CN112833692B - Radian-variable straight-plate uniform-temperature loop heat pipe - Google Patents
Radian-variable straight-plate uniform-temperature loop heat pipe Download PDFInfo
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- CN112833692B CN112833692B CN202110022558.XA CN202110022558A CN112833692B CN 112833692 B CN112833692 B CN 112833692B CN 202110022558 A CN202110022558 A CN 202110022558A CN 112833692 B CN112833692 B CN 112833692B
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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 loop heat pipe which comprises an evaporation part, a condensation part and an evaporation pipe, wherein liquid absorbs heat and evaporates in the evaporation part, wherein an acute angle formed by a first straight line wall and an inner wall is smaller than an acute angle formed by a second straight line wall and the inner wall, the first straight line wall and the second straight line wall extend towards the flowing direction of fluid, a plurality of layers of temperature equalizing parts are arranged on the inner wall of the evaporation pipe along the flowing direction of steam, and the total radian of an arc formed by the temperature equalizing parts on the same layer and the inner wall is smaller and smaller along the flowing direction of the steam. The invention provides a novel loop heat pipe, which enables the flow space required to be arranged to be larger and larger through radian change so as to reduce the flow resistance, and the temperature equalizing effect achieves the basically same effect on the aspects of reducing the resistance and saving the material cost.
Description
Technical Field
The invention relates to a loop heat pipe, in particular to a loop heat pipe provided with a temperature equalizing part.
Background
The heat pipe technology was Ross Alamos (Los Alamos) in 1963National laboratoryGeorge Grover, a heat transfer called "heat pipe" of the inventionComponentThe heat conduction principle and the quick heat transfer property of the phase change medium are fully utilized, the heat of a heating object is quickly transferred to the outside of a heat source through the heat pipe, and the heat conduction capability of the heat pipe 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.
The present heat pipe, especially the loop heat pipe with multiple pipes, includes double collecting pipes, one evaporating pipe and one condensing pipe to raise the heat exchange efficiency of the heat pipe.
In the flowing process of the fluid in the evaporating pipe, the evaporating pipe is generally a vapor-liquid two-phase flow with vapor as the main component, so that the fluid in the evaporating pipe is a vapor-liquid mixture, and the existence of the vapor-liquid two-phase flow affects the heat absorption efficiency of the evaporating pipe.
In the research, it is found that the temperature of the fluid at different positions of the evaporation tube is not uniform no matter the heat absorption end absorbs heat, or the evaporation tube keeps warm, for example, the side with good heat insulation effect has high temperature, the position with poor heat insulation effect has low temperature, the temperature of the fluid at different positions in the evaporation tube is different, the temperature in the evaporation tube is not uniform due to different temperatures, so that the heat dissipation of the condensation sections at different positions is different after entering the heat release end, especially when a plurality of heat release ends and corresponding heat utilization components are involved, the heat absorption of the heat utilization components caused by different heat release ends is not uniform, the heat utilization components are overheated or overcooled, and the operation is affected. Under the condition that a plurality of heat absorption ends are arranged, the different heat sources of the heat absorption ends cause different fluid temperatures at different positions of a condensation part of the heat pipe, so that the heat utilization part is overheated or overcooled, and the operation is influenced.
In view of the above problems, the prior patent of the applicant provides a new loop heat pipe, thereby solving the problem of uneven temperature of the fluid inside the heat pipe.
The application is an improvement to the prior application, and the application enables the flow resistance of fluid in the heat pipe to be reduced and the temperature equalizing effect to be optimal by improving the optimization of the prior application structure.
Disclosure of Invention
The present invention provides a new loop heat pipe to solve the above-identified technical problems.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a loop heat pipe comprises an evaporation part, a condensation part and an evaporation pipe, wherein liquid absorbs heat and evaporates in the evaporation part, enters the condensation part through the evaporation pipe to release heat, and then returns to the evaporation part through gravity; the temperature-equalizing device is characterized in that a temperature-equalizing component extending from the inner wall of the evaporation tube to the center of the evaporation tube is arranged in the evaporation tube, the temperature-equalizing component comprises a first straight line wall and a second straight line wall extending from the inner wall, wherein an acute angle formed by the first straight line wall and the inner wall is smaller than an acute angle formed by the second straight line wall and the inner wall, the first straight line wall and the second straight line wall extend towards the flowing direction of fluid, the intersection point of the first straight line wall and the second straight line wall is positioned at the upper part of the connection part of the first straight line wall and the inner wall and is positioned at the upper part of the connection part of the second straight line wall and the inner wall, and the temperature-equalizing component is in a shape formed by the first straight line wall, the second straight line wall and the inner wall rotating along the axis of the evaporation tube; the steam-water heater is characterized in that a plurality of layers of temperature-equalizing parts are arranged on the inner wall of the evaporation pipe along the flowing direction of steam, and the total radian of the circular arcs connecting the temperature-equalizing parts on the same layer with the inner wall is smaller and smaller along the flowing direction of the steam.
Preferably, the total radian of the arcs connecting the temperature equalizing parts and the inner wall of the same layer with each other is gradually reduced along the flowing direction of the steam.
Preferably, the inner wall of the evaporation tube is provided with a pore canal.
Preferably, the condensing part has a plurality of heat radiating ends.
Preferably, the heat sink of at least two heat release ends is independent of each other.
Compared with the prior art, the invention has the following advantages:
1) the invention provides a novel loop heat pipe, which enables the flow space required to be arranged to be larger and larger through radian change so as to reduce the flow resistance, and the temperature equalizing effect achieves the basically same effect on the aspects of reducing the resistance and saving the material cost.
2) The invention provides a novel loop heat pipe, which is characterized in that a linear temperature equalizing part is arranged in an evaporation pipe, so that a part of fluid flows along the temperature equalizing part and is guided to the opposite direction, and the fluid entering the evaporation pipe in the opposite direction is fully mixed with the fluid entering the evaporation pipe in the opposite direction, so that the temperature of the fluid is uniform, the further temperature uniformity is realized, and the service life of a product is prolonged.
3) According to the invention, through carrying out extensive research on the heat exchange rule caused by the change of each parameter of the temperature equalizing part, the structure of the temperature equalizing part of the heat exchanger is optimized under the condition of meeting the flow resistance, so that the optimal outlet fluid temperature equalizing effect is achieved.
4) According to the invention, through reasonable layout, the temperature equalizing parts in adjacent rows are arranged in a staggered manner, so that fluid is further fully mixed, and the temperature is uniform.
5) The invention further promotes the full mixing by setting the distribution change of parameters such as the size, the number angle and the like of the temperature equalizing part along the flowing direction of the fluid.
6) According to the invention, the distance of the temperature equalizing part is widely researched, a formula of the minimum distance is designed, the temperature equalizing and mixing requirements are fully met, the problems of uneven mixing and increased flow resistance are avoided, and the optimal outlet fluid temperature equalizing effect is achieved.
Drawings
FIG. 1 is a schematic diagram of a loop heat pipe configuration of the present invention;
FIG. 2 is a schematic diagram of the heat releasing/absorbing end of the loop heat pipe structure of the present invention;
FIG. 3 is an axial sectional view of the temperature equalizing member provided in the evaporating tube of the present invention;
FIG. 4 is a schematic size diagram of the temperature equalizing part of the evaporating tube of the present invention.
Fig. 5 is a perspective view of 1 temperature equalization member per layer.
Fig. 6 is a perspective view of 3 temperature equalization members per layer.
Fig. 7 is a perspective view of 1 temperature equalization member per layer.
Fig. 8 is an exploded perspective view of the evaporator tube side of fig. 7.
Fig. 9 is a schematic view of a heat releasing/absorbing end structure provided with a communication pipe.
In the figure: 1. evaporation part, 2, condensation part, 3, evaporation pipe, 4, temperature equalizing part, 41 first straight line wall, 42 second straight line wall, 43 intersection point
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings.
In this document, "/" denotes division and "×", "denotes multiplication, referring to formulas, if not specifically stated.
Fig. 1 shows a heat pipe. As shown in fig. 1, the loop heat pipe includes an evaporation portion 1, a condensation portion 2, an evaporation pipe 3 and a condensation pipe 5, and the liquid absorbs heat and evaporates in the evaporation portion 1, enters the condensation portion 2 through the evaporation pipe 3 to release heat, and then returns to the evaporation portion 1 through the condensation pipe 5.
Preferably, the evaporating pipe 3 is externally provided with a heat-insulating layer.
Preferably, the inner wall of the condensation pipe 5 is provided with a capillary structure. By arranging the capillary structure, the liquid is promoted to enter the evaporation part as soon as possible.
Preferably, the liquid is ammonia, methanol, acetone or heptane.
Preferably, the condensation portion is inserted into a casing, and a medicinal liquid, for example, a medicinal liquid for fumigation is provided in the casing. Is used for heating the liquid medicine for fumigation.
Preferably, the condensing part has a plurality of heat radiating ends 21, as shown in fig. 2.
The heat sink as preferably at least two heat emitting ends are independent of each other. Further preferably, the heat sink of each heat emitting end is different.
Preferably, as shown in fig. 2, the evaporation portion has a plurality of heat absorption ends 11, and at least two heat absorption ends have different heat sources.
Preferably, the heat source at each heat sink end is different.
Preferably, the evaporation tube 3 has a circular structure.
As a modification, as shown in fig. 3, a temperature equalizing member 4 extending from an inner wall 51 of the evaporation tube to the center of the evaporation tube is arranged in the evaporation tube 3, and the temperature equalizing member 4 includes a first straight wall 41 and a second straight wall 42 extending from the inner wall, wherein an acute angle formed by the first straight wall 41 and the inner wall is smaller than an acute angle formed by the second straight wall 42 and the inner wall, the first straight wall 41 and the second curved wall 22 extend in the fluid flowing direction, and an intersection 43 of the first straight wall 21 and the second straight wall 42 is located downstream of a connection between the first straight wall 41 and the inner wall 51, and is located downstream of a connection between the second straight wall 42 and the inner wall. The shape of the temperature equalizing member 4 is a shape formed by rotating the first and second linear walls 41 and 42 and the inner wall along the axis of the evaporator tube.
The invention provides a method for realizing uniform temperature of fluid by arranging the temperature equalizing part in the evaporating pipe, leading a part of fluid to flow along the temperature equalizing part and to be guided to the opposite direction, and fully mixing the fluid entering from the opposite direction, thereby realizing the requirement of further heat exchange and prolonging the service life of products. And through the arrangement of the second linear wall, the inclination of the second linear wall is small, so that the fluid guided from the opposite direction can also rotate along the direction of the second linear wall, the buffer is increased, and the flow resistance is reduced.
The temperature equalizing part is respectively provided with the first straight line wall and the second straight line wall, the two straight line walls are arranged, so that the fluid disturbance effect is better, the area of the temperature equalizing part contacting the inner wall is increased, and the stability is improved.
Preferably, the first rectilinear wall 41 at the location of the intersection point 43 forms an angle of 30-60 deg., preferably 45 deg., with the axis of the evaporating tubes. By providing this angle, fluid can be quickly directed to the opposite downstream location, and flow resistance can be further reduced.
Preferably, as shown in fig. 3, a plurality of layers of temperature equalizing members 4 are arranged on the inner wall of the evaporation tube 5 along the height direction, and the temperature equalizing members of adjacent layers are distributed in a staggered manner. Through the staggered distribution of the temperature equalizing parts in adjacent rows, the fluids can fully move to opposite positions mutually in the evaporating pipes, and the full and uniform mixing is ensured. For example, fig. 3, 5 and 7 show that one block is arranged on each layer of temperature equalizing part, and the total radian of the blocks is 150-180 degrees. Of course, multiple blocks of temperature equalization members may be provided per layer, for example, three blocks per layer in FIG. 6 may have a total arc of 150 and 180.
Preferably, the distance between the intersection point and the inner wall of the evaporator tube is 0.3 to 0.5 times, preferably 0.4 times, the diameter of the evaporator tube. With this arrangement, the air has less flow resistance on thorough mixing.
Preferably, the length of the first rectilinear wall is greater than the length of the second rectilinear wall.
Preferably, the total radian of the circular arc connecting the temperature equalizing part and the inner wall in the same layer is 150-180 degrees. This parameter set ensures thorough mixing while meeting the resistance requirements. For example, fig. 2 shows that one block is arranged for each layer of temperature equalizing part, and the total radian of the blocks is 150 degrees and 180 degrees. Of course, each layer of temperature equalization part can be provided with a plurality of blocks, for example, 3 blocks with a total arc of 150 and 180 degrees are provided.
Preferably, the temperature equalizing parts of the A layers are arranged in a plurality, intervals are arranged among the temperature equalizing parts of the A layers, the temperature equalizing parts of the A layers are arranged at equal intervals, the B layers are adjacent layers of the A layers, and the temperature equalizing parts of the B layers are arranged at the intervals of the A layers when viewed from the flowing direction. Through the complementation of the positions of the temperature equalizing parts of the adjacent layers, the fluids can fully move to the opposite positions mutually in the evaporation tube, and the full and uniform mixing is ensured. It should be noted that the layer a and the layer B are not specifically designated herein, and A, B is only used as a distinction and is used as an adjacent layer.
Preferably, a plurality of temperature equalizing members are provided on the inner wall of the evaporation tube along the fluid flow direction, and the distribution density of the temperature equalizing members is decreased along the fluid flow direction. Because the mixing degree of the fluid is better and better along with the continuous movement of the fluid, the distribution density is required to be smaller and smaller so as to reduce the flow resistance, and the temperature equalizing effect achieves the basically same effect on the aspects of reduced resistance and material cost saving.
Preferably, the distribution density of the temperature equalizing part is increased along the flowing direction of the fluid in a smaller and smaller range. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of fluid motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
Preferably, a plurality of temperature equalizing members are provided on an inner wall of the evaporation tube along the fluid flow direction, and the size of the temperature equalizing members becomes smaller along the fluid flow direction. Because the fluid is mixed better and better along with the continuous movement of the fluid, the size is required to be smaller and smaller so as to reduce the flow resistance, and the temperature equalizing effect achieves the same effect on the aspects of reduced resistance and material cost saving.
Preferably, a plurality of temperature equalizing members are provided on the inner wall of the evaporation tube along the fluid flow direction, and the size of the temperature equalizing members is gradually reduced along the fluid flow direction. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of fluid motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
Preferably, the evaporation tubes are arranged horizontally.
Through a large amount of numerical simulation and experimental study discovery, the angle and the size of samming part have very big influence to heat transfer and misce bene, samming part and inner wall contained angle are littleer, can lead to the mixed effect variation, and lead to samming part size too big, influence the flow resistance, the contained angle is big partially, it is good to lead to stirring the fluid effect, the resistance grow, the mixed effect variation, the interval of samming part is too big, can lead to the vortex effect not good, the interval undersize can lead to increasing the movement resistance, consequently, this application has obtained nearest samming part structure size optimization relation through a large amount of data simulation and experiments.
Preferably, the length L2 of the first straight wall and the length L1 of the second straight wall, the acute angle between the first line and the inner wall is a2, the acute angle between the second line and the inner part is a1, the distance S between the adjacent temperature equalization parts along the fluid flow direction (for example, the distance between the two adjacent temperature equalization plates on the left side of fig. 3 is S), namely the distance between the center points of the adjacent temperature equalization parts on the inner wall, and the center point is the midpoint of the connecting line of the connecting points of the first straight wall, the second straight wall and the inner wall, and the following requirements are met:
n-a-b ln (M), wherein N ═ L1+ L2)/S, M ═ sin (a2)/sin (a 1); ln is a function of the logarithm of the number,
0.3125<a<0.3130，0.1268<b<0.1272；
preferably, 0.25< M <0.75,0.34< N <0.44,45< a1<75 °, 15< a2<65 °,350< S <500mm, 70< L2<130mm, 30< L1<90 mm.
The optimal design requirements of the structure of the temperature equalizing part can be met by the above types. The structural optimization formula is a main improvement point of the invention, is the most optimized formula which is researched by a large number of numerical simulations and experiments, and is not common knowledge in the field.
More preferably, a is 0.3128 and b is 0.1270.
Preferably, in the case that the angle formed by the evaporation tube and the horizontal plane is A, the correction coefficient c can be increased to correct the data, that is, the data can be corrected
c*N＝a-b*Ln(M)；c＝cos(A)mWherein 0.095<m<0.108, preferably m is 0.11.
0°<A<50°。
In data simulation and experiments, the fact that the distance between the temperature equalizing parts is larger than a certain distance is found, otherwise, the fluid is guided to the opposite direction through the previous temperature equalizing part, if the distance between the temperature equalizing parts is too small, the fluid can flow in the opposite direction, the whole pipeline is not fully filled, the temperature equalizing part is arranged at the moment, the mixing effect cannot be achieved, the temperature equalizing part only plays the role of a baffle plate, the mixing guiding effect is not achieved, and only the flow resistance can be increased. Therefore, the design scheme of the minimum distance of the temperature equalizing part is provided through a large amount of research, and the design of the temperature equalizing part has certain guiding significance.
The intersection point 43 is a vertical point on the inner wall, a line formed by the intersection point and the vertical point is a third line, the distance between the connecting point of the first straight line wall and the inner wall and the vertical point is H, the inner pipe diameter of the evaporation pipe is R, and the distance S is designed in the following way:
S1>＝a*H+b*((H)2+R2)(1/2)；
wherein 2.5<a<3.5,
1.552<c<1.560，
Preferably, a is 3.2, c is 1.557;
according to the invention, through a large number of experiments and numerical simulation, the minimum design distance of the temperature equalizing part is obtained, the resistance is reduced through the design distance, and meanwhile, the full mixing can be realized.
Preferably, in the case that the angle formed by the evaporation tube and the horizontal plane is A, the data can be corrected by increasing the correction coefficient d, that is, the data can be corrected by
S/d>＝a*H+b*((H)2+R2)(1/2)；d＝cos(A)nWherein 0.085<n<0.98, preferably n-0.092.
Preferably 0 ° < a <50 °.
Preferably, the flow area of the evaporation portion is continuously increased along the direction in which the fluid flows. The main reasons are as follows: 1) the flow resistance can be reduced by increasing the flow area of the evaporation part, so that the vapor evaporated in the evaporation part continuously moves towards the direction of increasing the flow area, and the circulating flow of the heat pipe is further promoted. 2) Because the liquid is continuously evaporated in the evaporation part along with the continuous flowing of the fluid, the volume of the steam is larger and larger, and the pressure is also larger and larger, the continuously increased volume and pressure change of the steam is met by increasing the flow area, and the pressure distribution is uniform on the whole. 3) By increasing the flow area of the evaporation portion, the impact phenomenon caused by the increase in the volume of the vapor outlet can be reduced.
Preferably, the flow area of the evaporation portion is continuously increased in a direction along which the fluid flows to have a larger and larger extent. The amplitude change of the flow area is a result obtained by a large number of experiments and numerical simulation by the applicant, and through the arrangement, the circulating flow of the loop heat pipe can be further promoted, the pressure is integrally uniform, and the impact phenomenon is reduced.
Preferably, the flow area of the condensation section decreases continuously along the direction of fluid flow. The main reasons are as follows: 1) because steam is continuously condensed in the downcomer along with the continuous flowing of the fluid, the volume of the fluid is smaller and smaller, and the pressure is also smaller and smaller, so that the continuously increased volume and pressure changes of the fluid are met by reducing the flow area, the pressure distribution is uniform on the whole, and the heat exchange is uniform. 2) Through the reduction of the flow area of the condensation pipe, materials can be saved, and the cost is reduced.
Preferably, the flow area of the condensation section decreases more and more in the direction of fluid flow. The amplitude change of the flow area is a result obtained by a large number of experiments and numerical simulation by the applicant, and through the arrangement, the circulating flow of the loop heat pipe can be further promoted, so that the pressure is uniform as a whole.
Preferably, the heat source of the evaporation unit may be soil, boiler exhaust gas, or the like.
Preferably, the cold source of the condensation part is water or air.
Preferably, the heat absorbing end is provided with a plurality of heat absorbing ends, and a communication pipe 6 is arranged between at least two adjacent heat absorbing ends. In the research, it is found that in the process of absorbing heat in the evaporation part, different heat absorption amounts of the heat absorption ends at different positions can occur, so that the pressure or the temperature between the heat absorption ends is different, thus causing over-high heating of part of the heat absorption ends and shortening the service life, and once one heat absorption end has a problem, the problem that the whole heat pipe cannot be used can be caused. According to the invention, through a great deal of research, the communication pipes are arranged at the adjacent heat absorption ends, so that under the condition that the vertical pipes are heated differently to cause different pressures, the fluid in the vertical pipe with high pressure can rapidly flow to the heat absorption end with low pressure, thereby keeping the overall pressure balance and avoiding local overheating or overcooling.
Preferably, the evaporation portion has a plurality of communication pipes provided between adjacent heat absorbing ends from upstream to downstream of the heat absorbing ends. Through setting up a plurality of intercommunicating duct, can make the continuous balanced pressure of fluid in the heat absorption evaporation process, guarantee the pressure balance in the whole vertical pipe.
Preferably, in the evaporation portion, the distance between adjacent ones of the communication pipes decreases from upstream of the heat absorption end toward downstream of the heat absorption end. The purpose is to arrange more communication pipes, because the fluid is continuously heated along with the upward flow of the fluid, and the heating in different heat collecting pipes is more and more uneven along with the continuous heating of the fluid, so that the pressure balance can be ensured to be achieved as soon as possible in the flowing process of the fluid through the arrangement.
Preferably, in the evaporation portion, the distance between adjacent ones of the communication pipes decreases in a larger and larger manner from upstream of the heat absorption end toward downstream of the heat absorption end. Experiments show that the arrangement can ensure that the pressure balance is achieved more optimally and more quickly in the fluid flowing process. This is also the best way of communicating by extensively studying the law of change of the pressure distribution.
Preferably, in the evaporation portion, the flow area of the communication pipe increases from the upstream side of the heat absorption end to the downstream side of the heat absorption end. The purpose is to ensure a larger communication area, because the fluid is continuously heated along with the upward flow of the fluid, and the heating in different heat absorption ends is more and more uneven along with the continuous heating of the fluid, so that the pressure balance can be ensured to be achieved as soon as possible in the fluid flowing process through the arrangement.
Preferably, in the evaporation portion, the flow area of the communication pipe increases more and more from the upstream side of the heat absorption end to the downstream side of the heat absorption end. Experiments show that the arrangement can ensure that the pressure balance is achieved more optimally and more quickly in the fluid flowing process. This is also the best way of communicating by extensively studying the law of change of the pressure distribution.
Preferably, the heat radiating end is provided in plurality, and a communication pipe is provided between at least two adjacent heat radiating ends. Through setting up the through-connection pipe, can avoid being heated unevenly between the heat pipe, realize the pressure balance between the heat release end of heat pipe, avoid the defect that the inhomogeneous leads to of being heated between the different heat pipes.
At the heat release end, the distance between adjacent communication pipes increases from the upstream to the downstream of the heat release end. The purpose is to provide fewer through pipes and reduce the cost. Because the lower part of the heat release end is upward, the steam in the heat pipe continuously releases heat and condenses, and the pressure in the heat pipe is smaller and smaller along with the continuous heat release of the fluid, the phenomenon of non-uniformity is more and more alleviated, therefore, by the arrangement, the material can be saved, the communicating pipe is arranged according to the pressure change, and the pressure balance can be achieved as soon as possible in the flowing process of the fluid.
Preferably, the distance between adjacent communication pipes increases more and more in the heat radiating end in the upstream-downstream direction from the heat radiating end. Experiments show that the arrangement can ensure that the pressure balance is achieved more optimally and more quickly in the fluid flowing process. This is also the best way of communicating by extensively studying the law of change of the pressure distribution.
Preferably, at the heat radiating end, a lower portion of the heat radiating end is located in an upward direction, and a flow area of the communication pipe is decreased. The purpose is to ensure reduced communication area and reduce cost. The same principle as the distance from the front is increasing.
Preferably, the flow area of the communication pipe decreases more and more from the upstream side to the downstream side of the heat radiating end at the heat radiating end. Experiments show that the arrangement can ensure that the pressure balance is achieved more optimally and more quickly in the fluid flowing process. This is also the best way of communicating by extensively studying the law of change of the pressure distribution.
Preferably, a plurality of temperature equalizing members are arranged on the inner wall of the evaporation tube along the flow direction of the steam, and the included angle of A2 is smaller along the flow direction of the steam. Because the mixing degree of the fluid is better and better along with the continuous movement of the fluid, the included angle needs to be set to be smaller and smaller so as to reduce the flow resistance, and the temperature equalizing effect achieves the basically same effect on the aspects of reducing the resistance and saving the material cost.
Preferably, the included angle a2 increases with decreasing magnitude along the direction of flow of the steam. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of fluid motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
Preferably, a plurality of temperature equalizing members are provided on the inner wall of the evaporation tube along the flow direction of the steam, and the total arc of the arc connecting the temperature equalizing members and the inner wall of the same layer along the flow direction of the steam is gradually reduced. Because the mixing degree of the fluid is better and better along with the continuous movement of the fluid, the flow space which needs to be arranged is larger and larger so as to reduce the flow resistance, and the temperature equalizing effect achieves basically the same effect on the aspects of reducing the resistance and saving the material cost.
Preferably, the total radian of the arcs connecting the temperature equalizing parts and the inner wall of the same layer with each other is gradually reduced along the flowing direction of the steam. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of fluid motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
Preferably, a plurality of temperature equalizing members are arranged on the inner wall of the evaporation tube along the flow direction of the steam, and the included angle of A1 is increased along the flow direction of the steam. Because the mixing degree of the fluid is better and better along with the continuous movement of the fluid, the included angle needs to be set to be larger and larger so as to reduce the size, the flow resistance is reduced, and the temperature equalizing effect achieves the basically same effect on the aspects of reducing the resistance and saving the material cost.
Preferably, the included angle a1 increases with increasing magnitude in the direction of flow of the steam. The effect is obtained through a large number of numerical simulation and experimental research results, and the research finds that the rule accords with the rule of fluid motion, and the temperature equalizing effect achieves the basically same effect on the aspects of further reduction of resistance and saving of material cost.
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 (4)
1. A loop heat pipe comprises an evaporation part, a condensation part and an evaporation pipe, wherein liquid absorbs heat and evaporates in the evaporation part, enters the condensation part through the evaporation pipe to release heat, and then returns to the evaporation part through gravity; the temperature equalizing device is characterized in that a temperature equalizing part extending from the inner wall of the evaporation tube to the center of the evaporation tube is arranged in the evaporation tube, the temperature equalizing part comprises a first straight line wall and a second straight line wall extending from the inner wall, wherein an acute angle formed by the first straight line wall and the inner wall is smaller than an acute angle formed by the second straight line wall and the inner wall, the first straight line wall and the second straight line wall extend towards the flowing direction of fluid, the intersection point of the first straight line wall and the second straight line wall is positioned at the upper part of the connection part of the first straight line wall and the inner wall and is also positioned at the upper part of the connection part of the second straight line wall and the inner wall, and the temperature equalizing part is in a shape formed by the first straight line wall, the second straight line wall and the inner wall rotating along the axis of the evaporation tube; the steam-water heater is characterized in that a plurality of layers of temperature-equalizing parts are arranged on the inner wall of the evaporation pipe along the flowing direction of steam, and the total radian of the circular arcs connecting the temperature-equalizing parts on the same layer with the inner wall is smaller and smaller along the flowing direction of the steam.
2. A loop heat pipe according to claim 1, wherein the total curvature of the arc connecting the temperature equalizing part and the inner wall of the same layer increases in a decreasing range along the flow direction of the vapor.
3. The loop heat pipe of claim 1, wherein the condensing portion has a plurality of heat releasing ends.
4. The loop heat pipe of claim 3, wherein the heat sinks of the at least two heat releasing ends are independent of each other.
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| CN202110022558.XA CN112833692B (en) | 2021-01-08 | 2021-01-08 | Radian-variable straight-plate uniform-temperature loop heat pipe |
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| CN202110022558.XA CN112833692B (en) | 2021-01-08 | 2021-01-08 | Radian-variable straight-plate uniform-temperature loop heat pipe |
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| CN112833692B true CN112833692B (en) | 2022-05-24 |
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Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1003013A (en) * | 1962-05-28 | 1965-09-02 | Patterson Kelley Co | Heat exchange device |
| JP2003302180A (en) * | 2002-04-11 | 2003-10-24 | Furukawa Electric Co Ltd:The | Self-excited oscillation type heat pipe |
| CN101270961A (en) * | 2008-05-15 | 2008-09-24 | 中山大学 | Loop circuit heat pipe condenser |
| CN201255596Y (en) * | 2008-08-11 | 2009-06-10 | 丹腾空气系统(苏州)有限公司 | Isolation type hot pipe heat exchanger |
| JP2009243864A (en) * | 2008-03-31 | 2009-10-22 | Kobelco & Materials Copper Tube Inc | Inner surface grooved pipe for heat pipe, and heat pipe |
| CN104279770A (en) * | 2014-10-11 | 2015-01-14 | 南京工业大学 | Solar medium-high temperature loop heat pipe steam generator |
| CN105277028A (en) * | 2015-11-16 | 2016-01-27 | 中国电子科技集团公司第十研究所 | Thermal control loop heat pipe of integrated structure |
| CN105692748A (en) * | 2016-02-27 | 2016-06-22 | 山东大学（威海） | Auxiliary heating solar energy system and seawater desalination system |
| CN107062960A (en) * | 2017-04-28 | 2017-08-18 | 山东大学 | A kind of loop circuit heat pipe of annular and separation device short transverse change |
| CN109297329A (en) * | 2018-09-03 | 2019-02-01 | 北京空间机电研究所 | A kind of axial-grooved heat pipe and attaching method thereof with circumferential channel |
| CN109387104A (en) * | 2017-08-03 | 2019-02-26 | 山东大学 | A kind of loop circuit heat pipe |
| CN111238274A (en) * | 2017-08-03 | 2020-06-05 | 山东大学 | Size-variable rod-fin loop heat pipe |
-
2021
- 2021-01-08 CN CN202110022558.XA patent/CN112833692B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1003013A (en) * | 1962-05-28 | 1965-09-02 | Patterson Kelley Co | Heat exchange device |
| JP2003302180A (en) * | 2002-04-11 | 2003-10-24 | Furukawa Electric Co Ltd:The | Self-excited oscillation type heat pipe |
| JP2009243864A (en) * | 2008-03-31 | 2009-10-22 | Kobelco & Materials Copper Tube Inc | Inner surface grooved pipe for heat pipe, and heat pipe |
| CN101270961A (en) * | 2008-05-15 | 2008-09-24 | 中山大学 | Loop circuit heat pipe condenser |
| CN201255596Y (en) * | 2008-08-11 | 2009-06-10 | 丹腾空气系统(苏州)有限公司 | Isolation type hot pipe heat exchanger |
| CN104279770A (en) * | 2014-10-11 | 2015-01-14 | 南京工业大学 | Solar medium-high temperature loop heat pipe steam generator |
| CN105277028A (en) * | 2015-11-16 | 2016-01-27 | 中国电子科技集团公司第十研究所 | Thermal control loop heat pipe of integrated structure |
| CN105692748A (en) * | 2016-02-27 | 2016-06-22 | 山东大学（威海） | Auxiliary heating solar energy system and seawater desalination system |
| CN107062960A (en) * | 2017-04-28 | 2017-08-18 | 山东大学 | A kind of loop circuit heat pipe of annular and separation device short transverse change |
| CN109387104A (en) * | 2017-08-03 | 2019-02-26 | 山东大学 | A kind of loop circuit heat pipe |
| CN111238274A (en) * | 2017-08-03 | 2020-06-05 | 山东大学 | Size-variable rod-fin loop heat pipe |
| CN109297329A (en) * | 2018-09-03 | 2019-02-01 | 北京空间机电研究所 | A kind of axial-grooved heat pipe and attaching method thereof with circumferential channel |
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|---|---|
| CN112833692A (en) | 2021-05-25 |
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