure, the distribution density of the coiled tubes becomes larger (the distance between adjacent coiled tubes gets smaller as the distance between them grows). The main reason is that through such setting, the heat can be dissipated from the outer end of the circular structure first, and then gradually inward. Because the diameter of the coiled pipe at the outer end is large, more heat is needed, so that the overall heat dissipation is uniform and the effect of soil restoration is enhanced. Make the overall repair uniform.

Further preferably, as a preference, the distribution density of the coiled tubes increases continuously along the radial direction from the center of the circular structure. Through numerical simulation and experiments, it is found that the uniformity of soil heating can be further improved through the above structure.

Preferably, the diameter of the coil becomes larger and larger along the radial direction from the center of the circular structure. The main reason is that through such setting, the heat can be dissipated from the outer end of the circular structure first, and then gradually inward. Because the diameter of the coiled pipe at the outer end is large, more heat is needed, so that the overall heat dissipation is uniform and the effect of soil restoration is enhanced. Make the overall repair uniform.

Further preferably, as a preference, the diameter of the coil tube increases continuously along the radial direction from the center of the circular structure. Through numerical simulation and experiments, it is found that the uniformity of soil heating can be further improved through the above structure. Enhance the effect of soil remediation and make the overall remediation uniform.

Preferably, the condensation end is an annular pipe wound on the outer wall of the gas chamber.

Preferably, the gas chamber 7 is a square structure viewed from the bottom.

As another embodiment (not shown), the gas chamber 7 is a round pipe structure, and the condensation end is wound on the round pipe. The circular pipe is perpendicular to the inlet pipe 11 of the gas chamber.

As a preference, an electric heater for auxiliary heating is arranged in the gas chamber. When the heat of the air is insufficient, it is supplemented by an electric heater.

Preferably, it also includes a control system, the control system controls the heating of the electric heater by detecting the air temperature of the air inlet channel.

If the measured air temperature is lower than the specified value, the control system activates the electric heater for heating.

If the measured air temperature is higher than the specified value, the control system stops the heating of the electric heater.

Further preferably, the inlet pipe of the gas chamber 7 is connected to the gas inlet channel.

The structure of the gas chamber shown in Fig. 2 is a preferred embodiment. However, compared with the structure in Figure 2, the structure in Figure 4 is inferior in terms of expanding the heat exchange area, and the structure in Figure 4 is difficult to embed in the soil, but the structure in Figure 4 can also achieve the function of soil repair, so it is also Belong to a scheme of this application. As shown in FIG. 4 , the diameter of the gas chamber 7 gradually increases from the position where the inlet pipe is connected downwards at the beginning, and then gradually decreases at a certain position. It is beneficial for the gas to flow in the gas chamber, to complete the gas cycle, and to increase the heat exchange efficiency between the gas and the wall of the gas chamber.

Preferably, as shown in FIG. 2 , the bottom and top of the gas chamber 7 are planar structures.

Preferably, multiple gas chambers 7 are provided, and the gas inlet channels 5 of the multiple gas chambers are in a parallel structure.

Preferably, the gas outlet channels 5 of the plurality of gas chambers are in a parallel structure.

Preferably, the evaporation end 6 of the loop heat pipe is installed at the inlet pipe of the gas chamber, and the condensation end 8 of the loop heat pipe is wound outside the gas chamber and directly contacts the external soil. The loop heat pipe condenser is wrapped around the outside of the gas chamber, fully in contact with the external soil, increasing the heat dissipation of the gas at the evaporating end of the heat pipe, and improving the cooling efficiency.

As shown in Fig. 4, the condensation end is an annular pipe wound on the outer wall of the gas chamber.

Preferably, along the height direction from the top to the bottom, the density of the condensation end 8 of the loop heat pipe on the outer wall of the gas chamber 6 is more and more dense (the older the distance between the ring pipes, the smaller). The main reason is to concentrate the heat in the lower part for heat exchange as much as possible, because the temperature of the next step is low and more heat is needed to enhance the effect of soil restoration. Make the overall repair uniform. It is found through experiments that the above-mentioned structure can further improve the repair effect by about 11%.

Further preferably, along the height direction from the upper part to the lower part, the winding density of the condensing end 8 of the loop heat pipe on the outer wall of the gas chamber 6 increases continuously. It is found through experiments that the above-mentioned structure can further improve the repair effect by about 5%.

Preferably, a capillary wick 13 is provided in at least a part of the evaporating end 6, and its capillary force provides the power for the reflux cycle of the working fluid, and at the same time makes the reflux working fluid meet the heat transfer requirements, thereby realizing the function of an anti-gravity heat pipe.

By setting the capillary wick 13, and the capillary wick 13 is arranged on the evaporating end, so that flow resistance is naturally generated in the ascending section 6 of the evaporating end, so that the steam generated at the evaporating end naturally flows to the evaporating end with less resistance and flows to the condensing end pipeline 9, thereby An anti-gravity heat pipe is formed.

Preferably, the capillary wick 13 is only arranged in the ascending section of the evaporation end, preferably in a part of the ascending section. For example, as shown in Figure 4, Figure 6, and 7.

Preferably, at least a part of the gas outlet channel 4 is arranged in the inlet pipe of the gas chamber, and the cold gas at the gas outlet precools the hot gas at the gas inlet. Through the heat exchange between the outlet gas and the inlet gas, the heat exchange effect is further realized and the condensation efficiency of water is increased.

As preferably, as shown in Figure 4, the evaporation end is arranged at the inlet pipe of the gas chamber, and the rising section of the evaporation end is filled with a capillary wick 13 to provide sufficient capillary force. 10. By setting the pipeline 10 in this way (there is no capillary core), the fluid resistance of the pipeline can be reduced, making the working medium return more smoothly, and improving the heat transfer capacity under the anti-gravity state. The outer wall of the rising section of the evaporation end is surrounded by a longitudinal The vertical fins 12 increase the heat exchange area and improve the heat exchange efficiency with the gas.

The pipeline 10 is a gas or liquid pipeline, which realizes a flexible arrangement, and has a small diameter and is easy to bend. The principle of the loop heat pipe is that if the side of the evaporator and the pipeline 10 are steam pipelines, the principle is that the internal working medium evaporates when the evaporator is heated, and the steam enters the pipeline 10 along the upper outlet of the evaporator, and then flows to the surrounding pipeline at the lower part. The fluid contact begins to condense, and when the steam is completely condensed, it is returned to the evaporator by the capillary force of the evaporator, thereby realizing the circulation of the working fluid.

Preferably, the pipeline 10 communicates with the capillary core 13 . Through communication, the circulation of fluid between the capillary wick 13 and the pipeline 10 can be realized, so that when the liquid rises through the capillary wick, if a large pressure is generated due to heat absorption, for example, bubbles may even appear, it can pass through the pipeline. 10 to balance the pressure of the evaporation section, so as to ensure the balance of pressure.

Further preferably, the capillary wick 13 extends to the condensing end, so as to directly suck up the liquid at the condensing end. Further improve the circulation capacity of the anti-gravity heat pipe.

Preferably, the capillary cores are distributed along the height direction, as shown in Fig. 3 . Further preferably, along the height-decreasing direction, the capillary force of the capillary core is gradually enhanced. The closer to the condensation end, the greater the capillary force. It has been found through experiments that this method can further increase the suction force on the liquid, and can increase the suction force by more than 20% at the same cost, thereby improving the heat exchange effect.

Through further analysis, the preliminary reason may be that as the capillary force near the condensing end becomes stronger, the liquid at the condensing end can be quickly sucked into the capillary core, and the liquid continuously flows to the evaporating end. During the flow process, the liquid continuously absorbs heat, and the temperature rises due to the heat absorption, and the density becomes smaller. Therefore, due to the change in density, the capillary force required by it becomes significantly smaller. Sucks up easily. The above reasons are obtained by the inventor through a large number of experiments and researches, and are not common knowledge in this field.

Further preferably, along the height-decreasing direction, the capillary force of the capillary wick is gradually enhanced to a greater extent. It has been found through experiments that this method can further increase the suction force on the liquid, and can further increase the suction force by about 8% at the same cost, thereby improving the heat exchange effect.

Preferably, the pipeline is formed by a through hole opened in the middle of the capillary core.

Preferably, as shown in FIG. 7 , the tube diameter at the position of the heat pipe with the capillary core is larger than the tube diameter at the position of the heat pipe without the capillary core.

Further preferably, as shown in FIG. 7 , the change in diameter between the tube at the heat pipe position with the capillary wick and the tube at the heat pipe position without the capillary wick is a continuous change. More preferably, it changes linearly. The pipe at the position of the large diameter and the pipe with the small diameter are connected by a constriction at the joint. The change of the pipe diameter of the shrinkage part is a linear change.

Preferably, the gas outlet channel 4 is arranged between two adjacent vertical fins 12 and is in contact with the two adjacent vertical fins 12 . With such an arrangement, it is possible to reduce the number of independent mechanisms for supporting the gas outlet channel 4, making the structure compact, and the cold gas in the outlet channel can exchange heat with the fins through the pipes, keeping the fins cold and enhancing the heat exchange effect.

Preferably, the evaporating end flows to the condensing end and the evaporating end flows to the condensing end pipeline 9 is arranged between two adjacent vertical fins and is in contact with two adjacent vertical fins. By setting in this way, it is possible to reduce the number of independent supporting mechanisms for the gas outlet channel 4, making the structure compact, and the steam in the pipeline can transfer a small amount of heat to the fins through the pipeline, reducing the overall thermal resistance of the system and avoiding evaporation under the ground's anti-gravity condition The superheating of the steam generated in the device can slow down the temperature oscillation during the start-up of the heat pipe.

Further preferably, the pipe 9 from the evaporating end to the condensing end is closer to the outer wall of the evaporating end pipe than the gas outlet channel 4, so that the above two heat transfer processes can be realized simultaneously and play corresponding roles.

Further preferably, the diameter of the pipeline 9 flowing from the evaporation end to the condensation end is smaller than the gas outlet channel 4 .

Preferably, the evaporating end flows to the condensing end pipeline 9 along which multiple evaporating end flow directions can be set, as shown in FIGS. 4 and 6 . By setting multiple evaporating ends to flow to the condensing end pipeline 9, the steam generated by the evaporating end can flow through multiple evaporating ends to the condensing end pipeline 9 to enter the condensing end, further enhancing heat transfer, and because the fluid in the heat pipe absorbs heat Evaporation leads to an increase in volume. By setting multiple pipelines 9 from the evaporating end to the condensing end, the pressure can be further relieved and the heat exchange effect can be improved.

Further preferably, the vertical fins extend through the center of the inlet pipe of the gas chamber, and the ascending pipeline at the evaporation end has the same center of circle as the inlet pipe of the gas chamber.

Preferably, there are multiple pipes 9 from the evaporating end to the condensing end, and the distance between the centers of the multiple evaporating end to condensing end pipes 9 and the ascending section of the evaporating end is the same.

Further preferably, a pipeline 9 from the evaporating end to the condensing end is arranged between every two adjacent vertical fins 12 . The pipeline 9 from the evaporating end to the condensing end is a parallel structure.

As a preference, there are multiple gas outlet passages 4, and the distance between the center of circles of the multiple gas outlet passages 4 and the ascending pipeline at the evaporating end is the same, so that the temperature distribution between the fins is more uniform, and the above-mentioned heat exchange The effect is more obvious. Further preferably, a gas outlet channel 4 is provided between every two adjacent vertical fins 12 . The gas outlet channel 4 is a parallel structure.

Further preferably, there are multiple pipelines 9 from the evaporating end to the condensing end, and multiple gas outlet channels 4 , and the number of pipelines 9 flowing from the evaporating end to the condensing end is equal to the number of gas outlet channels 4 .

Further preferably, the pipeline 9 flowing from the evaporating end to the condensing end is arranged between adjacent gas outlet channels 4 , and the gas outlet channel 4 is between adjacent pipelines 9 flowing from the evaporating end to the condensing end. Further preferably, the distance between the center of the pipeline 9 from the evaporating end to the condensing end is the same as the center of the adjacent gas outlet channel 4 ; That is, the pipeline 9 flowing from the evaporating end to the condensing end is arranged in the middle of the adjacent gas outlet channels 4 , and the gas outlet channel 4 is in the middle of the pipelines 9 flowing from the adjacent evaporating end to the condensing end. That is, as shown in FIG. 4, the first connecting line between the center of the circle where the pipeline 9 at the evaporating end flows to the condensing end and the center of the evaporating end 6 forms a second line between the center of the circle of the adjacent gas outlet channel 4 and the center of the evaporating end 6. The first connecting line, the third connecting line, the first angle formed between the first connecting line and the second connecting line is equal to the second included angle formed between the first connecting line and the third connecting line. Similarly, the fourth connecting line between the center of the circle where the gas outlet channel 4 is located and the center of the evaporating end 6, the fifth connecting line is formed between the center of the circle of the adjacent evaporating end flowing to the condensing end pipeline 9 and the center of the evaporating end 6, The sixth connection line, the third angle formed between the fourth connection line and the fifth connection line is equal to the fourth angle formed between the fourth connection line and the sixth connection line. That is, along the circumferential direction, the piping 9 from the evaporating end to the condensing end and the outlet channel 4 are evenly distributed.

Through the above arrangement, it can ensure that the pipeline 9 from the evaporating end to the condensing end and the gas outlet channel 4 absorb heat evenly on the inlet gas, and avoid local uneven heating. The gas outlet channel 4 can continue to participate in heat exchange after absorbing heat, and transfer the heat to the evaporation end through the fins.

In the numerical simulation and experiment, it is found that the diameter difference between the gas outlet channel 4 and the pipeline 9 flowing from the evaporating end to the condensing end cannot be too large or too small. If it is too large, the gas outlet channel 4 and the evaporating end flow to the condensing end pipeline. If the distribution distance of 9 is too far, the gas heat exchange between channel 4 and the pipeline 9 flowing from the evaporating end to the condensing end is not good, resulting in uneven heat exchange as a whole; if it is too small, the gas outlet channel 4 and the evaporating end flow to the condensing end pipe The distribution distance of the road 9 is too short, resulting in poor heat exchange of the gas near the outer wall of the inlet pipe 11 and/or the gas near the outer wall of the evaporation end 6, resulting in uneven heat exchange of the gas in the overall inlet pipe 11; for the same reason, The included angle between adjacent fins 12 should not be too large. If it is too large, it will lead to fewer distribution fins and poor heat transfer effect. At the same time, the distribution of the gas outlet channel 4 and the pipeline 9 flowing from the evaporating end to the condensing end will be too large. If the angle is too small, the heat transfer will be uneven and the heat transfer effect will be poor. Similarly, the angle between adjacent fins 12 should not be too small. If it is too small, the fin distribution will be too dense, the flow resistance will increase greatly, and the gas outlet channel 4 and the diameter of the pipeline 9 flowing from the evaporating end to the condensing end are not much different, but their heat exchange capacities of the same area are quite different, so in this case, the heat exchange is not uniform, resulting in poor heat exchange effect.

Therefore, it is necessary to determine the optimal size relationship through a large number of numerical simulations and experiments.

The radius of the gas outlet channel 4 is R, the radius of the pipeline 9 flowing from the evaporating end to the condensing end is r, and the angle between adjacent fins is A, which meets the following requirements:

Sin(A)=a*(r/R)-b*(r/R)2-c;

a, b, c are parameters,

Among them, 1.23<a<1.24, 0.225<b<0.235, 0.0185<c<0.0195;

14°<A<30°;

0.24<r/R<0.5; more preferably, 0.26<r/R<0.38.

The above empirical formula is obtained through a large number of numerical simulations and experiments, and has higher accuracy than the previous logarithmic function, and has been verified by experiments, and the error is basically within 2.4.

More preferably, a=1.235, b=0.231, c=0.0190.

As preferably, said 3<R<10mm; said 1.5<r<4.0mm;

Further preferably, the diameter of the heat pipe at the capillary position is 30-40mm, more preferably 32mm;

Further preferably, the diameter of the heat pipe without a capillary wick is 5.0-6.4mm;

Further preferably, the pipe diameter of the pipeline flowing from the condensation end to the evaporation end is 5.0-6.4mm;

Further preferably, the diameter of the inlet pipe 11 is 80-200mm; preferably, 120-150mm;

Further preferably, the vertical length of the fins is 780-1500 mm, preferably 1200 mm; the longitudinal extension of the fins accounts for 95% of the difference between the outer diameter of the evaporation end 6 and the inner diameter of the gas outlet channel 4 . Under this length, the overall heat transfer capacity of the fins is significantly improved, and the heat transfer coefficient is also within a suitable range, and the impact on the breaking effect of the boundary layer and the effect of fluid flow is relatively small. The gas is sucked into the gas cavity. The external hot gas first exchanges heat with the relatively low temperature gas that is being discharged to the outside in the air inlet channel 5. After the heat exchange, the low temperature gas transfers heat to the evaporation end through the fins, and the heat exchange with the fluid The metal outer wall also has a heat conduction function, and the two work together to complete the gas heat exchange. After the gas begins to enter the gas chamber, the hotter gas first slowly passes through the fin channel of the loop heat pipe evaporator, and completes heat exchange with the medium in the loop heat pipe, and its own temperature is significantly reduced. The remaining gas goes deep into the gas chamber 7, and exchanges heat with the external fluid through the metal outer wall of the chamber. With the further heat exchange of the gas, the main cold source is provided by the loop heat pipe at this time. The evaporation end 6 of the loop heat pipe absorbs the heat of the hot gas, evaporates the liquid working medium into a gaseous state, and then transfers the heat to the external fluid through the loop heat pipe condensation end 8 wound outside the gas chamber, so that the gaseous working medium is condensed into a gaseous state. Liquid, and the anti-gravity loop heat pipe has the feature of allowing the liquid to flow back.

Preferably, the capillary core of the loop heat pipe is prepared by powder metallurgy. Before starting, the capillary core of the evaporator of the loop heat pipe, the supplementary cavity and the infusion tube are filled with working fluid, while the steam channel, condenser and steam tube are in a two-phase state.

The cooling chamber adopts a coordinated heat exchange method supplemented by fluid cooling and mainly anti-gravity loop heat pipes, which can greatly increase the gas cooling speed and increase the heat exchange capacity.

Preferably, the condensing end of the loop heat pipe is wound outside the gas chamber to increase the heat dissipation area.

Compared with the prior art, the present invention has the following advantages:

1) When the sun is sufficient, the heat of the sun is used to directly heat the device, and the solar energy can be stored in the heat storage medium in the heat storage device. When there is no light, the stored energy is used to heat the device, so that there is no need to input energy at all, and the purpose of soil heating is achieved.

2) As an efficient heat transfer tool, the loop heat pipe has a simple principle and a compact structure, which can effectively increase the air heat exchange area and significantly improve the cooling efficiency.

3) The loop heat pipe condenser is wound outside the condensation chamber and fully contacts with the external soil to increase the heat dissipation of the air at the evaporating end of the heat pipe and improve the cooling efficiency.

4) Microorganisms are used as the undertaker of the purification task instead of chemical products. The remaining substances after soil purification are completely harmless to the natural ecological structure and can be absorbed and utilized by it, so there will be no secondary pollution and no consumption new chemical products.

5) As the undertaker of purification, microorganisms have low maintenance cost and can be used for a long time without inputting new materials, which perfectly cooperates with our design device.

Although the present invention has been disclosed above with preferred embodiments, the present invention is not limited thereto. Any person skilled in the art can make various changes and modifications without departing from the spirit and scope of the present invention, so the protection scope of the present invention should be based on the scope defined in the claims.

Claims (10)

1. a kind of solar energy loop heat pipe system of microorganism soil purification, it is characterized in that, this system comprises solar energy device and loop heat pipe device, and described solar device comprises solar heat collector, heat exchanger and blower fan, and described heat exchanger Connect the solar heat collector, the air blower will input the air into the heat exchanger, after being heated into hot air in the heat exchanger, it enters the loop heat pipe device; the loop heat pipe device includes an air inlet channel, an air outlet channel, a ring A loop heat pipe and a gas chamber, the loop heat pipe includes an evaporation end and a condensation end, the evaporation end is located on the upper part of the condensation end, a capillary wick is set in the pipeline leading to the evaporation end from the condensation end, the condensation end is set On the outer wall of the chamber; the gas chamber is arranged in the soil, the loop heat pipe is an anti-gravity heat pipe, the outlet of the air inlet channel and the inlet of the air outlet channel communicate with the gas chamber, and the hot air passes through the air inlet When the channel is introduced into the gas chamber, it exchanges heat with the evaporation end, and the condensation end conducts heat to the soil around the gas chamber. 2. The system of claim 1, wherein the gas chamber is a flat structure. 3. The system according to claim 2, wherein the condensing end is a coil tube located on the lower outer wall of the gas chamber. 4. The system according to claim 3, wherein a groove is provided on the lower outer wall of the gas chamber, and the coil is arranged in the groove. 5. The system of claim 1, wherein the condensing end is an annular tube wound around the outer wall of the gas chamber. 6. The system according to claim 1, wherein a part or all of the capillary wick is arranged at the evaporation end. 7. The system according to claim 1, wherein the evaporating end includes a riser, and at least a part of the riser is provided with a capillary core, thereby realizing the effect of an anti-gravity heat pipe; The outer wall of the evaporation end is surrounded by longitudinal vertical fins; the air outlet channel is arranged between two adjacent vertical fins and is in contact with the adjacent two vertical fins; the downcomer of the heat pipe is arranged Between and in contact with two adjacent vertical fins; at least a part of the riser tube and the downcomer tube are arranged in the air inlet channel. 8. The system of claim 1, wherein the top and bottom of the gas chamber are planar structures. 9. The system according to claim 1, wherein the system is provided with a plurality of gas chambers, and the gas inlet channels of the plurality of gas chambers are in a parallel structure. 10. The system according to claim 1, wherein the condensing ends are arranged on the upper, lower and side outer walls of the gas chamber.