CN219418508U - High-power compact type separation type heat pipe - Google Patents

Abstract

The utility model discloses a high-power compact separation type heat pipe, which belongs to the technical field of nuclear power passive cooling and comprises an evaporator, a rising pipe, a condenser, a falling pipe and a gas-liquid cyclone separator, wherein an outlet of the evaporator is communicated with an inlet of the condenser through the rising pipe, an outlet of the condenser is communicated with an inlet of the gas-liquid cyclone separator, a gas outlet of the gas-liquid cyclone separator is communicated with the inlet of the condenser, and a liquid outlet of the gas-liquid cyclone separator is communicated with the inlet of the evaporator through the falling pipe. According to the utility model, the gas-liquid cyclone separator is used for separating the uncondensed gas from the condensed liquid, so that the gas returns to the inlet of the condenser to be continuously condensed, and the liquid continuously flows into the evaporator, so that the reduction of the heat absorption capacity of the uncondensed gas caused by the flowing of the uncondensed gas into the evaporator can be avoided, the obstruction of the continuous flow of the liquid caused by the aggregation of the uncondensed gas at the outlet of the condenser can be avoided, and the influence of the uncondensed gas on the operation of the separated heat pipe can be eliminated.

Description

High-power compact type separation type heat pipe

Technical Field

The utility model relates to the technical field of nuclear power passive cooling, in particular to a high-power compact type separated heat pipe.

Background

Nuclear power is an efficient, economical and green energy source and occupies a significant position in the global energy proportion. Spent fuel is usually stored in a spent fuel pool after being unloaded from a reactor, and the spent fuel still has large decay heat, so that the temperature in the pool is overhigh and is normally taken away by an active cooling system in the pool. When the whole plant is powered off due to a major disaster, the active cooling system can only work for 72 hours, and if the active system cannot work or exceeds 72 hours, the spent fuel cannot be cooled, the temperature of the spent fuel is too high due to continuous heat release, the water in the spent fuel pool is evaporated, and even the spent fuel rod is destroyed.

The waste heat discharging system of the spent fuel pool of the nuclear power plant needs to meet higher safety requirements, the working water temperature of the spent fuel pool is 40-60 ℃, the working water temperature cannot exceed 80 ℃ under accident working conditions, and the maximum temperature of air in a plant area is 40-50 ℃. Aiming at the heat transfer process of the small temperature difference and large heat quantity, the separation type heat pipe technology is adopted, so that an efficient passive heat dissipation mode is adopted, and the water temperature of the spent pool is ensured to be in a controllable range under extreme conditions.

The separated heat pipe is a novel heat pipe technology formed on the basis of a loop heat pipe, an evaporation section and a condensation section are arranged separately, an evaporation section heat exchanger is arranged in a spent pool, a condensation section heat exchanger is arranged at a position higher than the evaporation section heat exchanger, circulating driving force is provided through a certain height difference, and the two heat exchangers are connected through a rising pipe and a falling pipe to form a circulating loop. The separated heat pipe does not need external force for driving, has the advantages of simple system structure, high heat transfer efficiency, high reliability and the like, and can not consider the entrainment limit, the capillary limit and the boiling limit. At present, the low-power separated heat pipe is already applied to the fields of waste heat recovery, air conditioning refrigeration, data center heat dissipation and the like.

In the nuclear power field, areva and Xuehut companies respectively propose a scheme for cooling a spent fuel pool based on a separate heat pipe. However, the separated heat pipe has a relatively large number of parts, so that the heat pipe loop has poor tightness, noncondensable gas easily enters the heat pipe, the evaporation temperature is increased, and the inlet of the noncondensable gas accumulation condenser hinders the condensation process.

The Chinese patent with the application number of CN201520401230.9 discloses a separated heat pipe type passive waste heat discharging system of a pressurized water reactor nuclear power station, which is based on the scheme that the separated heat pipe is used as a passive waste heat discharging system of a pressurized water reactor nuclear power station steam generator, water in the generator is led out to exchange heat with the separated heat pipe, and the scheme designs the separated heat pipe, but does not consider the influence of non-condensable gas. In addition, chinese patent with application number CN201821167308.5 discloses a passive cooling separation type heat pipe arrangement structure in spent fuel pool, the scheme adopts a tube bundle as evaporator and a fin tube bundle as heat transfer element of condenser, the scheme designs the structures of evaporator and condenser, but the compactness of the heat transfer element of the scheme is lower, and the heat exchanger does not consider the influence of noncondensable gas on the heat pipe work.

Disclosure of Invention

The utility model aims to provide a high-power compact separation type heat pipe so as to solve the problems in the prior art, and by additionally arranging a gas-liquid cyclone separator in the separation type heat pipe, the gas which is not condensed by a condenser can be separated from the condensed liquid by utilizing the gas-liquid cyclone separator, so that the gas returns to an inlet of the condenser to be continuously condensed, the liquid continuously flows into an evaporator, and the influence of the uncondensed gas on the operation of the separation type heat pipe can be eliminated.

In order to achieve the above object, the present utility model provides the following solutions:

the utility model provides a high-power compact separation type heat pipe which comprises an evaporator, a rising pipe, a condenser, a falling pipe and a gas-liquid cyclone separator, wherein an outlet of the evaporator is communicated with an inlet of the condenser through the rising pipe, an outlet of the condenser is communicated with an inlet of the gas-liquid cyclone separator, a gas outlet of the gas-liquid cyclone separator is communicated with an inlet of the condenser, a liquid outlet of the gas-liquid cyclone separator is communicated with an inlet of the evaporator through the falling pipe, and the gas-liquid cyclone separator separates uncondensed gas and condensed liquid of the condenser, so that the gas returns to the inlet of the condenser to be continuously condensed, and the liquid continuously flows into the evaporator.

Preferably, the evaporator comprises a first plate heat exchange element, an outlet of the first plate heat exchange element is connected with a first outlet collecting portion, an inlet of the first plate heat exchange element is connected with a first inlet collecting portion, the first outlet collecting portion and the first inlet collecting portion are of dome structures, and a plurality of first plate heat exchange elements are arranged along the thickness direction and are attached to the inner diameter side of the dome structures.

Preferably, the first plate heat exchange element comprises heat exchange plates, herringbone heat exchange protrusions are arranged on the outer surfaces of the heat exchange plates, asymmetric bubbling structures are arranged on the inner surfaces of the heat exchange plates, and the asymmetric bubbling structures adjacent to the heat exchange plates are attached to form heat exchange channels.

Preferably, the condenser comprises a second plate heat exchange element and an air duct, wherein the second plate heat exchange elements are opposite in the thickness direction and are arranged in a V-shaped structure, and an opening of the V-shaped structure faces to an air outlet of the air duct.

Preferably, the second plate heat exchange element comprises a flat tube and a fin structure connected to the outer wall of the flat tube, wherein a plurality of through holes are distributed in the flat tube along the width direction, and the fin structure is arranged in a serpentine structure along the length direction of the flat tube.

Preferably, the inlet of the rising pipe is communicated with the outlet of the evaporator, the outlet of the rising pipe is communicated with the inlet of the condenser, the rising pipe comprises a first horizontal pipe section and a first rest pipe section, the first rest pipe section comprises a first vertical pipe section and/or a first inclined pipe section which is inclined upwards, and the first horizontal pipe section is positioned at the inlet of the condenser.

Preferably, the one-way conduction valve is of a Tesla valve structure, an inlet of the one-way conduction valve is communicated with an outlet of the evaporator, and an outlet of the one-way conduction valve is communicated with an inlet of the rising pipe.

Preferably, the rising pipe is provided with a vacuum pumping port, and the vacuum pumping port is connected with a vacuum pump.

Preferably, the inlet of the downcomer is communicated with the liquid outlet of the gas-liquid cyclone separator, the outlet of the downcomer is communicated with the inlet of the evaporator, the downcomer comprises a second horizontal pipe section and a second rest pipe section, the second rest pipe section comprises a second vertical pipe section and/or a second inclined pipe section which is inclined downwards, and the second horizontal pipe section is positioned at the inlet of the evaporator.

Preferably, the down tube is provided with a liquid filling port, the liquid filling port is sequentially connected with a liquid filling pump and a liquid storage tank, the liquid filling pump adopts a bidirectional pump, and a waste water outflow branch is arranged between the bidirectional pump and the liquid storage tank.

Compared with the prior art, the utility model has the following technical effects:

(1) According to the utility model, the gas-liquid cyclone separator is additionally arranged in the separated heat pipe, so that the gas which is not condensed by the condenser can be separated from the condensed liquid by utilizing the gas-liquid cyclone separator, so that the gas returns to the inlet of the condenser to be continuously condensed, the liquid continuously flows into the evaporator, the heat absorption capacity of the uncondensed gas is prevented from being reduced due to the fact that the uncondensed gas flows into the evaporator, the barrier that the liquid continuously flows due to the fact that the uncondensed gas is gathered at the outlet of the condenser is avoided, and the influence of the uncondensed gas on the operation of the separated heat pipe can be eliminated; in addition, the plate type heat transfer element is adopted as an evaporator and a condenser, so that the evaporator has the advantages of high efficiency, low resistance, strong pressure resistance and compact structure; by adopting corrugated plates as the evaporator heat transfer elements and aluminum high-fin flat tubes as the condenser heat transfer elements, the heat transfer performance of the equipment can be improved, the flow resistance of working media can be reduced, and the volume and weight of the equipment can be reduced;

(2) According to the utility model, the herringbone heat exchange protrusions are arranged on the surfaces of the heat exchange channels of the first plate type heat exchange element, the heat exchange area of the heat exchange channels can be increased by utilizing the herringbone heat exchange protrusions, the heat exchange effect is improved, the asymmetric bubbling structures are arranged between adjacent heat exchange channels, the supporting structures between the heat exchange plates can be formed by utilizing the asymmetric bubbling structures, the structural strength of the first plate type heat exchange element is improved, meanwhile, the asymmetric bubbling structures can also enhance the disturbance of fluid in the heat exchange channels, promote the air bubbles to separate from the wall surfaces of the heat exchange channels, form turbulence in the flowing process, and increase the heat exchange performance of the fluid;

(3) The condenser comprises the second plate heat exchange elements and the air duct, wherein the second plate heat exchange elements are opposite in the thickness direction and are arranged in a V-shaped structure, the opening of the V-shaped structure faces the air outlet of the air duct, and compared with the horizontal arrangement, the V-shaped structure can reduce the occupied area, reduce the flow resistance, and compared with the vertical arrangement, the V-shaped structure can improve the circulation effect of air flow and improve the heat dissipation effect;

(4) The second plate type heat exchange element comprises the flat tube and the fin structure connected to the outer wall of the flat tube, the heat transfer surface of the flat tube is approximately a plane, the dirt heat resistance of the heat transfer element can be reduced, the heat transfer coefficient is higher, the fin structure is arranged in a serpentine structure along the length direction of the flat tube, the contact area between fins of the serpentine structure and air is large, the air flowing direction is more stable, the pressure drop of the air side is smaller, and a better heat dissipation effect is achieved.

(5) The one-way conduction valve can enable steam in the head of the evaporator to flow into the ascending pipe at a higher speed, so that gas backflow and backflow are prevented, and the valve body structure can separate liquid working media in the steam and backflow into the evaporator for re-evaporation.

Drawings

In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the drawings that are needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present utility model, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

FIG. 1 is a schematic diagram of the overall circuit of the present utility model;

FIG. 2 is a schematic diagram of a liquid filling and draining system according to the present utility model;

FIG. 3 is a schematic diagram of a vacuum pumping system according to the present utility model;

FIG. 4 is a schematic view of an evaporator according to the present utility model;

FIG. 5 is a schematic view of the arrangement of the first plate heat exchange element of the present utility model;

FIG. 6 is a schematic view of a first plate heat exchange element according to the present utility model;

FIG. 7 is a schematic view of a condenser according to the present utility model;

FIG. 8 is a schematic view of a second plate heat exchange element according to the present utility model;

FIG. 9 is a schematic diagram of the end face structure of a single flat tube and fin structure thereof according to the present utility model

Wherein, 1, an evaporator; 11. a first plate heat exchange element; 111. a heat exchange plate; 112. a heat exchange channel; 113. the herringbone heat exchange bulges; 114. an asymmetric bubbling structure; 12. a first outlet collection portion; 13. a first inlet header; 2. a one-way conduction valve; 3. a rising pipe; 4. a condenser; 41. a second plate heat exchange element; 411. a flat tube; 4111. a through hole; 412. a fin structure; 4121. the fin heat exchange bulges; 42. a second inlet header; 43. a second outlet header; 5. a gas-liquid cyclone separator; 6. a down pipe; 7. a vacuum pumping port; 71. a vacuum pump; 72. a first stop valve; 8. a liquid filling port; 81. a liquid filling pump; 82. a liquid storage tank; 83. a waste water outflow branch; 84. a second shut-off valve; 85. a third stop valve; 86. a fourth shut-off valve; 9. an air duct.

Detailed Description

The following description of the embodiments of the present utility model will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present utility model, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.

The utility model aims to provide a high-power compact separation type heat pipe, which solves the problems in the prior art, and by additionally arranging a gas-liquid cyclone separator in the separation type heat pipe, the gas which is not condensed by a condenser can be separated from the condensed liquid by utilizing the gas-liquid cyclone separator, so that the gas returns to an inlet of the condenser to be continuously condensed, the liquid continuously flows into an evaporator, and the influence of the uncondensed gas on the operation of the separation type heat pipe can be eliminated.

In order that the above-recited objects, features and advantages of the present utility model will become more readily apparent, a more particular description of the utility model will be rendered by reference to the appended drawings and appended detailed description.

As shown in fig. 1 to 8, the utility model provides a high-power compact separation type heat pipe, which comprises an evaporator 1, a rising pipe 3, a condenser 4, a gas-liquid cyclone separator 5 and a falling pipe 6, wherein the separation type heat pipe forms a circulation loop of working media filled in the separation type heat pipe, the evaporator 1 and the condenser 4 are both heat exchanger structures, the heat exchange capacity is good, the condenser 4 is placed at a position higher than the evaporator 1, and the pressure head generated by the placement height difference needs to be larger than the maximum resistance drop when in circulation. Specifically, the evaporator 1 is used for absorbing heat to gasify the working medium therein to form gas, and the condenser 4 is used for dissipating heat to condense the gasified working medium to form liquid. The outlet of the evaporator 1 is communicated with the inlet of the condenser 4 through the ascending pipe 3, the outlet of the condenser 4 is communicated with the inlet of the gas-liquid cyclone separator 5, the gas outlet of the gas-liquid cyclone separator 5 is communicated with the inlet of the condenser 4, and the liquid outlet of the gas-liquid cyclone separator 5 is communicated with the inlet of the evaporator 1 through the descending pipe 6. The gas-liquid cyclone separator 5 can adopt the existing structure, and has an inlet, a gas outlet and a liquid outlet, the steam which cannot be completely condensed after passing through the condenser 4 generates cyclone flow through the gas-liquid cyclone separator 5, the steam and a small amount of uncondensed gas can be gathered at the upper part of the center because of centrifugal force, the liquid is gathered at the lower part, the gas phase gradually accumulates to generate pressure, the gas phase automatically returns to the inlet of the condenser 4 along a pipeline to enter the condenser 4 for re-condensation, and the liquid continuously returns to the inlet of the evaporator 1. According to the utility model, the gas-liquid cyclone separator 5 is additionally arranged in the separated heat pipe, so that the gas which is not condensed by the condenser 4 (particularly, the gas which is not condensed in summer and has more working medium gas when the condensation effect is poor) can be separated from the condensed liquid by the gas-liquid cyclone separator 5, the gas returns to the inlet of the condenser 4 to be continuously condensed, the liquid continuously flows into the evaporator 1, the increase of flow resistance and even unsmooth liquid return caused by the fact that the uncondensed gas flows into the downcomer 6 can be avoided, the decrease of the heat absorption capacity of the evaporator 1 can be caused, the obstruction of continuous flow of the liquid caused by the fact that the uncondensed gas is gathered at the outlet of the condenser 4 can be avoided, the rise of the working medium condensation temperature can be avoided, and the influence of the uncondensed gas on the operation of the separated heat pipe can be further eliminated.

As shown in fig. 4 to 6, the evaporator 1 may include a first plate heat exchange element 11, which is made of stainless steel by stamping, and a plurality of first plate heat exchange elements 11 may be arranged in the width direction, so that the heat transfer effect is ensured on the basis of increasing the tiling area; and the two layers can be arranged at intervals in the thickness direction, so that the occupied space requirement in the width direction is reduced. The first plate heat exchange element 11 has a heat exchange channel 112 provided therein, the working medium flows in the heat exchange channel 112, the outside of the first plate heat exchange element 11 contacts with an object to be cooled (e.g., a water body in a spent fuel pool), the working medium in the heat exchange channel 112 exchanges heat with an external object, and the working medium is heated and evaporated into gas. The flow direction of working medium in the heat exchange channel 112 of the first plate heat exchange element 11 is from bottom to top, when in operation, the bottom of the heat exchange channel 112 is liquid water, the middle section is in a gas-liquid two-phase state, and the top is in a pure gaseous state or a gaseous state with a part of water entrained. The first plate heat exchange element 11 has a generally plate-like structure, and a plurality of heat exchange channels 112 are provided in the extending direction of the plate-like structure, which can further improve the heat exchange efficiency. In order to ensure smooth circulation of the working medium, the outlet of the first plate heat exchange element 11 is connected with a first outlet collecting part 12, the inlet is connected with a first inlet collecting part 13, the working medium is distributed into each heat exchange channel 112 through the first inlet collecting part 13, and the working medium flowing out of the heat exchange channels 112 enters a pipeline (such as a riser 3) communicated with the condenser 4 through the first outlet collecting part 12. The first outlet collecting part 12 and the first inlet collecting part 13 are of dome structures, and the corresponding inlets and outlets are positioned at the top of the dome structures, so that inflow and outflow of working media can be better guaranteed. The plurality of first plate heat exchange elements 11 are arranged in the thickness direction and are attached to the inner diameter side of the dome structure, so that a structure with the width similar to the thickness dimension is formed, and the dome structure can be adapted to the first outlet collecting portion 12 and the first inlet collecting portion 13.

The first plate heat exchange element 11 may comprise heat exchanger plates 111, which heat exchanger plates 111 may be all welded after being rolled integrally from 304 stainless steel having a wall thickness of only 0.4 mm. The stainless steel alloy is adopted as a material, and the full-welded plate bundle is adopted, so that the limitation of the temperature and the pressure of the spent fuel pool due to the adoption of rubber cushion sealing is avoided, the corrosion resistance is excellent, the service life is long, and the stainless steel alloy is suitable for being soaked in the spent fuel pool for a long time. The outer surface of the rolled heat exchange plate 111 is provided with the herringbone heat exchange protrusions 113, and the heat exchange area of the heat exchange channel 112 can be increased by utilizing the herringbone heat exchange protrusions 113, so that the heat exchange effect is improved. The asymmetric bubbling structures 114 are arranged on the inner surfaces, the asymmetric bubbling structures 114 of the adjacent heat exchange plates 111 are attached to form the heat exchange channels 112, the asymmetric bubbling structures 114 can form a supporting structure between the heat exchange plates 111, so that the structural strength of the first plate heat exchange element 11 is improved, meanwhile, the asymmetric bubbling structures 114 can also enhance the disturbance of fluid in the heat exchange channels 112, promote bubbles to separate from the wall surfaces of the heat exchange channels 112, form turbulence in the flowing process, and improve the heat exchange performance of the fluid. Compared with the tube type element, the first plate heat exchange element 11 has light weight, higher compactness, better pressure resistance and lower pressure drop because the flow area is 5 times larger than that of the tube type element when the heat exchange area is the same; and the bubbling structure is adopted to increase the fluid disturbance, and the heat exchange coefficient is increased by 1-3 times compared with a tube type.

As shown in fig. 7 to 9, the condenser 4 may include a second plate heat exchange element 41 and a fan drum 9, where the second plate heat exchange element 41 adopts a structure that a high-fin small-channel flat tube bundle is formed by one-step forming aluminum flat tubes and brazing serpentine fins, and the compactness can be more than 800m ² /m ³ The heat dissipation capacity of the element is improved. The air duct 9 is arranged at the top of the condenser 4, the height is calculated according to the lift force required by the air and the ambient temperature, and the air duct 9 can be a frameThe cross-sectional shape and size of the frame structure are consistent with the top of the condenser 4. The second plate heat exchange elements 41 are opposite in thickness direction and are arranged in a V-shaped structure, and an included angle between two support arms of the V-shaped structure is 30-60 degrees. In addition, each of the support arms of the V-shaped structure may be provided with a plurality of second plate heat exchanging elements 41 in the width direction or the thickness direction of the second plate heat exchanging elements 41. A second inlet collection 42 is provided at the top and a second outlet collection 43 is provided at the bottom. The opening of the V-shaped structure faces the air outlet of the air duct 9, and the second plate heat exchange element 41 can be cooled by air flow. Compared with the structure of horizontally placing the second plate heat exchange element 41, the V-shaped structure can reduce the occupied area, reduce the flowing resistance of the internal working medium, and can improve the heat exchange area of windward arrangement, the circulation effect of cooling air flow and the heat dissipation effect relative to the structure of vertically placing.

The second plate heat exchange element 41 may include flat tubes 411 and fin structures 412 connected to outer walls of the flat tubes 411, wherein the fin structures 412 are disposed on flat tube walls on both sides of each flat tube 411, and when a plurality of flat tubes 411 are disposed in a thickness direction, adjacent fin structures 412 may be connected or may have gaps. The flat tube 411 and the fin structure 412 can be made of aluminum with good heat conduction performance, compared with the traditional carbon steel and low alloy steel, the mass is only 1/3, the heat conduction coefficient is improved by more than 3 times, and the corrosion resistance is better due to the fact that the flat tube 411 and the fin structure 412 contain 1.0% -1.5% of manganese. The fin structure 412 is welded to the flat tube 411 by high-temperature brazing. The heat transfer surface of the flat tube 411 is approximately plane, so that dirt heat resistance of the heat transfer element can be reduced, and the heat transfer coefficient is higher. The fin structure 412 may be strip-shaped sheet fins arranged in segments, or may be serpentine fins connected to each other. A plurality of through holes 4111 are distributed in the flat tube 411 along the width direction, and the through holes 4111 are used for circulating working media to be cooled. The fin structure 412 can be arranged along the length direction of the flat tube 411 to form a serpentine structure, the contact area between fins and air of the serpentine structure is large, the air flow direction is more stable, the pressure drop of the air side is smaller, a better heat dissipation effect is achieved, further, a plurality of fin heat exchanging protrusions 4121 can be arranged on the surface of the serpentine structure, the heat exchanging area of the serpentine structure can be remarkably increased through the fin heat exchanging protrusions 4121, and the heat dissipation effect is further improved.

And in combination with the illustration of fig. 1, the heat-insulating material is composed of a rising pipe 3, the rising pipe 3 can be made of stainless steel, all pipe sections of the rising pipe 3 are coated with the heat-insulating material for avoiding gas condensation in the rising pipe 3, the heat-insulating material can be made of glass fiber, and a metal shell protection layer is wrapped outside the heat-insulating material. The rising pipe 3 is connected with the evaporator 1 and the condenser 4 in a welding mode, the inlet of the rising pipe 3 is communicated with the outlet of the evaporator 1, the outlet of the rising pipe 3 is communicated with the inlet of the condenser 4, and gas generated in the evaporator 1 enters the evaporator 1 through the rising pipe 3. The riser 3 may comprise a first horizontal pipe section and a first remaining pipe section, wherein the first remaining pipe section may comprise only a first vertical pipe section, may comprise only a first inclined pipe section inclined upwards, may comprise both the first vertical pipe section and the first inclined pipe section inclined upwards, and when the first inclined pipe section is adopted, the inclination angle may be determined according to the actual installation site, and the minimum inclination angle should be greater than 5 °, and the first horizontal pipe section is located at the inlet of the condenser 4 so as to be connected with the condenser 4.

A one-way conduction valve 2 can be arranged, and the one-way conduction valve 2 can be connected with the evaporator 1 and the rising pipe 3 in a welding mode. Specifically, the one-way conduction valve 2 can select a common one-way valve with a mechanical movable component, and also can select a tesla valve without a mechanical movable component, an inlet of the tesla valve is communicated with an outlet of the evaporator 1, an outlet of the tesla valve is communicated with an inlet of the riser 3, high-pressure gas evaporated in the first outlet collecting part 12 of the evaporator 1 can flow into the riser 3 more quickly by the arrangement of the tesla valve, backflow and backflow are prevented, evaporation pressure is reduced due to speed increase in the process of flowing through the tesla valve, the evaporation process of the evaporator 1 is facilitated, and liquid water in the gas can be fully separated and flows back into the evaporator 1 for re-evaporation due to the collision process of the steam.

As shown in fig. 1 and 3, the riser 3 may be provided with a vacuum port 7, where the vacuum port 7 is located at a high point of the riser 3, and is capable of extracting gas from the top to perform vacuum pumping, so as to avoid the influence of the extracted liquid on the vacuum pump 71. In addition, when the vacuumizing port 7 is used for filling air for purging, liquid working media in the loop can be well discharged. The vacuumizing port 7 is connected with a vacuum pump 71, and an absolute pressure gauge is arranged at the outlet of the vacuum pump 71 and used for displaying the absolute pressure in the separated heat pipe in real time. The vacuumizing port 7 is sealed by a vacuum valve, a vacuum-resistant clamping sleeve or a liquid sealing structure. The vacuum pump 71 and the rising pipe 3 are provided with a first shut-off valve 72 (which may be a vacuum shut-off valve), and the inside of the loop of the split heat pipe can be evacuated by opening the first shut-off valve 72 and the vacuum pump 71 as needed, and air can be supplied into the loop of the split heat pipe by opening the first shut-off valve 72. In addition, the vacuum pump 71 can be used to discharge the non-condensed gas in the separate heat pipe.

The evaporator is shown in fig. 1, and comprises a down pipe 6, wherein the down pipe 6 can be made of stainless steel and is connected with the evaporator 1 and the gas-liquid cyclone separator 5 in a welding mode, the inlet of the down pipe 6 is connected with the liquid outlet of the gas-liquid cyclone separator 5, and the outlet of the down pipe 6 is connected with the inlet of the evaporator 1. The downcomer 6 may comprise a second horizontal pipe section and a second remaining pipe section, the second remaining pipe section may comprise only a second vertical pipe section, may comprise only a second inclined pipe section inclined downward, and may comprise both a second vertical pipe section and a second inclined pipe section inclined upward, when the second inclined pipe section is adopted, the inclination angle may be determined according to the actual installation site, and the minimum inclination angle should be greater than 5 °, and the second horizontal pipe section is located at the inlet of the evaporator 1 so as to be connected with the evaporator 1. It should be noted that when the cooling device is used for cooling the spent fuel pool, the part of the down tube 6 immersed in the spent fuel pool can be subjected to heat insulation treatment by adopting a vacuum sleeve, so that condensed water is prevented from carrying out a large amount of heat exchange with high temperature water in the spent fuel pool in the down tube 6, and vaporization occurs in advance.

As shown in fig. 1 and 2, the downcomer 6 is provided with a liquid filling port 8, and the liquid filling port 8 can be arranged at a position close to the inlet of the evaporator 1, so that the working medium in the loop of the separate heat pipe can be conveniently injected and emptied, and the normal work of the evaporator 1 can not be affected when the working medium enters the evaporator 1 after being injected, so that the working medium can be supplemented in the operation process. The liquid filling port 8 is sequentially connected with a liquid filling pump 81 and a liquid storage tank 82, a second stop valve 84 is arranged between the liquid filling pump 81 and the descending tube 6, a third stop valve 85 is arranged between the liquid filling pump 81 and the liquid storage tank 82, and the liquid filling pump 81 can inject working medium in the liquid storage tank 82 into the liquid filling port 8 to serve as circulating medium of a loop of the separated heat pipe. The liquid storage tank 82 adopts a closed water tank, and can withstand the negative pressure of 0.1 MPa. The liquid filling port 8 is sealed by a vacuum valve, a vacuum-resistant clamping sleeve or a liquid sealing structure. The charge pump 81 can also adopt a bidirectional pump, a waste water outflow branch 83 is arranged between the bidirectional pump and the liquid storage tank 82, a fourth stop valve 86 is arranged between the waste water outflow branch 83 and the charge pump 81, and the waste water outflow branch 83 can be used for carrying out emptying post-treatment by controlling the forward rotation and the reverse rotation of the charge pump 81 to control whether to inject working medium into the liquid filling port 8 or discharge working medium.

The working principle of the utility model is as follows:

in the use process, when the temperature of the outer side of the evaporator 1 exceeds the phase change temperature of working media in the evaporator 1, the working media in the evaporator 1 are evaporated into superheated steam, the superheated steam flows through the one-way conduction valve 2 and then rises to the condenser 4 along the rising pipe 3, the steam is condensed after convection heat exchange with external air in the condenser 4, the steam flows into the gas-liquid cyclone separator 5 along the falling pipe 6 under the action of gravity, liquid and gas are separated in the gas-liquid cyclone process, the separated liquid working media continue to return to the evaporator 1 along the falling pipe 6, the gas working media generate pressure after self compression, flow to the inlet of the condenser 4 and enter the condenser 4 to be continuously subjected to heat exchange condensation with the external air. Under the action of the air duct 9, air with lower temperature flows through the condenser 4 from bottom to top, the temperature is raised after absorbing the heat of the condenser 4, the air flows upwards along the air duct 9 by virtue of temperature difference, the purpose of continuously taking away the heat of working media in the condenser 4 can be realized after natural convection, and the working media in a loop of the separated heat pipe can realize continuous circulating operation.

When the separated heat pipe needs maintenance or is not used for a long time, external air can enter the loop of the separated heat pipe by opening the vacuumizing port 7, the operating working medium in the loop of the separated heat pipe is discharged through the liquid filling port 8, then the pipeline is cleaned through chemical reagents, and the pipeline is purged and sealed after cleaning, so that internal corrosion and pollutant entering are avoided. When the vacuum pump 71 is started and the separated heat pipe is vacuumized when the vacuum pump is needed to be reused, the loop of the separated heat pipe is vacuumized to a set vacuum degree, then the first stop valve 72 is closed, the vacuum pump 71 stops working, the loop vacuum is kept not less than 30 minutes, the numerical value change of the absolute pressure sensor is observed, and when the change value is smaller than a specified value, the separated heat pipe can be regarded as meeting the use condition. Then the liquid filling pump 81 is started, working medium (such as deionized water) in the liquid storage tank 82 is filled into the loop of the separation type heat pipe, and the liquid filling amount of the loop is obtained through the indication change of the liquid level meter arranged in the liquid storage tank 82 before and after liquid filling.

The principles and embodiments of the present utility model have been described in detail with reference to specific examples, which are provided to facilitate understanding of the method and core ideas of the present utility model; also, it is within the scope of the present utility model to be modified by those of ordinary skill in the art in light of the present teachings. In view of the foregoing, this description should not be construed as limiting the utility model.

Claims (10)

1. A high-power compact type separated heat pipe is characterized in that: the evaporator comprises an evaporator, a rising pipe, a condenser, a falling pipe and a gas-liquid cyclone separator, wherein an outlet of the evaporator is communicated with an inlet of the condenser through the rising pipe, an outlet of the condenser is communicated with an inlet of the gas-liquid cyclone separator, a gas outlet of the gas-liquid cyclone separator is communicated with an inlet of the condenser, a liquid outlet of the gas-liquid cyclone separator is communicated with an inlet of the evaporator through the falling pipe, and the gas-liquid cyclone separator separates uncondensed gas of the condenser from condensed liquid, so that the gas returns to the inlet of the condenser to be condensed continuously, and the liquid continuously flows into the evaporator.

2. The high power compact split heat pipe of claim 1 wherein: the evaporator comprises a first plate heat exchange element, wherein an outlet of the first plate heat exchange element is connected with a first outlet collecting part, an inlet of the first plate heat exchange element is connected with a first inlet collecting part, the first outlet collecting part and the first inlet collecting part are of dome structures, and a plurality of first plate heat exchange elements are arranged along the thickness direction and are attached to the inner diameter side of the dome structures.

3. The high power compact split heat pipe of claim 2 wherein: the first plate type heat exchange element comprises heat exchange plates, herringbone heat exchange protrusions are arranged on the outer surfaces of the heat exchange plates, asymmetric bubbling structures are arranged on the inner surfaces of the heat exchange plates, and the asymmetric bubbling structures of the adjacent heat exchange plates are attached to form heat exchange channels.

4. The high power compact split heat pipe of claim 1 wherein: the condenser comprises a second plate heat exchange element and an air duct, wherein the second plate heat exchange element is opposite in the thickness direction and is arranged in a V-shaped structure, and an opening of the V-shaped structure faces to an air outlet of the air duct.

5. The high power compact split heat pipe of claim 4 wherein: the second plate type heat exchange element comprises a flat tube and a fin structure connected to the outer wall of the flat tube, a plurality of through holes are distributed in the flat tube along the width direction, and the fin structure is arranged in a serpentine structure along the length direction of the flat tube.

6. The high power compact split heat pipe as claimed in any one of claims 1-5, wherein: the inlet of the rising pipe is communicated with the outlet of the evaporator, the outlet of the rising pipe is communicated with the inlet of the condenser, the rising pipe comprises a first horizontal pipe section and a first other pipe section, the first other pipe section comprises a first vertical pipe section and/or a first inclined pipe section which is inclined upwards, and the first horizontal pipe section is positioned at the inlet of the condenser.

7. The high power compact split heat pipe of claim 6 wherein: the one-way conduction valve is of a Tesla valve structure, an inlet of the one-way conduction valve is communicated with an outlet of the evaporator, and an outlet of the one-way conduction valve is communicated with an inlet of the rising pipe.

8. The high power compact split heat pipe of claim 6 wherein: the rising pipe is provided with a vacuumizing port, and the vacuumizing port is connected with a vacuum pump.

9. The high power compact split heat pipe of claim 6 wherein: the inlet of the descending pipe is communicated with the liquid outlet of the gas-liquid cyclone separator, the outlet of the descending pipe is communicated with the inlet of the evaporator, the descending pipe comprises a second horizontal pipe section and a second rest pipe section, the second rest pipe section comprises a second vertical pipe section and/or a second inclined pipe section which is inclined downwards, and the second horizontal pipe section is positioned at the inlet of the evaporator.

10. The high power compact split heat pipe of claim 9 wherein: the down tube is provided with a liquid filling port, the liquid filling port is sequentially connected with a liquid filling pump and a liquid storage tank, the liquid filling pump adopts a bidirectional pump, and a waste water outflow branch is arranged between the bidirectional pump and the liquid storage tank.