CN114370778B

CN114370778B - Multi-arc-shaped wall velocity field drainage gravity heat pipe

Info

Publication number: CN114370778B
Application number: CN202111280152.8A
Authority: CN
Inventors: 赵小龙; 温竞龙; 遇鹤儒
Original assignee: North University of China
Current assignee: North University of China
Priority date: 2020-11-05
Filing date: 2021-11-01
Publication date: 2023-03-21
Anticipated expiration: 2041-11-01
Also published as: CN114370778A

Abstract

The invention provides a multi-arc-wall velocity field drainage gravity heat pipe which comprises an evaporation part, a condensation part and a heat insulation part, wherein liquid absorbs heat and evaporates in the evaporation part, enters the condensation part through the heat insulation part to release heat, and then returns to the evaporation part through gravity; the shape of the temperature equalization plate is formed by rotating the first arc-shaped wall, the second arc-shaped wall and the inner wall along the axis of the heat insulation part. The invention provides a gravity heat pipe with a novel structure, wherein a temperature equalizing plate is arranged in a heat insulation part, so that a part of fluid flows along the temperature equalizing plate and is guided to the opposite direction, and the fluid entering the opposite direction is fully mixed with the fluid entering 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.

Description

Multi-arc-shaped wall velocity field drainage gravity heat pipe

Technical Field

The invention relates to a gravity assisted heat pipe, in particular to a gravity assisted heat pipe provided with a temperature equalizing part.

Background

The heat pipe technology is a heat transfer element called a heat pipe invented by George Grover Luo Fo of national laboratory of Los Alamos (Los 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 out 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, people change the design idea of the traditional radiator, get rid of the single heat dissipation mode of obtaining better heat dissipation effect by only depending on a high-air-volume motor, adopt the heat pipe technology to ensure that the radiator obtains satisfactory heat exchange effect, and open up a new place in the heat dissipation industry. 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. On one hand, the fluid in the heat insulation part is generally a vapor-liquid two-phase flow taking vapor as a main part in the upward process, so that the fluid in the heat insulation part is a vapor-liquid mixture, and the heat absorption efficiency of the heat insulation part is influenced due to the existence of the vapor-liquid two-phase flow.

In the research, it is found that the temperature of the fluid at different positions of the heat insulation part is not uniform no matter what the heat absorption end absorbs heat or the heat insulation part keeps the heat, for example, the position with good heat insulation effect has high temperature and the position with poor heat insulation effect has low temperature, the temperature of the fluid at different positions in the heat insulation part is different, the temperature in the heat insulation part is not uniform due to the temperature difference, so that the heat dissipation of the condensation section at different positions is also different after entering the heat release end, especially when a plurality of heat release ends and corresponding heat utilization parts are involved, the heat utilization parts caused by the different heat release ends absorb heat unevenly, thereby causing the overheating or overcooling of the heat utilization parts and affecting the operation. 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.

Aiming at the problems, the invention is improved on the basis of the previous invention, and provides a novel gravity heat pipe, thereby solving the problem of uneven temperature of fluid in the heat pipe.

Disclosure of Invention

The present invention provides a new gravity assisted heat pipe to solve the foregoing problems.

In order to achieve the purpose, the technical scheme of the invention is as follows:

a gravity heat pipe with a multi-arc-shaped wall velocity field for drainage comprises an evaporation part, a condensation part and a heat insulation part, wherein liquid absorbs heat and evaporates in the evaporation part, enters the condensation part through the heat insulation part to release heat, and then returns to the evaporation part through gravity; set up the temperature-uniforming plate that extends from adiabatic portion inner wall to adiabatic portion center in the adiabatic portion, the temperature-uniforming plate includes first arc wall and the second arc wall that extends from the inner wall, wherein the acute angle that first arc wall and inner wall junction tangent line and inner wall formed is less than the acute angle that second arc wall and inner wall junction tangent line and inner wall formed, first arc wall and second arc wall extend towards the fluid flow direction is crooked, crooked direction also is towards the fluid flow direction, the crossing point of first arc wall and second arc wall is located the upper portion of first arc wall and inner wall junction, be located the upper portion of second arc wall and inner wall junction simultaneously, the shape of temperature-uniforming plate is the rotatory shape that forms of first arc wall and second arc wall and inner wall along adiabatic portion axis.

Preferably, the inner wall of the heat insulation part is provided with a duct.

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.

Preferably, the first and second arcuate walls are arcs, wherein the arc diameter of the first arcuate wall is less than the arc diameter of the second arcuate wall.

Preferably, the tangent to the first curved wall at the location of the point of intersection forms an angle of 30-60 ° with the axis of the insulating portion.

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

1) The invention provides a novel gravity heat pipe, wherein a bent temperature-equalizing plate is arranged in a heat insulation part, so that a part of fluid flows along the temperature-equalizing plate and is guided to the opposite direction, and the fluid entering the heat-equalizing plate in the opposite direction are fully mixed, so that the temperature of the fluid is uniform, the further temperature uniformity is realized, and the service life of a product is prolonged.

2) 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 plate, the temperature equalizing plate structure 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.

3) According to the invention, through reasonable layout, the temperature equalizing plates of adjacent rows are arranged in a staggered manner, so that fluid is further fully mixed, and the temperature is uniform.

4) 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 plate along the flowing direction of the fluid.

5) According to the invention, the distance of the temperature-equalizing plate is widely researched, a formula of the minimum distance is designed, the temperature-equalizing mixing requirement is 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 view of the gravity assisted heat pipe of the present invention.

FIG. 2 is a schematic view of the heat releasing end of the gravity assisted heat pipe structure of the present invention.

FIG. 3 is an axial sectional view of the vapor chamber provided in the heat insulating part of the present invention.

Fig. 4 is a schematic size diagram of the thermal insulation part temperature equalization plate according to the present invention.

Fig. 5 is a schematic perspective view of 1 vapor chamber per layer.

Fig. 6 is a schematic perspective view of 3 vapor chambers arranged in each layer.

Fig. 7 is a schematic perspective view of 1 vapor chamber per layer.

Fig. 8 is an exploded perspective view of the heat insulation part side of fig. 7.

FIG. 9 is a schematic view of the heat absorption end of the gravity assisted heat pipe structure of the present invention.

FIG. 10 is a schematic view of the heat sink end of the present invention with the feedthrough.

FIG. 11 is a schematic view of the heat-releasing end of the present invention with a through-connection tube.

In the figure: 1. the heat-insulation water heater comprises an evaporation part, a condensation part, a heat insulation part, a temperature-equalizing plate, a first arc-shaped wall 41, a second arc-shaped wall 42, a 43 intersection point, a heat absorption end 11, a heat release end 21, a communication pipe 6 and a communication pipe 7.

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 gravity assisted heat pipe includes an evaporation portion 1, a condensation portion 2, and a heat insulation portion 3, wherein a liquid absorbs heat and evaporates in the evaporation portion 1, enters the condensation portion 2 through the heat insulation portion 3 to release heat, and then returns to the evaporation portion 1 through gravity and/or capillary force.

Of course the heat pipe may not be limited to a gravity heat pipe, but may be a Mao Xili heat pipe that passes entirely through capillary suction.

Preferably, a heat insulating layer is provided outside the heat insulating part 3.

Preferably, the capillary structure is arranged on the inner wall of the heat pipe, preferably the inner wall of the heat insulation part. 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.

Preferably, the heat sink of at least two heat release ends is 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 heat insulation portion 3 has a circular structure.

As a modification, as shown in fig. 3, a temperature-equalizing plate 4 extending from an inner wall 51 of the heat-insulating portion to the center of the heat-insulating portion is disposed in the heat-insulating portion 3, and the temperature-equalizing plate 4 includes a first arc-shaped wall 41 and a second arc-shaped wall 42 extending from the inner wall, wherein an acute angle formed by a tangent line at a junction of the first arc-shaped wall 41 and the inner wall 51 and the inner wall is smaller than an acute angle formed by a tangent line at a junction of the second arc-shaped wall 42 and the inner wall, the first arc-shaped wall 41 and the second arc-shaped wall 42 extend in a curved manner toward a fluid flow direction, the curved direction is also toward the fluid flow direction, and an intersection point 43 of the first arc-shaped wall 41 and the second arc-shaped wall 42 is located at an upper portion of the junction of the first arc-shaped wall 41 and the inner wall 51 and is located at an upper portion of the junction of the second arc-shaped wall 42 and the inner wall. The shape of the temperature equalization plate 4 is a shape formed by rotating the first arc-shaped wall 41 and the second arc-shaped wall 42 and the inner wall along the axis of the heat insulation portion.

In the research, it is found that the temperature of the fluid at different positions of the heat insulation part is not uniform no matter what the heat absorption end absorbs heat or the heat insulation part keeps the heat, for example, the position 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 heat insulation part is different, the temperature in the heat insulation part is different due to different temperatures, so that the heat dissipation of the condensation section at different positions is different after entering the heat release end, especially when a plurality of heat release ends and corresponding heat utilization parts are involved, the heat absorption of the heat utilization parts is not uniform due to different heat release ends, and under the condition of a plurality of heat absorption ends, the temperature of the fluid at different positions of the heat pipe condensation part is different due to different heat sources at the heat absorption end, so that the heat utilization parts are overheated or overcooled, which affects the operation.

According to the invention, the temperature equalizing plate is arranged in the heat insulation part, so that a part of fluid flows along the temperature equalizing plate and is guided to the opposite direction, and the fluid is fully mixed with the fluid entering in the opposite direction, thereby realizing uniform temperature of the fluid, uniform temperature of the fluid in the condensation part, uniform heat exchange, further heat exchange requirement, and prolonged service life of the product.

The temperature-equalizing plate is provided with the first arc-shaped wall and the second arc-shaped wall respectively, so that the fluid disturbance effect is better, the area of the temperature-equalizing plate contacting the inner wall is increased, and the stability is improved. And through setting up the second arc wall for fluid that the opposite direction water conservancy diversion came over also can be along the crooked direction motion of second arc wall direction, increases the buffering, reduces flow resistance.

Preferably, the inner wall of the heat pipe, especially the inner wall of the heat insulation part, is provided with a duct. The pore channel is arranged to promote the liquid to enter the evaporation part as soon as possible. So that the fluid after condensation enters the vicinity of the inner wall along the second arc-shaped wall and rapidly enters the evaporation part through the pore passage of the inner wall.

Preferably, the first and second

arcuate walls

41, 42 are arcs, wherein the diameter of the arc of the first arcuate wall 41 is smaller than the diameter of the arc of the second arcuate wall 42.

The first wall and the second wall are arc-shaped, so that the fluid flow resistance is smaller, and the fluid flows to the opposite side easily to be mixed.

Preferably, the tangent to the first curved wall 41 at the location of the intersection point 43 forms an angle of 30-60 deg. with the axis of the insulating portion, preferably 45 deg.. By providing this angle, the fluid can be quickly directed to the opposite upper position, and the flow resistance can be further reduced.

Preferably, as shown in fig. 3, a plurality of temperature-equalizing plates 4 are provided on the inner wall of the heat-insulating part along the height direction, and the temperature-equalizing plates of adjacent layers are staggered. Through the staggered distribution of the temperature equalizing plates in the adjacent rows, the fluids can fully move to opposite positions mutually in the heat insulation part, and the full and uniform mixing is ensured. Fig. 3 shows that one vapor chamber is provided for each layer. Of course, more than one plate, for example, 3 plates, may be provided for each layer.

Preferably, the distance between the intersection point and the inner wall of the heat insulating portion is 0.3 to 0.5 times, preferably 0.4 times, the diameter of the heat insulating portion. With this arrangement, the air has less flow resistance on thorough mixing.

Preferably, the length of the first arching wall is greater than the length of the second arching wall.

Preferably, the total radian of the circular arc connecting the inner wall and the temperature-equalizing plate on the same layer is 150-180 degrees. This parameter set ensures thorough mixing while meeting the resistance requirements. For example, figures 3, 5, and 7 show one for each temperature distribution plate, with a total arc of 150-180. Of course, multiple blocks may be provided per layer of vapor chamber, for example, the total arc of three blocks per layer in FIG. 5 is 150-180.

Preferably, the temperature-equalizing plates on the layer A are arranged in a plurality, intervals are arranged among the temperature-equalizing plates on the layer A, the temperature-equalizing plates on the layer A are arranged at equal intervals, the layer B is an adjacent layer of the layer A, and the temperature-equalizing plates on the layer B are arranged at the intervals of the layer A when viewed from the flowing direction. Through the complementation of the positions of the temperature equalizing plates of the adjacent layers, the fluids can fully move to the opposite positions mutually in the heat insulation part, and the full and uniform mixing is ensured. Note that, here, the layer a and the layer B are not specifically specified as that layer, and A, B is only used as a distinction and is used as an adjacent layer.

Preferably, a plurality of temperature equalization plates are provided on the inner wall of the heat insulation section along the height direction, and the distribution density of the temperature equalization plates becomes smaller along the height direction. Because the fluid is mixed better and better along with the continuous movement of the fluid, the distribution density is required 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 reduced resistance and material cost saving.

Preferably, the distribution density of the temperature equalization plates is increased in a smaller and smaller range along the height 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, a plurality of temperature equalization plates are provided on the inner wall of the heat insulating section in the height direction, and the size of the temperature equalization plates becomes smaller in the height 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 equalization plates are provided on the inner wall of the heat insulating section in the height direction, and the size of the temperature equalization plate is gradually reduced in the height direction. The effect is obtained through a large number of numerical simulation and experimental research results, the research finds that the rule accords with the rule of fluid motion, and the temperature equalizing effect achieves basically the same effect on the aspects of further reduction of resistance and material cost saving.

Through a large amount of numerical simulation and experimental study discovery, the angle and the size of temperature-uniforming plate have very big influence to heat transfer and misce bene, temperature-uniforming plate and inner wall contained angle are on the small side, can lead to the mixed effect variation, and lead to the temperature-uniforming plate oversize, influence the flow resistance, the contained angle is on the large side, lead to stirring the fluid effect not good, the resistance grow, the mixed effect variation, the interval of temperature-uniforming plate is too big, can lead to the vortex effect not good, interval undersize can lead to increasing the movement resistance, consequently, this application has obtained nearest temperature-uniforming plate structure size optimization relation through a large amount of data simulation and experiments.

Preferably, the length L2 of the first line between the connection point of the first arc-shaped wall and the inner wall and the intersection point 43, the length L1 of the second line between the connection point of the second arc-shaped wall and the inner wall and the intersection point 43, the acute angle between the first line and the inner wall is A2, the acute angle between the second line and the inner wall is A1, the distance S between the adjacent temperature equalization plates in the flowing direction of the fluid, namely the distance between the central points of the adjacent temperature equalization plates on the inner wall, and the central point is the central point of the connection line between the connection points of the first arc-shaped wall, the second arc-shaped wall and the inner wall, satisfy the following requirements:

n = a-b × Ln (M), where N = (L1 + L2)/S, M = sin (A2)/sin (A1); ln is a function of the logarithm of the number,

0.2697<a<0.2699，0.0830<b<0.0832；

preferably, 0.25-Ap-M-Ap-0.75, 0.29-Ap-N-Ap-0.36, 45-Ap-1-Ap-75, 15-Ap-2-Ap-45, 400-Ap-S-Ap-550mm, 70-Ap-L2-Ap-130mm and 30-Ap-L1-Ap-90mm.

The optimal design requirements of the structure of the temperature equalization plate can be met by the above formulas. 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.

Further preferably, a =0.2698, b =0.0831.

Preferably, when the angle formed by the adiabatic part and the horizontal plane is A, the data can be corrected by increasing the correction coefficient c, that is, by increasing the correction coefficient c

c* N=a-b*Ln(M)；c=1/sin(A) ^m Wherein 0.09<m<0.11, preferably m =0.10.

50°<A<90°。

In data simulation and experiments, the fact that the distance between the temperature equalizing plates must be larger than a certain distance, otherwise, fluid can be guided to the opposite direction through the previous temperature equalizing plate, if the distance between the temperature equalizing plates is too small, the fluid can flow in the opposite direction, the whole pipeline is not fully filled, the temperature equalizing plates are arranged at the moment, the mixing effect cannot be achieved, the temperature equalizing plates only play a role of a baffle plate, the mixing is not guided, and only the flow resistance can be increased. Therefore, the design scheme of the minimum distance of the temperature-equalizing plate is provided through a large amount of research, and the design of the temperature-equalizing plate has certain guiding significance.

The perpendicular point of intersection point 43 on the inner wall, the line that intersection point and perpendicular point formed is the third line, the distance of the connecting point of first arc wall and inner wall and perpendicular point is H, the acute angle that first line and third line formed is A3, the acute angle that tangent line of first arc wall and the axis of heat-insulating portion at the position of intersection point formed is A4, the interior pipe diameter of heat-insulating portion is R, distance S adopts following mode design:

(S/H)>a+b*Ln (T)，(S/R) ² >c+d*Ln (T)；

wherein T = sin (A3)/sin (A4), 2.66 yarn-woven a yarn-woven 2.68,17.1 yarn-woven 17.2,1.976 yarn-woven c yarn-woven 1.978,3.425 yarn-woven d yarn-woven 3.426,

30-straw (A3) woven fabric (70 degree), 20-straw (A4) woven fabric (60 degree); preferably 1.07 t-woven fabrics of 1.30;

preferably, a =2.67, b =17.15, c =1.977, d =3.4255;

according to the invention, through a large number of experiments and numerical simulation, the minimum design distance of the temperature-uniforming plate is obtained, and the resistance is reduced through the design distance, and meanwhile, the full mixing can be realized.

Preferably, when the angle formed by the adiabatic part and the horizontal plane is a, the data can be corrected by increasing the correction coefficients d and f, that is, by increasing the correction coefficients d and f

( (S/H)/d)>a+b*Ln (T)； ((S/R) ² /f)>c+d*Ln (T)；

d=sin(A) ⁿ Wherein 0.085<n<0.098, preferably n =0.092.f = sin (A) ^k Wherein 0.076<k<0.078, preferably k =0.077

50°<A<90°。

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 pipe diameter of the evaporation part, the impact phenomenon caused by the increase of the volume of the steam 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 part, 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 a plurality of, and the 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 large amount of research, the communication pipe is arranged at the adjacent heat absorption ends to realize the communication function, and under the condition that the vertical pipes are heated differently to cause different pressures, the fluid in the vertical pipe with large pressure can rapidly flow to the heat absorption end with small pressure, so that the overall pressure balance is maintained, and the local overheating or overcooling is avoided.

Preferably, a plurality of communication pipes are provided between adjacent heat absorbing ends from the lower portion of the heat absorbing end toward the upper portion of the heat absorbing end. Through setting up a plurality of intercommunicating duct, can make fluid at the continuous balanced pressure of heat absorption evaporation process, guarantee the pressure balance in the whole heat absorption portion.

Preferably, the distance between adjacent ones of the communication tubes decreases from the lower portion of the heat absorbing end to the upper portion of the heat absorbing 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, the distance between adjacent communication tubes decreases from the lower part of the heat absorbing end to the upper part of the heat absorbing 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 flow area of the through-pipe increases from the lower portion of the heat absorbing end to the upper portion of the heat absorbing 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 flowing process of the fluid through the arrangement.

Preferably, the flow area of the communication pipe increases from the lower portion of the heat absorption end to the upper portion of the heat absorption end to a larger extent. 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 plural, and the communication pipe 7 is provided between at least two adjacent heat radiating ends. Through the arrangement of the communication pipe, uneven heating between the heat release ends can be avoided, pressure balance between the heat release ends of the heat pipe is realized, and the defect caused by uneven heating between different heat release ends is avoided.

At the heat release end, the distance between adjacent communication pipes increases from the lower part of the heat release end to the upper part. The purpose is to provide fewer through-connecting 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, at the heat radiating end, the distance between the adjacent communication pipes increases from the lower portion to the upper portion of 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 directed upward, and the 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 width of the flow area of the communication pipe decreases gradually in the upper direction at the lower portion 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.

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

1. A gravity heat pipe with a multi-arc-shaped wall velocity field for drainage comprises an evaporation part, a condensation part and a heat insulation part, wherein liquid absorbs heat and evaporates in the evaporation part, enters the condensation part through the heat insulation part to release heat, and then returns to the evaporation part through gravity; its characterized in that sets up the samming board that extends from adiabatic portion inner wall to adiabatic portion center in the adiabatic portion, the samming board includes first arc wall and the second arc wall that extends from the inner wall, wherein the acute angle that first arc wall and inner wall junction tangent line and inner wall formed is less than the acute angle that second arc wall and inner wall junction tangent line and inner wall formed, and first arc wall and second arc wall extend towards the fluid flow direction is crooked, and crooked direction also faces the fluid flow direction, and the nodical point of first arc wall and second arc wall is located the upper portion of first arc wall and inner wall junction, is located the upper portion of second arc wall and inner wall junction simultaneously, and the shape of samming board is the rotatory shape that forms of first arc wall and second arc wall and inner wall along the adiabatic portion axis.

2. The gravity heat pipe of claim 1, wherein the insulating portion has a duct formed in an inner wall thereof.

3. The gravity heat pipe of claim 1, the condensing portion having a plurality of heat radiating ends.

4. The gravity heat pipe of claim 1, wherein the heat sinks of the at least two heat releasing ends are independent of each other.

5. A gravity heat pipe according to claim 1 wherein the first and second arcuate walls are arcs wherein the arc diameter of the first arcuate wall is less than the arc diameter of the second arcuate wall.

6. A gravity heat pipe according to claim 1 wherein a tangent to the first curved wall at the point of intersection forms an angle of between 30 ° and 60 ° with the axis of the insulating portion.