CN110736374A - heat accumulator capable of automatically heating according to temperature of heat accumulation material - Google Patents
heat accumulator capable of automatically heating according to temperature of heat accumulation material Download PDFInfo
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- CN110736374A CN110736374A CN201911032936.1A CN201911032936A CN110736374A CN 110736374 A CN110736374 A CN 110736374A CN 201911032936 A CN201911032936 A CN 201911032936A CN 110736374 A CN110736374 A CN 110736374A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0233—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes the conduits having a particular shape, e.g. non-circular cross-section, annular
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H7/00—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release
- F24H7/02—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid
- F24H7/0208—Storage heaters, i.e. heaters in which the energy is stored as heat in masses for subsequent release the released heat being conveyed to a transfer fluid using electrical energy supply
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
- F28D15/046—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure characterised by the material or the construction of the capillary structure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/06—Control arrangements therefor
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Filling Or Discharging Of Gas Storage Vessels (AREA)
Abstract
The invention provides loop heat pipe heat accumulators which can be heated automatically according to the temperature of heat storage materials, the heat accumulator comprises a shell, a gas inlet channel, a gas outlet channel, loop heat pipes and a gas chamber, the heat storage materials are arranged in the shell, an electric heater for auxiliary heating is arranged in the shell, a valve is arranged on the gas inlet channel, a second valve is arranged on a bypass pipeline, a second temperature sensor is arranged in the heat accumulator and used for detecting the temperature of the heat storage materials in the heat accumulator, the second temperature sensor is in data connection with a central controller, if the temperature detected by the second temperature sensor is lower than a fixed value of , the central controller controls the electric heater to heat, and if the temperature detected by the second temperature sensor is higher than a fixed value of , the central controller stops the electric heater to heat.
Description
Technical Field
The invention relates to an loop heat pipe heat accumulator, in particular to a intelligent control loop heat pipe heat accumulator.
Background
The heat pipe technology is heat transfer elements called heat pipes invented by George glover Grover (George Grover) of national laboratory of Los Alamos (Los Alamos) in 1963, fully utilizes the heat conduction principle and the rapid heat transfer property of a phase change medium, and quickly transfers the heat of a heating object to the outside of a heat source through the heat pipes, and the heat conduction capability of the heat transfer elements exceeds the heat conduction capability of any known metal.
The heat pipe technology is widely applied to industries such as aerospace, military and the like by before, and is introduced into the radiator manufacturing industry, so that people change the design idea of the traditional radiator, get rid of a single heat dissipation mode of obtaining a better heat dissipation effect by only depending on a high-air-volume motor, adopt the heat pipe technology to enable the radiator to obtain a satisfactory heat exchange effect, and open up a new place in the heat dissipation industry.
In the prior art, the heat pipes generally rely on gravity to realize the circulation of the heat pipes, but the heat pipes are only suitable for the situation that the heat is absorbed at the lower part and released at the upper part, and cannot be applied to the situation that the heat is absorbed at the upper part and released at the lower part, therefore, aiming at the situation, in the previous invention, the inventor improves the prior invention, invents antigravity heat pipes and applies the antigravity heat pipes to heat accumulators, but the heat accumulators are not high in intelligent degree and cannot realize intelligent control, so heat accumulators based on intelligent control need to be designed.
Disclosure of Invention
The invention provides new loop heat pipe heat accumulators, which realize intelligent control by utilizing the performance of antigravity heat pipes and the expanded heat exchange area, thereby solving the technical problems in the prior art.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a th valve is arranged on the gas inlet channel and used for controlling the flow of the gas entering the heat accumulator, and a th valve is in data connection with the central controller.A th temperature sensor is arranged on the gas inlet channel, a th temperature sensor is used for measuring the temperature of the gas, a th temperature sensor is arranged upstream of the th valve , and a th temperature sensor is in data connection with the central controller;
the system is also provided with a bypass pipeline connected with the inlet channel, the connection position of the bypass pipeline and the inlet channel is positioned at the upstream of the valve , a second valve is arranged on the bypass pipeline, and the second valve is in data connection with the central controller;
a second temperature sensor is arranged in the heat accumulator and used for detecting the temperature of the heat storage material in the heat accumulator, the second temperature sensor is in data connection with a central controller, and the central controller automatically controls the opening and closing of the valve and the second valve according to the temperatures detected by the temperature sensor and the second temperature sensor.
Preferably, if the temperature detected by the th temperature sensor is lower than the temperature detected by the second temperature sensor, the central controller controls the th valve to be closed and the second valve to be opened.
Preferably, if the temperature detected by the th temperature sensor is higher than the temperature detected by the second temperature sensor, the central controller controls the th valve to be opened and the second valve to be closed.
Preferably, the electric heater is provided in plurality, and the heating power of the electric heater is lower and lower as the electric heater is closer to the gas chamber.
Preferably, the lower the heating power of the electric heater, the greater the magnitude closer to the gas chamber.
Preferably, the heat storage material is paraffin.
Preferably, the housing includes a fluid inlet and a fluid outlet, and the thermal storage material has a channel therein communicating the fluid inlet and the fluid outlet.
Preferably, the condensing end is an annular tube wrapped around the outer wall of the gas chamber.
Preferably, parts or all of the capillary wick are located at the evaporation end.
Preferably, the gas inlet passage is connected to the inlet pipe of the gas chamber, and the gas outlet passage is provided in the inlet pipe of the gas chamber and protrudes from the inlet pipe side of the gas chamber.
Preferably, the evaporation end comprises an ascending pipe, at least parts of the ascending pipe are provided with capillary cores so as to realize the function of a antigravity heat pipe, a pipeline of a condensation end flowing to the evaporation end is arranged in the center of the capillary cores, the outer wall surface of the evaporation end is provided with longitudinal vertical fins in a surrounding mode, an air outlet channel is arranged between two adjacent vertical fins and is in contact with the two adjacent vertical fins, a descending pipe of the heat pipe is arranged between the two adjacent vertical fins and is in contact with the two adjacent vertical fins, and at least parts of the ascending section and the descending section are arranged in the air inlet channel.
Preferably, the fluid inlet is located on the lower side of the housing and the fluid outlet is located on the upper side of the housing.
Preferably, the inlet duct of the gas chamber extends partially into the housing, the cross-sectional area of the gas chamber within the housing tapering downwardly in the height direction.
Preferably, the bottom of the gas chamber is of planar configuration.
Preferably, a plurality of gas chambers are arranged in the shell, and gas inlet channels of the plurality of gas chambers are in a parallel structure.
Preferably, the evaporation end is arranged at the inlet pipe of the gas chamber, at least parts of the evaporation end are filled with the capillary core, the center of the capillary core is provided with a pipeline from the condensation end to the evaporation end, and the outer wall surface of the evaporation end is provided with longitudinal vertical fins in a surrounding mode.
Preferably, the gas outlet channel is disposed between and in contact with two adjacent vertical fins.
Preferably, the condensation end pipeline flowing to the evaporation end is arranged between and in contact with two adjacent vertical fins.
The pipeline is a plurality of, the gas outlet passageway is a plurality of, the pipeline equals with gas outlet passageway's quantity.
, the tubes are preferably arranged between adjacent gas outlet channels, the gas outlet channels 4 flowing between adjacent evaporation end to condensation end tubes 9.
, the evaporation end flowing to the condensation end has the same distance to the center of the adjacent gas outlet channel 4, and the center of the gas outlet channel 4 has the same distance to the center of the adjacent gas evaporation end flowing to the condensation end 9.
Preferably, the radius of the gas outlet channel 4 is R, the radius of the pipeline 9 from the evaporation end to the condensation end is R, and the included angle between adjacent fins is a, so that the following requirements are met:
Sin(A)＝a*(r/R)-b*(r/R)2-c；
a, b, c are parameters,
wherein 1.23< a <1.24,0.225< b <0.235, 0.0185< c < 0.0195;
14°<A<30°；
0.24<r/R<0.5；
further , preferably, 0.26< R/R < 0.38.
Compared with the prior art, the invention has the following advantages:
1) the invention can realize the automatic heat storage of the heat accumulator by controlling the opening and closing of the valve through detecting the temperature of the heat storage material, because the temperature of high-temperature gas is lower than the temperature of the heat storage material in the heat accumulator in the research and development and experiment process, the heat storage is impossible in the situation, but the heat of the heat accumulator can be taken away, therefore, the heat storage of the heat accumulator can be intelligently controlled by intelligently controlling the opening and closing of the valve according to the detected temperature.
2) The invention provides heat accumulators with novel structures, which utilize anti-gravity heat pipes to exchange heat, transfer heat in gas to a cold source in the heat accumulator and improve the utilization of the heat.
3) The condensing end of the antigravity heat pipe is wound on the outer wall of the gas cavity, and the area of the gas cavity is enlarged, so that the heat exchange area is increased, and the heat exchange effect is improved.
4) The invention improves and designs the structure of the evaporation end of the loop heat pipe, and further improves the heat exchange coefficient.
5) According to the invention, through a large number of numerical simulation and experiments, included angles between the pipeline 9 at the gas outlet channel and the evaporation end of the loop heat pipe, which flow to the condensation end, and the adjacent fins are optimized, and the heat exchange efficiency is further improved by .
Drawings
Fig. 1 is a schematic view of the overall structure of the regenerator of the present invention.
Fig. 2 is a schematic view of embodiments of the gas chamber of the present invention.
Fig. 3 is a cross-sectional view of another embodiments of the gas chamber of the present invention.
Fig. 4 is a cross-sectional view a-a of fig. 3.
Fig. 5 is a schematic structural diagram of a heat pipe according to the present invention.
Fig. 6 is a schematic diagram of a multi-evaporation-end to condensation-end pipeline (descending section) according to the present invention.
Fig. 7 is a schematic view of a pipe connection structure for providing a capillary wick according to the present invention.
Fig. 8 is a schematic diagram of an intelligent control structure according to the present invention.
The reference numbers are that 1 shell, 2 heat storage materials, 3 bottom of gas chamber, 4 gas outlet channels, 5 gas inlet channels, 6 loop heat pipe evaporation end, 7 gas chamber, 8 loop heat pipe condensation end, 9 evaporation end flowing to condensation end pipeline (descending section), 10 condensation end flowing to evaporation end pipeline, 11 gas chamber inlet pipe, 12 fins, 13 capillary core, 14 central controller, 15 valve , 16 temperature sensor, 17 second valve
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.
The following detailed description of embodiments of the invention refers to the accompanying drawings.
antigravity loop heat pipe, as shown in fig. 5, the heat pipe comprises an evaporation end 6 and a condensation end 8, the evaporation end 6 is located above the condensation end 8, the evaporation end 6 is partially arranged on the fluid rising section, and at least part of the evaporation end of the fluid rising section is provided with a capillary wick 13, as shown in fig. 7.
Preferably, the evaporation end comprises two parts, namely an evaporation end flow direction condensation end pipeline (descending section) 9 and an ascending section. Preferably, a condensation end flow to the evaporation end line 10 is arranged in the rising section.
As shown in FIG. 1, loop heat pipe heat accumulators comprise a shell 1, a gas inlet channel 5, a gas outlet channel 4, a loop heat pipe and a gas chamber 7, wherein a heat accumulation material 2 is arranged in the shell 1, the heat pipe comprises an evaporation end 6 and a condensation end 8, the evaporation end 6 is positioned at the upper part of the condensation end 8, a capillary wick 13 is arranged in a pipeline leading to the evaporation end 6 of the condensation end 8, the condensation end 8 is arranged on the outer wall of the gas chamber 7, the gas chamber 7 is arranged in the shell 1, the loop heat pipe is a counter-gravity heat pipe as shown in FIG. 5, an outlet 5 of the gas inlet channel and an inlet of the gas outlet channel 4 are communicated with the gas chamber 7, the gas exchanges heat with the evaporation end 6 in the process of being introduced into the gas chamber 7 from the gas inlet channel 5, and the condensation end 8 conducts the heat to the heat accumulation material in the shell 1.
The invention provides heat accumulators with loop heat pipes of novel structures, which are simple in principle and compact in structure and obviously improve the cooling efficiency by arranging the loop heat pipes as efficient heat transfer tools.
Preferably, at least parts of the evaporation end 6 of the loop heat pipe are installed at the inlet of the gas chamber 7.
Preferably, at least parts of the gas inlet channels 5 are provided in the gas chamber 7 inlet duct and at least parts of the gas chamber 7 inlet duct are provided in the housing 1, whereby the gas in the gas inlet channels 5 can be made to participate in the heat exchange of the heat accumulating material in the housing 1, increasing the heat exchange effect.
Preferably, the gas chamber 7 is made of heat conducting material, preferably metal, such as copper and aluminum, and the heat of the gas can be transferred outwards through the gas chamber through the material of the gas chamber, so that heat exchange modes are added, and the heat of the gas can be transferred to the external heat storage material through the loop heat pipe and the gas chamber.
Preferably, an electric heater for auxiliary heating is arranged in the housing 1. When the heat is insufficient, the heating is supplemented by the electric heater.
Preferably, the electric heaters are arranged in plurality, the heating power of the electric heaters is lower and lower as the electric heaters are closer to the gas chamber 7, and step is further selected, the lower the heating power of the electric heaters is larger and larger as the electric heaters are closer to the gas chamber 7.
The heating of the electrical heating may be controlled by a central controller 14.
The fluid is preferably a medical fluid, the heat accumulator is heat accumulators with the function of heating medical fluid, and the medical fluid is used for fumigating and washing wounds.
Preferably, as shown in fig. 8, an th valve 15 is provided on the gas inlet channel 5 for controlling the flow of gas into the regenerator, and the th valve 15 is in data connection with the central controller 14, a temperature sensor 16 is provided on the gas inlet channel 5, a th temperature sensor 16 is provided for measuring the temperature of the gas, a th temperature sensor 16 is provided upstream of the th valve 15, and a th temperature sensor 16 is in data connection with the central controller 14.
The system is also provided with a bypass pipeline connected with the inlet channel 5, the connecting position of the bypass pipeline and the inlet channel 5 is positioned at the upstream of the th valve 15, the bypass pipeline is provided with a second valve 17, the second valve 17 is in data connection with the central controller 14, and the opening and closing of the second valve 17 can ensure whether the gas passes through a bypass pipeline or not.
Preferably, the th valve is open and the second valve is closed.
() controlling opening and closing of valve according to gas flow
Preferably, a gas sensor is arranged in the gas inlet channel 5 upstream of the th valve 15, and the gas sensor is used for detecting whether gas flows through the flue, the gas sensor is in data connection with a central controller, and the central controller controls the th valve 15 and the second valve 17 to open and close according to the data detected by the gas sensor and controls the electric heater to heat.
When the central controller detects that gas passes through the gas inlet channel 5, for example, when a fan starts to operate, high-temperature gas is conveyed, the central controller controls the valve to be opened, the second valve is closed, the gas can enter the heat accumulator, and the gas is discharged from the gas outlet channel after heat accumulation is completed.
Second, opening and closing of the control valve are detected according to temperature
Preferably, a second temperature sensor is provided in the regenerator to sense the temperature of the thermal storage material in the regenerator, the second temperature sensor is in data communication with the central controller 14, and the central controller 14 automatically controls the opening and closing of the valve and the second valve based on the temperatures sensed by the th temperature sensor and the second temperature sensor.
If the temperature sensed by the th temperature sensor is lower than the temperature sensed by the second temperature sensor, the central controller 14 controls the th valve to close and the second valve to open, if the temperature sensed by the th temperature sensor is higher than the temperature sensed by the second temperature sensor, the central controller 14 controls the th valve to open and the second valve to close.
The valve is controlled to open and close according to the detected temperature, so that the heat accumulator can be automatically stored, because the temperature of high-temperature gas is lower than the temperature of a heat storage material in the heat accumulator during research and development and experiments, the heat storage is impossible in the case that the heat storage is carried out, and the heat storage of the heat accumulator can be taken away.
(III) controlling the heating of the electric heater according to the temperature detection
The central controller 14 automatically controls the electric heater to heat according to the temperature detected by the th temperature sensor.
If the temperature detected by the th temperature sensor is lower than the constant value, the central controller 14 controls the electric heater to heat, and if the temperature detected by the th temperature sensor is higher than the constant value, the central controller 14 stops the electric heater from heating.
(IV) controlling the electric heater to heat according to the temperature of the heat storage material
Preferably, a second temperature sensor is arranged in the heat accumulator and used for detecting the temperature of the heat storage material in the heat accumulator. The second temperature sensor is in data connection with the central controller 14.
If the temperature detected by the second temperature sensor is lower than , the central controller 14 controls the electric heater to heat, and if the temperature detected by the second temperature sensor is higher than , the central controller 14 stops the electric heater to heat.
(V) opening and closing of the control valve and heating of the electric heater are controlled according to temperature detection
The central controller 14 automatically controls the opening and closing of the th valve and the second valve and the heating by the electric heater according to the temperatures detected by the th temperature sensor and the second temperature sensor.
If the temperature detected by the th temperature sensor is lower than the temperature detected by the second temperature sensor, the central controller 14 controls the th valve to close, the second valve to open, and the electric heater to heat, if the temperature detected by the th temperature sensor is higher than the temperature detected by the second temperature sensor, the central controller 14 controls the th valve to open, the second valve to close, and the electric heater to heat is stopped.
The valve is controlled to open and close according to the detected temperature, so that the heat accumulator can be automatically stored, because the temperature of high-temperature gas is lower than the temperature of a heat storage material in the heat accumulator in the research and development and experiment processes, the heat storage is impossible in the case that the heat storage is impossible, and the heat of the heat accumulator is taken away, so that an electric heater is needed to heat and store the heat at the moment to meet the working requirement, and the heat storage of the heat accumulator is intelligently controlled by intelligently controlling the valve to open and close according to the detected temperature.
Sixth, the opening degree of the control valve and the heating of the electric heater are detected according to the temperature of the fluid
Preferably, the central controller 14 automatically controls the opening of the valve and the electric heater to heat according to the temperatures detected by the th temperature sensor and the second temperature sensor.
If the temperature detected by the second temperature sensor is decreased, the central controller 14 controls the opening degree of the th valve to be increased to increase the amount of gas entering the heat exchanger to increase the amount of heat exchange, and if the temperature detected by the second temperature sensor is increased, the central controller 14 controls the opening degree of the th valve to be decreased to decrease the amount of gas entering the heat exchanger to decrease the amount of heat exchange.
Preferably, the central controller 14 controls the electric heater heating power to be increased while the central controller 14 controls the opening degree of the th valve to be increased, and the central controller 14 controls the electric heater heating power to be decreased while the central controller 14 controls the opening degree of the th valve to be decreased.
Preferably, the th temperature sensor detects a higher temperature than the second temperature sensor, otherwise not the gas heats the thermal storage material, but the thermal storage material heats the gas.
The opening degree of the valve and the change of the heating power of the electric heater are controlled by the detected temperature, so that the heat storage temperature of the heat accumulator can be constant, and the intelligence degree of the system is improved.
Preferably, the gas is exhaust gas or hot air.
preferably, the inlet tube of the gas chamber 7 is connected to the gas inlet channel.
Preferably, the heat storage material 2 is paraffin.
Preferably, the housing 1 comprises a fluid inlet and a fluid outlet, and the thermal storage material 2 is provided with a channel therein communicating the fluid inlet and outlet. Fluid to be heated enters through the fluid inlet, then passes through the thermal storage material to be heated, and then exits through the flow-through outlet.
Preferably, the channel is a pipe.
Preferably, the heat storage capacity of the heat storage material in the regenerator 13 gradually increases from the outer wall of the gas chamber 7 toward the outer wall of the regenerator.
The gradual change of the heat storage capacity of the heat storage material is adopted, steps can be further carried out to improve the heat storage capacity, and uniform heating of the heat storage material can be realized, because the heat storage material is in direct contact with the gas chamber 7 and the condensation end of the heat pipe, the temperature at the position is highest, the heat storage material can be directly heated, and heat can be transferred to the outside of the heat accumulator after the heat storage material is fully stored.
Preferably, the extent of gradual increase in the heat storage capacity of the heat storage material increases gradually from the outer wall of the gas chamber 7 toward the outer wall of the heat accumulator 13, it has been found through experiments and numerical simulations that with this arrangement, the overall heat storage heating uniformity can be further improved .
Preferably, as shown in FIG. 3, the gas chamber 7 has a diameter gradually increasing from the position where the inlet pipe is connected to the lower part, and then gradually decreasing from the position , so as to facilitate the gas flowing in the gas chamber, complete the gas circulation and increase the heat exchange efficiency between the gas and the wall of the gas chamber.
Preferably, as shown in FIG. 1, the inlet duct of the gas chamber 7 extends partially into the housing, the cross-sectional area of the gas chamber 7 being greater than the cross-sectional area of the inlet duct 11, the cross-sectional area of the gas chamber within the housing tapering downwardly in the height direction.
Preferably, the average cross-sectional area of the gas chamber 7 is 15-30 times the cross-sectional area of the inlet pipe 11.
Through the structural design, the heat exchange area of the gas cavity is greatly increased, the length of the heat pipe condensation end 8 wound on the outer wall of the gas cavity is also greatly increased, the heat exchange area is increased, and the heat exchange effect is further improved by steps.
The condensing end is an annular tube wrapped around the outer wall of the gas chamber.
Preferably, the condensing end 8 of the loop heat pipe is wound on the outer wall of the gas chamber 6 more and more densely along the height direction from the upper part to the lower part (the distance between the loop pipes is longer and smaller), the main reason is to concentrate heat on the lower part as much as possible for heat exchange, and the heat exchange amount of the lower part is larger and larger, so that the heated water flows upwards, the sufficient convection of the water is promoted, and the heat exchange effect is enhanced.
, the winding density of the condensation end 8 of the loop heat pipe on the outer wall of the gas chamber 6 increases along the height direction from the upper part to the lower part, and experiments show that the heat exchange effect can be improved by .
In the research, it is found that the heat source fluid in the heat accumulator can only be gas, because if the heat source fluid is liquid, the liquid can be completely accumulated in the chamber 7 and is difficult to discharge, and because the cross-sectional area of the chamber 7 is much larger than that of the inlet pipeline, the existence of excessive liquid can cause that the chamber 7 cannot be well fixed on the shell due to gravity, so that the fixing difficulty is increased, and therefore, the heat source in the heat accumulator can only be gas.
Preferably, as shown in fig. 1, the bottom 3 and the top of the gas chamber 7 are of planar configuration.
Preferably, a plurality of gas chambers 7 are arranged in the housing 1, and the gas inlet channels 5 of the plurality of gas chambers are in a parallel structure.
Preferably, the gas outlet channels 5 of the plurality of gas chambers are in a parallel configuration.
Preferably, the gas chamber 7 is suspended in the housing 1, and the bottom is away from the bottom of the housing 1. by this design, the bottom can be sufficiently heat-exchanged with the heat storage material.
Preferably, the heat storage capacity of the heat storage material in the portion above the top and the portion below the bottom of the gas chamber 7 in the housing is greater than the heat storage capacity of the material between the top and the bottom. Through so setting up, can make whole heat accumulation heating even, improve product life. The main reason is that the temperature of the middle part is highest, the heat storage material can be directly heated, and after the heat storage material is fully stored, the heat can be transferred to the upper part and the lower part. Through the change of the heat storage capacity of the heat storage material of the heat accumulator, the heat storage material in the middle part can immediately transfer heat to the lower part of the upper part after reaching heat storage saturation, and the heat storage material in other parts can also store heat. Like this, the heat can both fully be stored in the different positions in the heat accumulator, avoids some local overheat, and local heat absorption is not enough, guarantees the even of whole heat accumulation, makes like this that the fluid can the even heating through the heat accumulator heating process, avoids local overheat or local heating not enough. Through setting up like this, can be that whole heat accumulation heating is even, improves product life.
Preferably, the heat storage capacity of the heat storage material in the portion below the bottom of the gas chamber 7 becomes stronger and stronger downward in the height direction.
Step is selected, and the stronger amplitude is increased continuously.
Preferably, the heat storage capacity of the heat storage material in the portion above the top of the gas chamber 7 becomes stronger upward in the height direction.
Step is selected, and the stronger amplitude is increased continuously.
The main reason is that the heat storage capacity of the heat storage material is changed, and the heat storage material can store heat and heat uniformly as a whole and prolong the service life of a product.
Preferably, the evaporation end 6 of the loop heat pipe is mounted on the gas chamber inlet pipe, and the condensation end 8 of the loop heat pipe is wound outside the gas chamber and in direct contact with the external heat storage material. The loop heat pipe condenser is wound outside the gas chamber and fully contacts with an external heat storage material, so that the heat dissipation of gas at the evaporation end of the heat pipe is increased, and the cooling efficiency is improved.
Preferably, at least part of the evaporation end 6 is provided with a capillary core 13, and the capillary force provides power for the working medium to flow back and circulate, and simultaneously, the amount of the working medium flowing back meets the requirement of heat transfer, thereby realizing the function of the antigravity heat pipe.
By arranging the capillary core 13, the capillary core 13 is arranged at the evaporation end, so that the ascending section 6 of the evaporation end naturally generates flow resistance, and the steam generated at the evaporation end naturally flows to the evaporation end with low resistance and flows to the condensation end pipeline 9, thereby forming the antigravity heat pipe.
Preferably, the capillary wick 13 is only disposed in the rising section of the evaporation end, preferably in the portion of the rising section, as shown in fig. 3 and 7, for example.
Preferably, at least portions of the gas outlet channel 4 are provided in the inlet duct of the gas chamber, the cold gas of the gas outlet pre-cooling the hot gas of the gas inlet, by heat exchange of the outlet gas with the inlet gas, a heat exchange effect is achieved , increasing the condensation efficiency of the water.
Preferably, as shown in fig. 4, the evaporation end is disposed at the inlet tube of the gas chamber, the rising section of the evaporation end is filled with the capillary wick 13 to provide a sufficient capillary force, the center of the capillary wick 13 is provided with the pipeline 10 from the condensation end to the evaporation end, by disposing the pipeline 10 (without the capillary wick), the fluid resistance of the pipeline can be reduced, the working medium flows back more smoothly, the heat transfer capability in the anti-gravity state is improved, and the outer wall surface of the rising section of the evaporation end is provided with the longitudinal vertical fins 12 in a surrounding manner, so that the heat exchange area is increased, and the heat exchange efficiency with the gas is improved.
The pipeline 10 is a gas or liquid pipeline, flexible arrangements are realized, the pipe diameter is small, and the pipeline is easy to bend, the principle of the loop heat pipe is that if the evaporator side and the pipeline 10 are steam pipelines, the principle is that the evaporator is heated and internal working media are evaporated, steam enters the pipeline 10 along the upper outlet of the evaporator, then flows to a lower surrounding pipeline and contacts with heat storage materials to start condensation, and after the steam is completely condensed, the steam returns to the evaporator under the action of capillary force of the capillary core of the evaporator, so that the circulation of the working media is realized.
Preferably, the tube 10 communicates with the capillary wick 13. Through the communication, the fluid communication between the capillary wick 13 and the pipeline 10 can be realized, so that if a large pressure is generated due to heat absorption during the liquid ascending through the capillary wick, for example, even bubbles can occur, the pressure of the evaporation section can be equalized through the pipeline 10, and thus the equalization of the pressure is ensured.
It is further preferred that the wick 13 extends to the condensation end to directly draw up the liquid at the condensation end increase the circulation capacity of the antigravity heat pipe.
Preferably, the capillary cores are distributed along the height direction, as shown in fig. 3, step is preferably, the capillary force of the capillary cores is gradually increased along the height descending direction, the capillary force is larger as the capillary cores are closer to the condensation end, experiments show that by adopting the mode, the suction force to the liquid can be increased by step , the suction force can be increased by more than 20% at the same cost, and therefore the heat exchange effect is improved.
Through further analysis, the primary reason may be that as the capillary force near the condensation end is increased, the liquid at the condensation end can be rapidly absorbed into the capillary wick, and the liquid continuously flows towards the evaporation end.
, the capillary force of the capillary wick is increased gradually along the height descending direction, and experiments show that in this way, the suction force to the liquid can be increased , and the suction force can be increased about 8% at the same cost, so that the heat exchange effect is improved.
Preferably, the pipeline is formed by a through hole formed in the middle of the capillary core.
Preferably, as shown in fig. 7, the pipe diameter of the heat pipe position where the capillary wick is provided is larger than the pipe diameter of the heat pipe position where the capillary wick is not provided.
It is further preferred that the change in pipe diameter between the pipe at the heat pipe location where the capillary wick is located and the pipe at the heat pipe location where the capillary wick is not located is a continuous change as shown in fig. 7. step is preferably a linear change.the pipe at the large pipe diameter location and the pipe through which the small pipe passes are connected at the junction by a constriction.
Preferably, the gas outlet channel 4 is arranged between and in contact with two adjacent vertical fins 12. Through so setting up, can reduce the mechanism that sets up independent support gas outlet passage 4 for compact structure, outlet passage's cold gas accessible pipeline and fin heat transfer keep the degree of coldness of fin, reinforcing heat transfer effect.
Preferably, the evaporation end flow direction condensation end flow direction evaporation end flow direction condensation end pipe 9 is arranged between and in contact with two adjacent vertical fins. Through so setting up, can reduce the mechanism that sets up independent support gas outlet passage 4 for compact structure, the steam accessible pipeline in the pipeline is short for a short time a small amount of heat transfer to the fin, reduces the whole thermal resistance of system, avoids producing in the evaporimeter overheated under the antigravity condition on ground, slows down the temperature shock phenomenon in the heat pipe start-up process.
, the evaporation end flow direction is preferably closer to the outer wall of the evaporation end pipe than the gas outlet channel 4 is to the condensation end pipe 9, so that the above two heat transfer processes can be simultaneously realized and the corresponding effect can be achieved.
, the diameter of the evaporation end to condensation end pipe 9 is preferably smaller than the diameter of the gas outlet channel 4.
Preferably, the steam generated by absorbing heat at the evaporation end flows to the condensation end pipeline 9 through the plurality of evaporation ends and enters the condensation end, step enhances heat transfer, and the volume is increased because the fluid in the heat pipe absorbs heat and evaporates, step relieves pressure and improves heat exchange effect by arranging the plurality of evaporation ends to flow to the condensation end pipeline 9.
, the vertical fin preferably extends through the center of the inlet tube of the gas chamber, and the evaporation end riser tube is concentric with the inlet tube of the gas chamber.
Preferably, the number of the evaporation end flow direction condensation end pipelines 9 is multiple, and the distance between the circle center of the multiple evaporation end flow direction condensation end pipelines 9 and the pipeline at the ascending section of the evaporation end is the same.
preferably, evaporation end to condensation end pipelines 9 are arranged between every two adjacent vertical fins 12, and the evaporation end to condensation end pipelines 9 are in a parallel structure.
Preferably, the number of the gas outlet channels 4 is multiple, the distance between the circle center of the multiple gas outlet channels 4 and the ascending section pipeline of the evaporation end is the same, so that the temperature distribution among the fins is more uniform, and the heat exchange effect is more obvious, is further preferred, gas outlet channels 4 are arranged between every two adjacent vertical fins 12, and the gas outlet channels 4 are in a parallel structure.
, preferably, there are a plurality of evaporation end to condensation end pipelines 9, a plurality of gas outlet channels 4, and the number of evaporation end to condensation end pipelines 9 is equal to the number of gas outlet channels 4.
, preferably, the evaporation end flow direction condensation end pipeline 9 is arranged between adjacent gas outlet channels 4, the gas outlet channels 4 flow between adjacent evaporation end flow direction condensation end pipelines 9, , preferably, the evaporation end flow direction condensation end pipeline 9 center is at the same distance as the adjacent gas outlet channel 4 center, the gas outlet channel 4 is at the same distance as the adjacent gas evaporation end flow direction condensation end pipeline 9 center, i.e., the evaporation end flow direction condensation end pipeline 9 is arranged in the middle of the adjacent gas outlet channel 4, the gas outlet channel 4 flows to the middle of the adjacent evaporation end flow direction condensation end pipeline 9, i.e., as shown in fig. 4, the center of the evaporation end flow direction condensation end pipeline 9 is at the third connecting line between the center of the evaporation end 6 and the center of the evaporation end, the center of the adjacent gas outlet channel 4 and the center of the evaporation end 6 form the third connecting line, the connecting line is formed between the connecting line and the second connecting line is equal to the second connecting line formed between the third connecting line, the center of the evaporation end flow direction condensation end flow direction, the fourth connecting line and the fourth connecting line forming the included angle between the center of the evaporation end flow direction condensation end connecting line 9 and the fourth connecting line, and the fourth connecting line forming the evaporation end connecting line forming the same angle between the center of the evaporation end flow direction connecting line forming the fourth line forming the same distance.
Through the arrangement, the evaporation end can be ensured to flow to the condensation end pipeline 9 and the gas outlet channel 4 to absorb heat uniformly to the inlet gas, and local heating unevenness is avoided. The gas outlet channel 4 can continuously participate in heat exchange after absorbing heat, and the heat is transferred to the evaporation end through the fins.
In numerical simulation and experiments, it is found that the difference between the pipe diameters of the gas outlet channel 4 and the evaporation end flowing to the condensation end pipeline 9 cannot be too large or too small, and if the difference is too large, the distance between the gas outlet channel 4 and the evaporation end flowing to the condensation end pipeline 9 is too far, so that the gas heat exchange between the channel 4 and the evaporation end flowing to the condensation end pipeline 9 is poor, the overall heat exchange is not uniform, and if the difference is too small, the distance between the gas outlet channel 4 and the evaporation end flowing to the condensation end pipeline 9 is too close, so that the gas near the outer wall of the inlet pipe 11 and/or the gas near the outer wall of the evaporation end 6 are poor, and the gas heat exchange in the overall inlet pipe 11 is not uniform; the same reason, the contained angle between adjacent fin 12 can not be too big, can lead to the distribution fin few too big, the heat transfer effect is too good, lead to gas outlet passageway 4 and evaporating end flow direction condensing end pipeline 9 quantity of distribution too little simultaneously, lead to the heat transfer inhomogeneous and the heat transfer effect is not good, on the same principle, the contained angle between adjacent fin 12 can not be too little, lead to the fin distribution too closely too little, the flow resistance greatly increases, and gas outlet passageway 4 and evaporating end flow direction condensing end pipeline 9's pipe diameter differs not greatly, but their heat transfer capacity of equal area is very different, therefore the heat transfer is inhomogeneous under this kind of condition, lead to the heat transfer effect not good. It is therefore necessary to determine the optimum dimensional relationship by extensive numerical simulations and experiments thereof.
The radius of the gas outlet channel 4 is R, the radius of the evaporating end flowing to the condensing end pipeline 9 is R, the included angle between adjacent fins is A, and the following requirements are met:
Sin(A)＝a*(r/R)-b*(r/R)2-c；
a, b, c are parameters,
wherein 1.23< a <1.24,0.225< b <0.235, 0.0185< c < 0.0195;
14°<A<30°；
0.24< R/R <0.5, preferably 0.26< R/R <0.38, further .
Further , a is preferably 1.235, b is preferably 0.231, and c is preferably 0.0190.
The above empirical formula is obtained through a large number of numerical simulations and experiments, and has higher accuracy than the previous logarithmic function, and the error is basically within 2.4 after experimental verification.
Further , a is preferably 1.235, b is preferably 0.231, and c is preferably 0.0190.
Preferably, said 3< R <10 mm; 1.5< r <4.0 mm;
, preferably, the pipe diameter of the heat pipe at the position where the capillary core is arranged is 30-40mm, and preferably is 32 mm;
, preferably, the pipe diameter of the heat pipe without the capillary core is 5.0-6.4 mm;
, preferably, the pipe diameter of the pipeline from the condensation end to the evaporation end is 5.0-6.4 mm;
, the tube diameter of the inlet tube 11 is preferably 80-200mm, preferably 120-150 mm;
, the length of the fin in the vertical direction is 780-1500mm, preferably 1200mm, the length of the longitudinal extension of the fin accounts for 95% of the difference between the outer diameter of the evaporation end 6 and the inner diameter of the gas outlet channel 4, the overall heat exchange capacity of the fin is obviously improved under the length, the heat exchange coefficient is also in a proper range, and the influence on the damage effect of the boundary layer and the fluid flow effect is relatively small
After gas is filtered, the filtered gas is sucked into a gas cavity through an induced draft fan, external hot gas exchanges heat with relatively low-temperature gas which is exhausted outdoors in the gas inlet channel 5 and the gas outlet channel, the heat of the gas with low temperature is transferred to an evaporation end through fins after heat exchange, the outer wall of metal has a heat conduction function, the gas and the low-temperature gas exchange together complete gas heat exchange, after the gas enters the gas cavity, the hot gas slowly passes through a fin channel of a loop heat pipe evaporator to complete heat exchange with a medium in the loop heat pipe, the temperature of the gas is obviously reduced, the residual gas enters the gas cavity 7 to exchange heat with external heat storage materials through the outer wall of the cavity metal, -step heat exchange is carried out along with the gas, at the moment, a main cold source is provided by the loop heat pipe, the evaporation end 6 of the loop heat pipe absorbs the heat of the hot gas, the liquid working medium is evaporated into a gas state, then the heat is conducted to the external heat storage materials through a loop heat pipe condensation end 8 wound outside the gas cavity.
Preferably, the loop heat pipe capillary wick is prepared by using a powder metallurgy method. Before starting, the capillary core, the supplement cavity and the liquid conveying pipe of the evaporator of the loop heat pipe are filled with working medium, and the steam channel, the condenser and the steam pipe are in two-phase states.
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 (5)
- The loop heat pipe heat accumulator comprises a shell, a gas inlet channel, a gas outlet channel, a loop heat pipe and a gas chamber, wherein heat accumulation materials are arranged in the shell, the heat pipe comprises an evaporation end and a condensation end, the evaporation end is positioned at the upper part of the condensation end, a capillary core is arranged in a pipeline leading from the condensation end to the evaporation end, and the condensation end is arranged on the outer wall of the gas chamber;an electric heater for auxiliary heating is arranged in the shell; a second temperature sensor is arranged in the heat accumulator and used for detecting the temperature of a heat storage material in the heat accumulator; the second temperature sensor is in data connection with the central controller;if the temperature detected by the second temperature sensor is lower than constant value, the central controller controls the electric heater to heat, and if the temperature detected by the second temperature sensor is higher than constant value, the central controller stops the electric heater to heat.
- 2. The regenerator as claimed in claim 1, in which parts of the capillary wick are arranged partially or completely at the evaporation end, the evaporation end comprises a riser tube, at least parts of the riser tube are provided with the capillary wick to realize the function of a antigravity heat pipe, the outer wall surface of the evaporation end is provided with longitudinal vertical fins around, an air outlet channel is arranged between and in contact with two adjacent vertical fins, a downcomer of the heat pipe is arranged between and in contact with two adjacent vertical fins, and at least parts of the rising section and the falling section are arranged in the air inlet channel.
- 3. The regenerator as claimed in claim 1, in which the fluid inlet is located at the lower side of the shell and the fluid outlet is located at the upper side of the shell, the inlet pipe for the gas chamber extending partially into the shell, the cross-sectional area of the gas chamber within the shell tapering downwardly in the height direction.
- 4. The heat accumulator as set forth in claim 3, characterized in that a fluid passage is provided in said heat accumulating material, a fluid flows in said fluid passage, said heat accumulating material transfers heat to said fluid, said fluid is a liquid medicine, and said heat accumulator is kinds of heat accumulators functioning to heat said liquid medicine, said liquid medicine is used for fumigation and washing of wounds.
- The loop heat pipe heat accumulator comprises a shell, a gas inlet channel, a gas outlet channel, a loop heat pipe and a gas chamber, wherein heat accumulation materials are arranged in the shell, the heat pipe comprises an evaporation end and a condensation end, the evaporation end is positioned at the upper part of the condensation end, a capillary core is arranged in a pipeline leading from the condensation end to the evaporation end, the condensation end is arranged on the outer wall of the gas chamber, the gas chamber is arranged in the shell, the loop heat pipe is a counter-gravity heat pipe, an outlet of the gas inlet channel and an inlet of the gas outlet channel are communicated with the gas chamber, the gas exchanges heat with the evaporation end in the process of being introduced into the gas chamber from the gas inlet channel, and the condensation end conducts heat to the heat accumulation materials in the shell.
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| CN201810289462.8A CN109539838B (en) | 2018-04-03 | 2018-04-03 | Intelligent control liquid medicine heat accumulator capable of realizing automatic heat accumulation according to temperature |
| CN201911032936.1A CN110736374B (en) | 2018-04-03 | 2018-04-03 | Heat accumulator capable of automatically heating according to temperature of heat storage material |
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| CN201810289462.8A Expired - Fee Related CN109539838B (en) | 2018-04-03 | 2018-04-03 | Intelligent control liquid medicine heat accumulator capable of realizing automatic heat accumulation according to temperature |
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| CN201810289462.8A Expired - Fee Related CN109539838B (en) | 2018-04-03 | 2018-04-03 | Intelligent control liquid medicine heat accumulator capable of realizing automatic heat accumulation according to temperature |
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| CN112964100B (en) * | 2020-03-04 | 2022-03-08 | 山东大学 | Loop heat pipe heat exchanger capable of switching heat sources according to temperature difference |
| CN112964098B (en) * | 2020-03-04 | 2022-03-04 | 山东大学 | Loop heat pipe heat exchanger capable of switching heat sources according to speed difference |
| CN113815908B (en) * | 2020-11-05 | 2024-03-08 | 山东大学 | Intelligent heat-preserving loop heat pipe and heat control system thereof |
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| CN110736374B (en) | 2021-10-08 |
| CN110736373B (en) | 2021-11-30 |
| CN110736373A (en) | 2020-01-31 |
| CN109539838B (en) | 2020-02-11 |
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