CN114440676B

CN114440676B - Multi-triangular-wall velocity field drainage gravity heat pipe

Info

Publication number: CN114440676B
Application number: CN202111280105.3A
Authority: CN
Inventors: 田二明; 马弢; 张权; 石宇; 丁仕杰; 李凯璇; 李扬
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: CN114440676A

Abstract

The invention provides a multi-triangular-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, 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 the fluid, and the intersection point of the first straight line wall and the second straight line wall is positioned at the upper part of the joint of the first straight line wall and the inner wall and is also positioned at the upper part of the joint of the second straight line wall and the inner wall. The shape of the temperature equalizing plate is formed by rotating the first and second linear walls and the inner wall along the axis of the heat insulation part. Through set up sharp temperature-uniforming plate in adiabatic portion for fluid partly flows along the temperature-uniforming plate and guides to opposite direction, with the fluid intensive mixing that opposite direction got into, thereby realizes that fluidic temperature is even, with the realization further temperature is even, improves product life.

Description

Multi-triangular-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, 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. On the one hand, the fluid in the heat insulation part is generally a vapor-liquid two-phase flow with the vapor as the main part in the upward process, so that the fluid in the heat insulation part is a vapor-liquid mixture, and the existence of the vapor-liquid two-phase flow affects the heat absorption efficiency of the heat insulation part.

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 multiple triangular wall velocity fields 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; the heat insulation part is internally provided with a temperature-equalizing plate extending from the inner wall of the heat insulation part to the center of the heat insulation part, the temperature-equalizing plate comprises a first linear wall and a second linear wall extending from the inner wall, wherein an acute angle formed by the first linear wall and the inner wall is smaller than an acute angle formed by the second linear wall and the inner wall, the first linear wall and the second linear wall extend towards the flowing direction of fluid, the intersection point of the first linear wall and the second linear wall is positioned on the upper part of the joint of the first linear wall and the inner wall, and is positioned on the upper part of the joint of the second linear wall and the inner wall, and the temperature-equalizing plate is in a shape formed by the first linear wall, the second linear wall and the inner wall rotating along the axis of the heat insulation part.

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 sources of the at least two heat radiating ends are independent of each other.

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

1) The invention provides a novel gravity heat pipe, wherein a linear 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 pipe in the opposite direction is fully mixed with the fluid entering the heat 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.

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 temperature equalization plate per layer.

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

Fig. 7 is a perspective view of 1 uniform temperature plate 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 pipe.

In the figure: 1. the heat-insulation water heater comprises an evaporation part, a condensation part, a heat insulation part, a heat-insulation part, a uniform temperature plate, a first straight wall 41, a second straight wall 42, a crossing point 43, 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, the 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. Used for heating the liquid medicine for fumigation and washing.

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 heat insulating part 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 provided in the heat-insulating portion 3, and the temperature-equalizing plate 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 straight wall 42 extend in the fluid flow direction, and an intersection 43 of the first straight wall 41 and the second straight wall 42 is located downstream of a junction of the first straight wall 41 and the inner wall 51 and downstream of a junction of the second straight wall 42 and the inner wall. The shape of the temperature equalization plate 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 heat insulation portion.

The invention provides a heat insulation part, which is provided with the temperature equalizing plate, so that a part of fluid flows along the temperature equalizing plate and is guided to the opposite direction, and the fluid entering from the opposite direction is fully mixed with the fluid, thereby realizing uniform temperature of the fluid, realizing the requirement of further heat exchange and prolonging the service life of a product. And through setting up the second straight line wall, the gradient of second straight line wall is little moreover for fluid that the opposite direction water conservancy diversion came over also can be along the rotatory motion of second straight line wall direction, increases the buffering, reduces flow resistance.

The temperature-equalizing plate is provided with the first linear wall and the second linear wall respectively, the two linear walls are arranged, 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.

Preferably, the first rectilinear 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, 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 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. For example, fig. 3, 5, and 7 show one for each layer of vapor chamber, the total arc of which is 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. 6 is 150-180.

Preferably, the distance between the intersection point and the inner wall of the heat insulating part is 0.3 to 0.5 times, preferably 0.4 times, the diameter of the heat insulating part. This arrangement provides less flow resistance to the air on a well-mixed basis.

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 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, fig. 2 shows one for each layer of vapor chamber, the total arc of which is 150-180 °. Of course, each layer of the vapor chamber can be provided with a plurality of blocks, for example, 3 blocks with a total arc of 150-180 deg.

Preferably, the temperature-equalizing plates on the layer A are arranged in a plurality of blocks, 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 insulating section in the height direction, and the distribution density of the temperature equalization plates becomes smaller in the height 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 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 mixing degree of the fluid is better and better along with the continuous movement of the fluid, the size is required to be smaller and smaller to reduce the flow resistance, and the temperature equalizing effect achieves the same effect in the aspects of reducing the resistance and saving the 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 plate is gradually reduced in 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.

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 linear wall, the length L1 of the second linear wall, 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 isothermal plate structures along the fluid flowing direction, that is, the distance between the central points of the adjacent isothermal plates on the inner wall, and the central point is the midpoint of the connecting line of the connecting points of the first linear wall, the second linear 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,

0.3218<a<0.3230，0.1284<b<0.1286；

preferably, 0.25-Ap-M-Ap-0.75, 0.34-Ap-N-Ap-0.44, 45-Ap-1-Ap-75, 15-Ap-2-Ap-65, 350-Ap-S-Ap-500mm, 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 =0.3219, b =0.1285.

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.

30°<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 the intersection point 43 on the inner wall, the line formed by the intersection point and the perpendicular point is a third line, the distance between the connecting point of the first straight line wall and the inner wall and the perpendicular point is H, the inner pipe diameter of the heat insulation part is R, and the distance S is designed in the following way:

S>=a*H+b*((H) ² +R ² ) ^(1/2) ；

therein 2.38<a<3.18,

，1.432<c<1.443，

Preferably, a =2.78, c =1.437;

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 may be corrected by increasing the correction coefficient d, that is, by increasing the correction coefficient d

S/d>=a*H+b*((H) ² +R ² ) ^(1/2) ；d=sin(A) ⁿ Wherein 0.093<n<0.105, preferably n =0.099.

Preferably 30 ° < 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 of the applicant, and through the arrangement, the circulating flow of the loop heat pipe can be further promoted, the pressure is uniform as a whole, 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 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 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 the arrangement of the plurality of the communication pipes, the pressure of the fluid can be continuously balanced in the heat absorption and evaporation process, and the pressure balance in the whole heat absorption part is ensured.

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 pipes decreases from the lower portion of the heat absorbing end to the upper portion of the heat absorbing end to a greater 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 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. 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 is equalized 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 setting up the UNICOM's pipe, can avoid between the end of sending out heat to be heated inhomogeneous, realize the pressure equilibrium between the end of sending out heat of heat pipe, avoid the defect that the inhomogeneous results in of being heated between the different end of sending out heat.

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 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 in connection with 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 multiple triangular wall velocity fields 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; the heat insulation structure is characterized in that a temperature-equalizing plate extending from the inner wall of the heat insulation part to the center of the heat insulation part is arranged in the heat insulation part, the temperature-equalizing plate comprises a first straight line wall and a second straight line wall extending from the inner wall, 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 located at the upper part of the connection part of the first straight line wall and the inner wall, and is located at the upper part of the connection part of the second straight line wall and the inner wall, and the shape of the temperature-equalizing plate is formed by the first straight line wall, the second straight line wall and the inner wall rotating along the axis of the heat insulation part.

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 emitting 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 linear walls are arcs, wherein the diameter of the arc of the first linear wall is less than the diameter of the arc of the second linear wall.

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