CN110243081B - Solar loop heat pipe system for purifying microbial soil - Google Patents
Solar loop heat pipe system for purifying microbial soil Download PDFInfo
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- CN110243081B CN110243081B CN201810636600.5A CN201810636600A CN110243081B CN 110243081 B CN110243081 B CN 110243081B CN 201810636600 A CN201810636600 A CN 201810636600A CN 110243081 B CN110243081 B CN 110243081B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
- F28D15/043—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure forming loops, e.g. capillary pumped loops
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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
Technical Field
The invention relates to the field of solar energy and heat pipes, in particular to a solar loop heat pipe system for purifying microbial soil.
Background
The heat pipe technology is a heat transfer element called a heat pipe invented by George Grover of national laboratory of los Alamos (L os Alamos) in 1963, which makes full use of the heat conduction principle and the rapid heat transfer property of a phase change medium, and the heat of a heating object is rapidly transferred to the outside of a heat source through the heat pipe, and the heat conduction capability of the heat transfer element exceeds the heat conduction capability of any known metal.
The heat pipe technology is widely applied to the industries of aerospace, military industry and the like, and since the heat pipe technology is introduced into the radiator manufacturing industry, the design idea of the traditional radiator is changed for people, the single heat radiation mode that a high-air-volume motor is used for obtaining a better heat radiation effect is avoided, the heat pipe technology is adopted for enabling the radiator to obtain a satisfactory heat exchange effect, and a new place in the heat radiation industry is opened up. At present, the heat pipe is widely applied to various heat exchange devices, including the field of nuclear power, such as the utilization of waste heat of nuclear power.
With the rapid development of industrialization, the problem of soil pollution is increasingly serious, and the search for a green and efficient soil purification method is urgent. The soil remediation industry has gradually emerged since the eighties of the last century. The study work of soil remediation is carried out by students such as Liuyang and Chen Tong, etc., a method for catalyzing and degrading organic pollutants by using microorganisms is provided, and the purpose of treatment is achieved by changing various environmental conditions to strengthen the degradation effect of the microorganisms. However, the scheme has the following defects: on one hand, energy is not saved, and on the other hand, the energy is limited by more geographical limitations and natural conditions.
The invention provides a solar loop heat pipe system for microbial soil purification, which ensures the activity of microbes through the extremely high heat transfer efficiency of a loop heat pipe and accurately controls the temperature, the humidity and the pH value of soil so as to achieve the effects of quickly purifying the soil and removing pollution.
Disclosure of Invention
The invention provides a solar loop heat pipe system for microbial soil purification, which solves the technical problems in the prior art by combining solar energy and a loop heat pipe and utilizing the performance of an antigravity heat pipe and the expanded heat exchange area.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a solar loop heat pipe system for microbial soil purification comprises a solar device and a loop heat pipe device, wherein the solar device comprises a solar thermal collector, a heat exchanger and a fan, the heat exchanger is connected with the solar thermal collector, the fan inputs air into the heat exchanger, and the air enters the loop heat pipe device after being heated into hot air in the heat exchanger; the loop heat pipe device comprises an air inlet channel, an air outlet channel, a loop heat pipe and a gas chamber, wherein 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 of the condensation end leading to the evaporation end, and the condensation end is arranged on the outer wall of the gas chamber; the gas cavity 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 cavity, heat exchange is carried out between hot air and the evaporation end in the process of introducing the hot air into the gas cavity from the air inlet channel, and the condensation end conducts the heat to the soil around the gas cavity.
Preferably, the gas chamber is of a flat construction.
Preferably, the condensation end is a coil located on the lower wall of the gas chamber.
Preferably, the lower wall surface of the gas chamber is provided with a groove, and the coil is arranged in the groove.
Preferably, the condensing end is an annular tube wrapped around the outer wall of the gas chamber.
Preferably, a part or the whole of the capillary wick is arranged at the evaporation end.
Preferably, the evaporation end comprises a riser, and at least one part of the riser is provided with a capillary core, so that the function of a counter-gravity heat pipe is realized; a pipeline with a condensing end flowing to an evaporating end is arranged in the center of the capillary core, and a longitudinal vertical fin is arranged on the outer wall surface of the evaporating end in a surrounding manner; the air outlet channel is arranged between and in contact with two adjacent vertical fins; the descending tube of the heat pipe is arranged between and contacted with the two adjacent vertical fins; at least a portion of the upleg and downleg are disposed within the air inlet passage.
Preferably, the top and bottom of the gas chamber are planar structures.
Preferably, a plurality of gas chambers are provided, the gas inlet passages of the plurality of gas chambers being in a parallel configuration.
Preferably, the evaporation end is arranged on the inlet pipe of the gas chamber, at least one part of the evaporation end is filled with the capillary core, the center of the capillary core is provided with a pipeline from the condensation end to the evaporation end, and the outer wall surface of the evaporation end is provided with longitudinal vertical fins in a surrounding mode.
Preferably, the gas outlet channel is disposed between and in contact with two adjacent vertical fins.
Preferably, the condensation end pipeline flowing to the evaporation end is arranged between and in contact with two adjacent vertical fins.
The pipeline is a plurality of, the gas outlet passageway is a plurality of, the pipeline equals with gas outlet passageway's quantity.
Further preferably, the pipes are arranged between adjacent gas outlet channels which flow between adjacent evaporation end to condensation end pipes.
Further preferably, the distance between the center of the pipeline of the evaporation end flowing to the condensation end and the center of the adjacent gas outlet channel is the same; the distance between the center of the gas outlet channel and the center of the pipeline flowing from the adjacent gas evaporation end to the condensation end is the same.
Preferably, the radius of the gas outlet channel is R, the radius of the pipeline from the evaporation end to the condensation end is R, and the included angle between adjacent fins is A, so that the following requirements are met:
Sin(A)＝a*(r/R)-b*(r/R)2-c；
a, b, c are parameters,
wherein 1.23< a <1.24, 0.225< b <0.235, 0.0185< c < 0.0195;
14°<A<30°；
0.24<r/R<0.5；
further preferably, 0.26< R/R < 0.38.
Compared with the prior art, the invention has the following advantages:
1) the invention provides a soil purification device with a novel structure, which utilizes solar energy and a counter-gravity heat pipe to exchange heat, transfers heat in gas to soil, and ensures the activity of microorganisms through extremely high heat transfer efficiency of a loop heat pipe and accurate control of soil temperature, humidity and pH value so as to achieve the effects of quickly purifying soil and removing pollution.
2) The condensing end of the antigravity heat pipe is wound or coiled on the outer wall of the gas chamber, and the area of the gas chamber is enlarged, so that the heat exchange area is increased, and the heat exchange effect is improved.
3) The invention improves and designs the structure of the loop heat pipe evaporation end, and further improves the heat exchange coefficient.
4) According to the invention, through a large number of numerical simulation and experiments, included angles between the gas outlet channel of the loop heat pipe, the pipeline of the evaporation end flowing to the condensation end and the adjacent fins are optimized, and the heat exchange efficiency is further improved.
Drawings
Fig. 1 is a schematic structural diagram of a solar heat collection system of the present invention.
FIG. 2 is a schematic view of one embodiment of a heat pipe apparatus of the present invention.
Fig. 3 is a bottom view of fig. 2.
FIG. 4 is a schematic view of another embodiment of a heat pipe apparatus;
fig. 5 is a cross-sectional view a-a in fig. 4.
Fig. 6 is a schematic diagram of a multi-evaporation-end to condensation-end pipeline (descending section) according to the present invention.
Fig. 7 is a schematic view of a pipe connection structure for providing a capillary wick according to the present invention.
Fig. 8 is a schematic view of a structure in which a plurality of gas outlet pipes are provided.
The reference numbers are as follows: the solar heat collector comprises a solar heat collector body, a fan body, a heat exchanger body, a heat pipe evaporator, a loop heat pipe condenser.
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings.
Herein, if not specifically stated, "/" denotes division, "×", "x" denotes multiplication, referring to formulas.
The following detailed description of embodiments of the invention refers to the accompanying drawings.
As shown in fig. 1, a solar loop heat pipe system for microbial soil purification comprises a solar thermal collector 1, a heat exchanger 3 and a fan 2, wherein the heat exchanger 3 is connected with the solar thermal collector 1, the fan 2 inputs air into the heat exchanger 3, and the air enters an air inlet channel 5 of a loop heat pipe device after being heated into hot air in the heat exchanger 3. The heat pipe is arranged in soil and used for repairing the soil.
The invention utilizes solar energy to heat the soil to generate a heat source, applies the solar energy to the soil remediation function, saves energy and greatly reduces development cost.
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, the high-temperature molten salt tank 14 is arranged at the upstream of the heat exchanger 3, and the low-temperature molten salt tank 15 is arranged at the downstream of the heat exchanger 3. Through setting up high temperature molten salt jar 14 and low temperature molten salt jar 15, store solar energy's high temperature waste heat energy and low temperature waste heat energy to satisfy and carry out the heat utilization at weather badly or evening.
Referring to fig. 1, the mature solar photo-thermal technology is utilized to generate controllable high-temperature hot air, and the generated high-temperature hot air is introduced into a heat pipe device buried in soil. Thereby saving energy.
The heat pipe device comprises an antigravity loop heat pipe, as shown in fig. 4 and 5, the heat pipe comprises an evaporation end 6 and a condensation end 8, the evaporation end 6 is located above the condensation end 8, a part of the evaporation end 6 is arranged at the fluid rising section, and at least a part of the evaporation end of the fluid rising section is provided with a capillary wick 13, as shown in fig. 6.
Preferably, the evaporation end comprises two parts, namely an evaporation end flow direction condensation end pipeline (descending section) 9 and an ascending section. Preferably, a condensation end flow to the evaporation end line 10 is arranged in the rising section.
The solar loop heat pipe system for microbial soil purification shown in fig. 2 comprises an air inlet channel 5, an air outlet channel 4, a loop heat pipe and a gas chamber 7, wherein the loop heat pipe shown in fig. 4 comprises an evaporation end 6 and a condensation end 8, the evaporation end 6 is positioned on the upper part of the condensation end 8, a capillary wick is arranged in a pipeline leading from the condensation end 8 to the evaporation end 6, and the condensation end 8 is arranged on the outer wall of the gas chamber; the gas chamber 7 is arranged in soil, the loop heat pipe is an antigravity heat pipe, an outlet of the air inlet channel 5 and an inlet of the air outlet channel 4 are communicated with the gas chamber 7, heat exchange is carried out between hot air and the evaporation end in the process of introducing the hot air into the gas chamber 7 from the air inlet channel 5, and the condensation end conducts the heat to the soil around the gas chamber.
The invention provides a soil remediation system of a loop heat pipe with a novel structure, and the loop heat pipe is used as a high-efficiency heat transfer tool, so that the principle is simple, the structure is compact, and the cooling efficiency is obviously improved.
Preferably, at least a portion of the evaporator end 6 of the loop heat pipe is mounted 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, said gas inlet channel 5 is at least partly arranged in the gas chamber 7 inlet pipe. Through so setting up, can make the gas in the gas inlet passage 5 directly participate in the prosthetic heat transfer of soil through the inlet tube, make gaseous under the combined action of fluid and loop heat pipe, further cool off, improve the heat transfer effect.
Preferably, the gas chamber 7 is made of a heat conducting material, preferably a metal, such as copper, aluminum. Through the material of the gas cavity, the heat of the gas can be transferred outwards through the cavity, so that a heat exchange mode is added, and the heat of the gas is transferred to external fluid through the loop heat pipe and the gas cavity.
Preferably, the gas chamber 7 is of a flat construction, as shown in figure 2. Through setting up flat tubular construction, can make gas chamber and soil area of contact increase.
Preferably, the gas chamber 7 has a circular configuration, as seen from the bottom, as shown in fig. 3. Through setting up circular structure, can make the heat to the peripheral heat dissipation even.
Preferably, the condensation end 8 is a coil located on the lower wall of the gas chamber, as shown in fig. 3.
Preferably, the air outlet channel 4 is provided with a plurality of channels. Through the cooperation of many air outlet pipelines, the discharge of realization air that can be quick.
Preferably, the inlet end of the air outlet channel 4 extends from the centre of the gas chamber to the edge of the gas chamber. Such as fig. 8. Of course, fig. 8 only shows the air outlet channel 4, other components not being shown. The inlet end of the air outlet channel 4 is arranged at the edge of the air chamber, so that air can be forced to flow from the edge of the central flow channel, the air participates in the whole heat exchange process, and the short circuit of hot air is avoided.
Preferably, as shown in fig. 3, the lower wall surface of the gas chamber is provided with a groove, and the coil is arranged in the groove. So as to facilitate the fixation of the condensation end.
Preferably, the coiled tube structure extends 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. Through so setting up, can make the heat begin the heat dissipation from the outer end of circular structure earlier, then inwards gradually. Because the outer coil is larger in diameter, more heat is required, and because the hot air enters the gas chamber, the hot air transfers heat outwardly through the chamber, as opposed to the central heat source, which is the most efficient because the hot air enters the central portion first. Through the arrangement, the soil can be uniformly heated on the whole.
Preferably, the distribution density of the coils is increased (the spacing between adjacent coils is increased and decreased) in the radial direction along the center of the circular structure. The main reason is that by so arranging, heat can be dissipated from the outer end of the circular structure first and then gradually inwards. Because the pipe diameter of the coil pipe of outer end is big, need more heats for whole heat dissipation is even, strengthens soil remediation effect. So that the overall repair is uniform.
Further preferably, the distribution density of the coils increases to a greater and greater extent, preferably in the radial direction along the centre of the circular structure. Numerical simulation and experiments show that the uniformity of soil heating can be further improved through the structure.
Preferably, the diameter of the coil increases to a radial direction along the center of the circular structure. The main reason is that by so arranging, heat can be dissipated from the outer end of the circular structure first and then gradually inwards. Because the pipe diameter of the coil pipe of outer end is big, need more heats for whole heat dissipation is even, strengthens soil remediation effect. So that the overall repair is uniform.
Further preferably, the diameter of the coil increases to a greater and greater extent in the radial direction along the center of the circular structure. Numerical simulation and experiments show that the uniformity of soil heating can be further improved through the structure. The soil restoration effect is enhanced, and the overall restoration is uniform.
Preferably, the condensing end is an annular tube wrapped around the outer wall of the gas chamber.
Preferably, the gas chamber 7 is of a square configuration when viewed from below.
As another example (not shown), the gas chamber 7 is a round tube structure, and the condensation end is wound around the round tube. The circular tube is perpendicular to the gas chamber inlet tube 11.
Preferably, an electric heater for auxiliary heating is arranged in the gas chamber. When the heat of the air is insufficient, the heating is supplemented by the electric heater.
Preferably, the air conditioner further comprises a control system for controlling 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 starts the electric heater to heat.
If the measured air temperature is higher than a prescribed 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 described in figure 2 is a preferred embodiment. However, the structure of fig. 4 is inferior to the structure of fig. 2 in terms of expanding the heat exchange area, and the structure of fig. 4 has difficulty in being buried in soil, but the structure of fig. 4 can also achieve the soil restoration function, and thus, the structure also belongs to one aspect of the present application. As shown in fig. 4, the gas chamber 7 has a diameter gradually increasing from the position where the inlet pipe is connected to the bottom, and then gradually decreasing to a certain position. The gas circulation is completed, and the heat exchange efficiency between the gas and the wall of the gas chamber is increased.
Preferably, as shown in fig. 2, the bottom and top of the gas chamber 7 are planar structures.
Preferably, a plurality of gas chambers 7 are provided, the gas inlet channels 5 of which are of parallel configuration.
Preferably, the gas outlet channels 5 of the plurality of gas chambers are in a parallel configuration.
Preferably, the evaporation end 6 of the loop heat pipe is arranged on the gas chamber inlet pipe, and the condensation end 8 of the loop heat pipe is wound outside the gas chamber and is in direct contact with the external soil. The loop heat pipe condenser is wound outside the gas chamber and fully contacts with external soil, so that heat dissipation of gas at the evaporation end of the heat pipe is increased, and cooling efficiency is improved.
As shown in fig. 4, the condensing end is a circular tube wound around the outer wall of the gas chamber.
Preferably, the condensing end 8 of the loop heat pipe is wound more and more densely on the outer wall of the gas chamber 6 from the upper portion to the lower portion in the height direction (the spacing between the loop pipes is smaller and larger). The main reason is to concentrate the heat on the lower part as much as possible for heat exchange, and because the temperature in the next step is low, more heat is needed, and the soil remediation effect is enhanced. So that the overall repair is uniform. Experiments show that the repairing effect can be further improved by about 11% by the structure.
Further preferably, the winding density of the condensation end 8 of the loop heat pipe on the outer wall of the gas chamber 6 is increased more and more from the upper part to the lower part along the height direction. Experiments show that the repairing effect can be further improved by about 5 percent through the structure.
Preferably, at least one part of the evaporation end 6 is provided with a capillary core 13, the capillary force of the capillary core provides power for the working medium to flow back and circulate, and meanwhile, the amount of the flowing back working medium meets the requirement of heat transfer, so that the effect of the antigravity heat pipe is realized.
By arranging the capillary core 13, the capillary core 13 is arranged at the evaporation end, so that the ascending section 6 of the evaporation end naturally generates flow resistance, and the steam generated at the evaporation end naturally flows to the evaporation end with low resistance and flows to the condensation end pipeline 9, thereby forming the antigravity heat pipe.
Preferably, the capillary wick 13 is only arranged in the rising section of the evaporation end, preferably in a part of the rising section. Such as shown in fig. 4, 6, and 7.
Preferably, at least a part of the gas outlet channel 4 is arranged in the inlet pipe of the gas chamber, the cold gas of the gas outlet pre-cooling the hot gas of the gas inlet. Through the heat exchange of outlet gas and inlet gas, further realize the heat transfer effect, increase the condensation efficiency of water.
Preferably, as shown in fig. 4, the evaporation end is disposed at the inlet tube of the gas chamber, the rising section of the evaporation end is filled with the capillary wick 13 to provide a sufficient capillary force, the center of the capillary wick 13 is provided with the pipeline 10 from the condensation end to the evaporation end, by disposing the pipeline 10 (without the capillary wick), the fluid resistance of the pipeline can be reduced, the working medium flows back more smoothly, the heat transfer capability in the anti-gravity state is improved, and the outer wall surface of the rising section of the evaporation end is provided with the longitudinal vertical fins 12 in a surrounding manner, so that the heat exchange area is increased, and the heat exchange efficiency with the gas is improved.
The pipeline 10 is a gas or liquid pipeline, and realizes flexible arrangement, namely the pipe diameter is small and the pipe is easy to bend. The principle of the loop heat pipe is that if the evaporator side and the pipeline 10 are steam pipelines, the principle is that the evaporator is heated and internal working media are evaporated, steam enters the pipeline 10 along the upper outlet of the evaporator and then flows to the pipeline surrounding the lower part to be contacted with fluid to start condensation, and after the steam is completely condensed, the steam returns to the evaporator under the capillary force of the capillary core of the evaporator, so that the circulation of the working media is realized.
Preferably, the tube 10 communicates with the capillary wick 13. Through the communication, the fluid communication between the capillary wick 13 and the pipeline 10 can be realized, so that if a large pressure is generated due to heat absorption during the liquid ascending through the capillary wick, for example, even bubbles can occur, the pressure of the evaporation section can be equalized through the pipeline 10, and thus the equalization of the pressure is ensured.
Further preferably, the capillary wick 13 extends to the condensation end so as to directly suck up the liquid at the condensation end. Further improving the circulation capacity of the antigravity heat pipe.
Preferably, the capillary wick is distributed along the height direction, as shown in fig. 3. Further preferably, the capillary force of the capillary wick is gradually increased along the height decreasing direction. The closer to the condensation end, the greater the capillary force. Experiments show that the suction force to the liquid can be further improved by adopting the mode, and the suction force can be improved by more than 20% at the same cost, so that the heat exchange effect is improved.
By further analysis, the primary reason may be that as the capillary force near the condensation end becomes larger, the liquid at the condensation end can be rapidly absorbed into the capillary wick, and the liquid continuously flows towards the evaporation end. In the flowing process, the liquid absorbs heat continuously, the temperature is increased due to heat absorption, the density is reduced, the required capillary force is obviously reduced due to density change, and the liquid can be easily sucked upwards under the condition of small capillary force. The reason for this is that the present inventors have conducted extensive experiments and studies, and are not common knowledge in the art.
Further preferably, the capillary force of the capillary wick increases gradually in the height decreasing direction to a larger and larger extent. Experiments show that the suction to liquid can be further improved by adopting the mode, and the suction about 8 percent can be further improved at the same cost, so that the heat exchange effect is improved.
Preferably, the pipeline is formed by a through hole formed in the middle of the capillary core.
Preferably, as shown in fig. 7, the pipe diameter of the heat pipe position where the capillary wick is provided is larger than the pipe diameter of the heat pipe position where the capillary wick is not provided.
Further preferably, as shown in fig. 7, the change in the tube diameter between the tube at the position of the heat pipe where the capillary wick is disposed and the tube at the position of the heat pipe where the capillary wick is not disposed is a continuous change. Further preferably a straight line variation. The pipe at the large pipe diameter position and the pipe at the small pipe diameter position are connected at the joint through a contraction member. The change in the tube diameter of the constriction is a linear change.
Preferably, the gas outlet channel 4 is arranged between and in contact with two adjacent vertical fins 12. Through so setting up, can reduce the mechanism that sets up independent support gas outlet passage 4 for compact structure, outlet passage's cold gas accessible pipeline and fin heat transfer keep the degree of coldness of fin, reinforcing heat transfer effect.
Preferably, the evaporation end flow direction condensation end flow direction evaporation end flow direction condensation end pipe 9 is arranged between and in contact with two adjacent vertical fins. Through so setting up, can reduce the mechanism that sets up independent support gas outlet passage 4 for compact structure, the steam accessible pipeline in the pipeline is short for a short time a small amount of heat transfer to the fin, reduces the whole thermal resistance of system, avoids producing in the evaporimeter overheated under the antigravity condition on ground, slows down the temperature shock phenomenon in the heat pipe start-up process.
Further preferably, the evaporation end flow direction condensation end pipeline 9 is closer to the outer wall of the evaporation end pipeline than the gas outlet channel 4, so that the two heat transfer processes can be simultaneously realized, and the corresponding effects are achieved.
Further preferably, the diameter of the evaporation end to condensation end pipe 9 is smaller than the gas outlet channel 4.
Preferably, the evaporation end flows to the condensation end pipeline 9 along the condensation end where a plurality of evaporation end flows can be arranged, as shown in fig. 4 and 6. Through setting up a plurality of evaporating ends flow direction condensing end pipeline 9, can make the steam that the evaporating end endotherm produced flow to condensing end pipeline 9 through a plurality of evaporating ends and get into the condensing end, further strengthen heat transfer, because the fluid endotherm evaporation in the heat pipe leads to the volume to increase moreover, flows to condensing end pipeline 9 through setting up a plurality of evaporating ends, can further alleviate pressure, improves heat transfer effect.
Further preferably, the vertical fin extends through the center of the inlet pipe of the gas chamber, and the evaporation end rising section pipeline and the inlet pipe of the gas chamber have the same center.
Preferably, the number of the evaporation end flow direction condensation end pipelines 9 is multiple, and the distance between the circle center of the multiple evaporation end flow direction condensation end pipelines 9 and the pipeline at the ascending section of the evaporation end is the same.
Further preferably, an evaporation end flow direction condensation end pipeline 9 is arranged between every two adjacent vertical fins 12. The pipeline 9 from the evaporation end to the condensation end is of a parallel structure.
Preferably, the number of the gas outlet channels 4 is multiple, and the distance between the circle center of the plurality of gas outlet channels 4 and the pipeline at the ascending section of the evaporation end is the same, so that the temperature distribution among the fins is more uniform, and the heat exchange effect is more obvious. It is further preferred that one gas outlet channel 4 is provided between each adjacent two of the vertical fins 12. The gas outlet channels 4 are of a parallel configuration.
Preferably, the number of the evaporation end flow direction condensation end pipelines 9 is multiple, the number of the gas outlet channels 4 is multiple, and the number of the evaporation end flow direction condensation end pipelines 9 is equal to that of the gas outlet channels 4.
Further preferably, the evaporation end flow direction condensation end pipe 9 is arranged between adjacent gas outlet channels 4, and the gas outlet channels 4 flow between the adjacent evaporation end flow direction condensation end pipe 9. Further preferably, the distance between the center of the evaporation end pipeline 9 flowing to the condensation end pipeline and the center of the adjacent gas outlet channel 4 is the same; the distance between the center of the gas outlet channel 4 and the center of the pipeline 9 from the adjacent gas evaporation end to the condensation end is the same. I.e. the evaporation end flow to condensation end pipe 9 is arranged in the middle of the adjacent gas outlet channel 4, and the gas outlet channel 4 flows in the middle of the adjacent evaporation end flow to condensation end pipe 9. That is, as shown in fig. 4, a first connection line is formed between the center of the circle where the evaporation end flows to the condensation end pipeline 9 and the center of the circle of the evaporation end 6, a first connection line and a third connection line are formed between the centers of the circles of the adjacent gas outlet channels 4 and the center of the circle of the evaporation end 6, and a first included angle formed between the first connection line and the second connection line is equal to a second included angle formed between the first connection line and the third connection line. Similarly, a fourth connecting line between the center of the circle of the gas outlet channel 4 and the center of the circle of the evaporation end 6, a fifth connecting line and a sixth connecting line are formed between the centers of the circles of the pipelines 9 flowing to the condensation end and the centers of the circles of the evaporation ends 6 of the adjacent evaporation ends, and a third included angle formed between the fourth connecting line and the fifth connecting line is equal to a fourth included angle formed between the fourth connecting line and the sixth connecting line. I.e. in the circumferential direction, the evaporation end flow to the condensation end line 9 and the outlet channel 4 are evenly distributed.
Through the arrangement, the evaporation end can be ensured to flow to the condensation end pipeline 9 and the gas outlet channel 4 to absorb heat uniformly to the inlet gas, and local heating unevenness is avoided. The gas outlet channel 4 can continuously participate in heat exchange after absorbing heat, and the heat is transferred to the evaporation end through the fins.
In numerical simulation and experiments, it is found that the difference between the pipe diameters of the gas outlet channel 4 and the evaporation end flowing to the condensation end pipeline 9 cannot be too large or too small, and if the difference is too large, the distance between the gas outlet channel 4 and the evaporation end flowing to the condensation end pipeline 9 is too far, so that the gas heat exchange between the channel 4 and the evaporation end flowing to the condensation end pipeline 9 is poor, the overall heat exchange is not uniform, and if the difference is too small, the distance between the gas outlet channel 4 and the evaporation end flowing to the condensation end pipeline 9 is too close, so that the gas near the outer wall of the inlet pipe 11 and/or the gas near the outer wall of the evaporation end 6 are poor, and the gas heat exchange in the overall inlet pipe 11 is not uniform; the same reason, the contained angle between adjacent fin 12 can not be too big, can lead to the distribution fin few too big, the heat transfer effect is too good, lead to gas outlet passageway 4 and evaporating end flow direction condensing end pipeline 9 quantity of distribution too little simultaneously, lead to the heat transfer inhomogeneous and the heat transfer effect is not good, on the same principle, the contained angle between adjacent fin 12 can not be too little, lead to the fin distribution too closely too little, the flow resistance greatly increases, and gas outlet passageway 4 and evaporating end flow direction condensing end pipeline 9's pipe diameter differs not greatly, but their heat transfer capacity of equal area is very different, therefore the heat transfer is inhomogeneous under this kind of condition, lead to the heat transfer effect not good.
It is therefore necessary to determine the optimum dimensional relationship by extensive numerical simulations and experiments thereof.
The radius of the gas outlet channel 4 is R, the radius of the evaporating end flowing to the condensing end pipeline 9 is R, the included angle between adjacent fins is A, and the following requirements are met:
Sin(A)＝a*(r/R)-b*(r/R)2-c；
a, b, c are parameters,
wherein 1.23< a <1.24, 0.225< b <0.235, 0.0185< c < 0.0195;
14°<A<30°；
0.24< R/R < 0.5; further 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 the error is basically within 2.4 after experimental verification.
More preferably, a is 1.235, b is 0.231, and c is 0.0190.
Preferably, said 3< R <10 mm; 1.5< r <4.0 mm;
further preferably, the pipe diameter of the heat pipe at the position where the capillary core is arranged is 30-40mm, and further preferably 32 mm;
further preferably, the pipe diameter of the heat pipe without the capillary core is 5.0-6.4 mm;
further preferably, the pipe diameter of the pipeline from the condensation end to the evaporation end is 5.0-6.4 mm;
further preferably, the pipe diameter of the inlet pipe 11 is 80-200 mm; preferably, 120-;
further preferably, the length of the fins in the vertical direction is 780-1500mm, preferably 1200 mm; the length of the longitudinal extension of the fins is 95% of the difference between the outer diameter of the evaporation end 6 and the inner diameter of the gas outlet channel 4. The whole heat exchange capacity of the fin is remarkably improved under the length, the heat exchange coefficient is also in a proper range, and after the gas is filtered with relatively small influence on the damage effect of a boundary layer and the fluid flowing effect, the filtered gas is sucked into the gas cavity through the induced draft fan. The external hot gas exchanges heat with the relative low-temperature gas which is discharged outdoors in the air outlet channel in the air inlet channel 5, the heat of the low-temperature gas after heat exchange is transferred to the evaporation end through the fins, the low-temperature gas and the metal outer wall of the fluid have a heat conduction function, and the heat exchange of the gas is completed under the combined action of the heat and the metal outer wall of the fluid. After the gas begins to enter the gas chamber, hotter gas slowly passes through the fin channel of the loop heat pipe evaporator to exchange heat with the medium in the loop heat pipe, and the temperature of the hotter gas is obviously reduced. The residual gas goes deep into the gas chamber 7, exchanges heat with the external fluid through the metal outer wall of the cavity, and along with the further heat exchange of the gas, the main cold source is provided by the loop heat pipe at the moment. The evaporation end 6 of the loop heat pipe absorbs the heat of the hot gas, the liquid working medium is evaporated into a gas state, then the heat is conducted to external fluid through the loop heat pipe condensation end 8 wound outside the gas chamber, the gas working medium is condensed into a liquid state, and the antigravity loop heat pipe has the characteristic of enabling the liquid to flow back.
Preferably, the loop heat pipe capillary wick is prepared by using a powder metallurgy method. Before starting, the capillary core, the supplement cavity and the liquid conveying pipe of the evaporator of the loop heat pipe are filled with working medium, and the steam channel, the condenser and the steam pipe are in two-phase states.
The cooling chamber part adopts a cooperative heat exchange mode of taking fluid cooling as an auxiliary and taking an antigravity loop heat pipe as a main, so that the gas cooling speed can be greatly improved, and the heat exchange quantity is improved.
Preferably, the condensation end of the loop heat pipe is wound outside the gas chamber, so that the heat dissipation area is increased.
Compared with the prior art, the invention has the following advantages:
1) when sunlight is sufficient, the device is directly heated by the heat of the sunlight, and the solar energy can be stored in the heat storage medium in the heat storage device. When no illumination is available, the device is heated by utilizing the stored energy, so that the purpose of heating the soil without inputting energy is achieved.
2) The loop heat pipe is used as an efficient heat transfer tool, has a simple principle and a compact structure, can effectively increase the air heat exchange area, and obviously improves the cooling efficiency.
3) The loop heat pipe condenser is wound outside the condensing chamber and fully contacts with external soil, so that heat dissipation of air at the evaporation end of the heat pipe is increased, and cooling efficiency is improved.
4) The microorganisms are used as the undertaker of the purification task, but not the chemical products, and the residual substances after the soil purification are substances which are completely harmless to the natural ecological structure and can be absorbed and utilized by the natural ecological structure, so that the secondary pollution can not be generated, and the new chemical products can not be consumed.
5) The microorganism is used as a purification bearer, has low maintenance cost, can be used for a long time without inputting new data, and is perfectly matched with the design device of the people.
Although the present invention has been described with reference to the preferred embodiments, it is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (7)
1. A solar loop heat pipe system for microbial soil purification is characterized by comprising a solar device and a loop heat pipe device, wherein the solar device comprises a solar heat collector, a heat exchanger and a fan; the loop heat pipe device comprises an air inlet channel, an air outlet channel, a loop heat pipe and a gas chamber, wherein 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 of the condensation end leading to the evaporation end, and the condensation end is arranged on the outer wall of the gas chamber; the gas cavity 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 cavity, the hot air exchanges heat with the evaporation end in the process of being introduced into the gas cavity from the air inlet channel, and the condensation end conducts the heat to the soil around the gas cavity;
the gas chamber is a flat structure;
the condensation end is a coil pipe positioned on the outer wall surface of the lower part of the gas chamber;
the evaporation end comprises a riser, and at least one part of the riser is provided with a capillary core, so that the effect of the antigravity heat pipe is realized; a pipeline with a condensing end flowing to an evaporating end is arranged in the center of the capillary core, and a longitudinal vertical fin is arranged on the outer wall surface of the evaporating end in a surrounding manner; the air outlet channel is arranged between and in contact with two adjacent vertical fins; the descending tube of the heat pipe is arranged between and contacted with the two adjacent vertical fins; at least a portion of the riser and downcomer are disposed within the air inlet passage.
2. The system of claim 1, wherein the lower exterior wall surface of the gas chamber is provided with grooves and the coils are disposed in the grooves.
3. The system of claim 1, wherein the condensing end is an annular tube wrapped around an outer wall of the gas chamber.
4. The system of claim 1, wherein a portion or all of the capillary wick is disposed at the evaporation end.
5. The system of claim 1, wherein the top and bottom of the gas chamber are planar structures.
6. The system of claim 1, wherein the system provides a plurality of gas chambers having gas inlet passages in a parallel configuration.
7. The system of claim 1, wherein the condensing end is provided on an outer wall surface of an upper portion, a lower portion and a side portion of the gas chamber.
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| CN201810196438X | 2018-03-09 | ||
| CN201810196438 | 2018-03-09 |
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| CN201810636600.5A Active CN110243081B (en) | 2018-03-09 | 2018-06-20 | Solar loop heat pipe system for purifying microbial soil |
| CN201810635888.4A Active CN110243080B (en) | 2018-03-09 | 2018-06-20 | Microbial soil purification solar loop heat pipe system with variable heat pipe density |
| CN201810636976.6A Withdrawn CN108801018A (en) | 2018-03-09 | 2018-06-20 | A kind of microbe soil purification solar energy loop circuit heat pipe system of heat pipe caliber height change |
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| CN201810635888.4A Active CN110243080B (en) | 2018-03-09 | 2018-06-20 | Microbial soil purification solar loop heat pipe system with variable heat pipe density |
| CN201810636976.6A Withdrawn CN108801018A (en) | 2018-03-09 | 2018-06-20 | A kind of microbe soil purification solar energy loop circuit heat pipe system of heat pipe caliber height change |
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| CN109631644A (en) * | 2018-12-03 | 2019-04-16 | 北京工业大学 | Runner preheating device between a kind of energy-saving narrow deep space under suitable adverse circumstances |
| CN111811302B (en) * | 2019-04-11 | 2021-11-30 | 山东大学 | Coil pipe type loop heat pipe |
| CN112556466B (en) * | 2019-09-26 | 2022-03-04 | 中北大学 | Temperature difference loop heat pipe system |
| CN113108491B (en) * | 2020-01-11 | 2022-08-09 | 山东鑫瑞安装工程有限公司 | Solar heat collecting pipe |
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| CN110243080A (en) | 2019-09-17 |
| CN108801018A (en) | 2018-11-13 |
| CN110243080B (en) | 2020-08-11 |
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