CN116399147B - Sleeve type heat pipe phase change heat accumulator - Google Patents
Sleeve type heat pipe phase change heat accumulator Download PDFInfo
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- CN116399147B CN116399147B CN202310509137.9A CN202310509137A CN116399147B CN 116399147 B CN116399147 B CN 116399147B CN 202310509137 A CN202310509137 A CN 202310509137A CN 116399147 B CN116399147 B CN 116399147B
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- 230000008859 change Effects 0.000 title claims abstract description 14
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 112
- 239000012782 phase change material Substances 0.000 claims abstract description 107
- 239000002918 waste heat Substances 0.000 claims abstract description 97
- 238000009825 accumulation Methods 0.000 claims abstract description 40
- 239000012530 fluid Substances 0.000 claims abstract description 37
- 238000005338 heat storage Methods 0.000 claims description 72
- 230000001360 synchronised effect Effects 0.000 claims description 28
- 238000009833 condensation Methods 0.000 claims description 24
- 230000005494 condensation Effects 0.000 claims description 24
- 230000008020 evaporation Effects 0.000 claims description 24
- 238000001704 evaporation Methods 0.000 claims description 24
- 238000000034 method Methods 0.000 claims description 15
- 238000010438 heat treatment Methods 0.000 claims description 13
- CSCPPACGZOOCGX-UHFFFAOYSA-N Acetone Chemical group CC(C)=O CSCPPACGZOOCGX-UHFFFAOYSA-N 0.000 claims description 8
- 238000012546 transfer Methods 0.000 claims description 6
- 239000008367 deionised water Substances 0.000 claims description 4
- 229910021641 deionized water Inorganic materials 0.000 claims description 4
- 238000005485 electric heating Methods 0.000 claims description 4
- 230000005484 gravity Effects 0.000 abstract description 9
- 230000008569 process Effects 0.000 description 10
- 238000005516 engineering process Methods 0.000 description 7
- 238000011084 recovery Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 239000002440 industrial waste Substances 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 239000012188 paraffin wax Substances 0.000 description 3
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 239000010949 copper Substances 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000003860 storage Methods 0.000 description 2
- 239000011232 storage material Substances 0.000 description 2
- 230000003245 working effect Effects 0.000 description 2
- 101000927062 Haematobia irritans exigua Aquaporin Proteins 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 239000002803 fossil fuel Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000009776 industrial production Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000008018 melting Effects 0.000 description 1
- 238000002844 melting Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- VWDWKYIASSYTQR-UHFFFAOYSA-N sodium nitrate Inorganic materials [Na+].[O-][N+]([O-])=O VWDWKYIASSYTQR-UHFFFAOYSA-N 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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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
-
- 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
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/14—Thermal energy storage
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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)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
The invention provides a sleeve type heat pipe phase change heat accumulator, which comprises a cold water flow passage, a waste heat flow passage, a phase change material, an auxiliary heater and a Z-shaped heat pipe, wherein the Z-shaped heat pipe comprises three types, namely a heat accumulation heat release heat pipe, a heat release heat pipe and a heat accumulation heat pipe, the cold water flow passage is arranged on the outer side, the waste heat flow passage is arranged on the inner side, the phase change material is arranged between the cold water flow passage and the waste heat flow passage, the auxiliary heater is arranged in the phase change material, the heat accumulation heat release heat pipe penetrates through the cold water flow passage, the waste heat flow passage and the phase change material, the heat release heat pipe is arranged in the cold water flow passage and the phase change material, and the heat accumulation heat pipe is arranged in the waste heat flow passage and the phase change material. According to the invention, the phase change material is arranged between cold and hot fluid to store heat, and the energy is stored and released through the Z-shaped gravity heat pipe, so that the energy utilization rate is improved.
Description
Technical Field
The invention relates to the field of heat storage and heat exchange, in particular to the field of industrial waste heat recovery and utilization, and particularly relates to a sleeve type heat pipe phase change heat accumulator.
Background
With the continuous use of fossil fuels by various industries, mainly industry, energy shortage and environmental problems are increasingly prominent. Compared with highly developed countries, the energy utilization rate of various industries in China is low in the production process, the problem of energy waste is serious, and the waste heat recovery technology is used for recovering and storing waste heat in the industrial production process and releasing heat when the waste heat is required. Therefore, the industrial waste heat recovery and utilization has promotion effect on solving the problems of energy shortage, environmental pollution and the like.
At present, the waste heat recovery equipment generally takes a traditional heat exchanger as a main component, water is used as a working medium for sensible heat exchange, and the output of industrial waste heat is discontinuous in time, so that the general waste heat recovery equipment needs to be matched with a large-volume water tank to store heat. The sensible heat storage technology is a low-energy-density heat storage technology, the occupied area of equipment is large, meanwhile, all the equipment are connected through pipelines, and the system integration is poor.
The heat pipe is used as a heat transfer element with high heat conductivity, the heat conductivity coefficient of the heat pipe is far higher than that of any one of the known metal materials, and the gravity heat pipe is used as a self-driven heat pipe which can run only by gravity, so that the gravity heat pipe has a simple structure and is easy to manufacture. The phase change material has a specific phase change temperature, when the temperature crosses the phase change temperature, the state of the phase change material changes, and the process can absorb or release a large amount of heat, so that the phase change material is widely applied to the heat storage technology, and the latent heat storage technology has the advantages of high energy density, small volume of heat storage equipment and the like. At present, the gravity assisted heat pipe and the phase change material are less in coupling heat storage and release technology, so that the gravity assisted heat pipe and the phase change material have a great prospect in the field of waste heat recovery and storage.
Disclosure of Invention
The invention aims to solve the problems and provides a sleeve type heat pipe phase change heat accumulator applied to the field of waste heat recovery and a working method thereof. The phase change material is placed between cold and hot fluids to store heat, the energy is stored and released through the Z-shaped gravity heat pipe, the energy utilization rate is improved, and the phase change material has important significance on the double-carbon targets in China and has wide application prospect.
In order to achieve the above object, the technical scheme of the present invention is as follows:
the utility model provides a sleeve type heat pipe phase transition heat accumulator, the heat accumulator includes cold water runner, waste heat runner, phase change material, auxiliary heater and "Z" shape heat pipe, Z "shape heat pipe includes three types, is heat accumulation exothermic heat pipe, exothermic heat pipe and heat accumulation heat pipe respectively, and cold water runner is arranged in the outside, and the waste heat runner is arranged in the inboard, and phase change material is arranged between cold water runner and waste heat runner, is equipped with auxiliary heater in the phase change material, heat accumulation exothermic heat pipe runs through between cold water runner, waste heat runner and phase change material, and exothermic heat pipe is arranged in cold water runner and phase change material, and heat accumulation heat pipe is arranged in waste heat runner and phase change material.
Preferably, the Z-shaped heat pipe comprises a vertical evaporation section positioned at the lower part, a vertical condensation section positioned at the upper part and an inclined section connected with the evaporation section and the condensation section, wherein the evaporation section of the heat accumulation and release heat pipe is arranged in the waste heat flow channel, the condensation section is arranged in the cold water flow channel, and the inclined section is arranged in the phase change material; the exothermic heat pipe evaporation section is arranged in the phase change material, and the condensation section is arranged in the cold water flow passage; the heat accumulation heat pipe evaporation section is arranged in the waste heat runner, and the condensation section is arranged in the phase change material.
Preferably, when the waste heat temperature is 50-100 ℃, the heat is as followsR134-a can be selected as the tube working medium, and paraffin with corresponding purity can be selected as the phase change material; when the temperature of the waste heat is 100-150 ℃, the working medium of the heat pipe can be acetone, and the phase change material can be KAl (SO 4) 2.12H2O; when the temperature of the waste heat is 150-200 ℃, the working medium of the heat pipe can be deionized water, and the phase change material can be KNO 3 -NaNO 2 -NaNO 3 The mass ratio was 53:40:7.
Preferably, the evaporation section of the heat-releasing heat pipe is thermally connected to the auxiliary heater.
Preferably, the cold water flow channel, the waste heat flow channel and the phase change material are arranged in concentric circles.
Preferably, the auxiliary heater is an electric heater.
Preferably, a heat exchange method of a regenerator as described above, four different modes of operation can be performed:
synchronous heat storage and release mode: when waste heat fluid exists and needs to heat cold water, the waste heat fluid flows through a waste heat flow channel, the synchronous heat storage and release Z-shaped heat pipe and the heat storage Z-shaped heat pipe start to work, at the moment, the cold water flows through the cold water flow channel and the condensation section of the synchronous heat storage and release Z-shaped heat pipe to perform forced convection heat exchange, and the heat storage Z-shaped heat pipe has higher thermal resistance with the phase change material and lower heat transfer performance than the synchronous heat storage and release Z-shaped heat pipe, at the moment, most heat of the waste heat fluid is used for heating the cold water, and a small part of heat is absorbed by the phase change material and stored in a latent heat form;
and (3) a heat storage mode: when the waste heat fluid exists and the cold water does not need to be heated, the waste heat fluid flows through the waste heat flow channel, the synchronous heat storage and release Z-shaped heat pipe and the heat storage Z-shaped heat pipe start to work, at the moment, no cold water flows through the cold water flow channel to cool the synchronous heat storage and release Z-shaped heat pipe, and the heat absorbed by the heat pipe can only be absorbed by the phase change material and is stored in a latent heat form;
exothermic mode: when there is no waste heat fluid but there is a need to heat the cold water, and the phase change material has previously accumulated enough heat. At the moment, the exothermic Z-shaped heat pipe starts to work, the exothermic Z-shaped heat pipe absorbs heat in the phase-change material, cold water flows through the cold water flow channel to perform forced convection heat exchange with the exothermic Z-shaped heat pipe, and the heat is transferred into the cold water from the phase-change material;
auxiliary electric heating mode: when there is no waste heat fluid but there is a need to heat the cold water, and the phase change material does not accumulate sufficient heat. At this time, the auxiliary electric heater is turned on, the heat release Z-shaped heat pipe starts to work, the heat release Z-shaped heat pipe absorbs the heat provided by the electric heater, cold water flows through the cold water flow channel to perform forced convection heat exchange with the heat release Z-shaped heat pipe, and the heat is transferred into the cold water by the phase change material.
Compared with the prior art, the invention has the following advantages:
(1) The prior art heat accumulator generally uses a heat exchange coil to accumulate and release heat, has lower heat conductivity coefficient and single working mode. The heat conductivity coefficient of the heat pipe is tens or even hundreds times that of metal, and the heat pipe type heat accumulator can rapidly realize heat storage and release. The sleeve type heat pipe phase change heat accumulator can synchronously perform a plurality of working modes. The heat accumulation and heat release functions can be realized at the same time, and the energy utilization rate is improved.
(2) The heat accumulator in the prior art needs to accumulate heat and release heat in the operation process, and the heat pipe is used as a heat transfer element to realize a synchronous heat accumulation and release mode.
(3) In the prior art, a heat source can only be positioned below a heat storage material and cold water for exerting the performance of a heat pipe, the sleeve type heat accumulator can be used in vertical upward or downward flow on the premise of not changing the performance of the heat accumulator, and the positions of the heat source and the cold water are relatively free.
(4) In the heat release process of the heat pipe type phase change heat accumulator in the prior art, the heat pipe cannot exert the maximum heat conduction performance because the phase change material is low in energy storage quality and is positioned in the middle section of the heat pipe, and the heat release effect is poor. The invention is provided with three Z-shaped heat pipes, so that the heat accumulator can exert maximum performance in the heat accumulation and heat release processes.
(5) The electric heater is arranged around the heat pipe, and in the auxiliary heating mode, the heat pipe can absorb heat at the highest speed to release heat outwards. When the heat accumulator does not need to release heat, the electric heater is started, and the phase-change material can absorb heat to realize heat accumulation.
(6) The invention is a sleeve type phase change heat accumulator, which can be arranged along a heat accumulation pipeline and occupies a small area. The requirements on the field are small, the ground is not required to be arranged, and the device can be arranged in the air.
Drawings
Fig. 1 is a schematic cross-sectional view of a sleeve-type heat pipe phase change thermal storage of the present invention.
FIG. 2 is a schematic view of section A-A of FIG. 1 in accordance with the present invention.
FIG. 3 is a schematic view of the internal structure of the heat source runner of section B-B in FIG. 1 according to the present invention.
FIG. 4 is a schematic view of a heat pipe add-on fin according to the present invention.
In the figure:
1. cold water flow passage, 2, waste heat flow passage, 3, phase change material, 4, auxiliary heater, 5, "Z" shape heat pipe, 5a, heat accumulation exothermic heat pipe, 5b, exothermic heat pipe, 5c, heat accumulation heat pipe, 6a, inclined section fin structure, 6b, vertical section fin structure.
Detailed Description
The following describes the embodiments of the present invention in detail with reference to the drawings.
Herein, "/" refers to division, "×", "x" refers to multiplication, unless otherwise specified.
As shown in fig. 1-3, the heat accumulator comprises a cold water flow channel 1, a waste heat flow channel 2, a phase change material 3, an auxiliary heater 4 and a Z-shaped heat pipe 5, wherein the Z-shaped heat pipe 5 comprises three types, namely a heat accumulating and releasing heat pipe 5a, a heat releasing heat pipe 5b and a heat accumulating heat pipe 5c, the cold water flow channel 1 is arranged at the outer side, the waste heat flow channel 2 is arranged at the inner side, the phase change material 3 is arranged between the cold water flow channel 1 and the waste heat flow channel 2, the auxiliary heater 4 is arranged in the phase change material 3, the heat accumulating and releasing heat pipe 5a penetrates through the cold water flow channel 1, the waste heat flow channel 2 and the phase change material 3, the heat releasing heat pipe 5b is arranged in the cold water flow channel 1 and the phase change material 3, and the heat accumulating heat pipe 5c is arranged in the waste heat flow channel 2 and the phase change material 3.
According to the invention, the phase change material is arranged between cold and hot fluid to store heat, and the energy is stored and released through the Z-shaped gravity heat pipe, so that the heat storage and release functions can be realized at the same time, and the energy utilization rate is improved.
The auxiliary heater is arranged in the heat storage material, so that heat can be timely supplemented, or the heat release function can be realized by simply relying on the auxiliary heater.
Preferably, the Z-shaped heat pipe 5 comprises a vertical evaporation section positioned at the lower part, a vertical condensation section positioned at the upper part and an inclined section connecting the evaporation section and the condensation section, wherein the evaporation section of the heat accumulating and releasing heat pipe 5a is arranged in the waste heat flow channel 2, the condensation section is arranged in the cold water flow channel 1, and the inclined section is arranged in the phase change material 3; the evaporation section of the heat release heat pipe 5b is arranged in the phase change material 3, and the condensation section is arranged in the cold water flow passage 1; the evaporation section of the heat storage heat pipe 5c is arranged in the waste heat flow channel 2, and the condensation section is arranged in the phase change material 3. According to the invention, through reasonably arranging the Z-shaped heat pipes of various types, the heat storage and release functions are realized, the heat storage and release functions are simultaneously carried out, and the energy utilization rate is improved.
Preferably, when the temperature of the waste heat is 50-100 ℃, R134-a can be selected as the working medium of the heat pipe, and paraffin with corresponding purity can be selected as the phase change material 3; when the temperature of the waste heat is 100-150 ℃, the working medium of the heat pipe can be acetone, and the phase change material 3 can be KAl (SO 4) 2.12H2O; when the temperature of the waste heat is 150-200 ℃, the working medium of the heat pipe can be deionized water, and the phase change material 3 can be KNO 3 -NaNO 2 -NaNO 3 (53:40:7) (mass ratio). According to the invention, proper heat pipe working medium and phase change material are selected according to the preheating temperature, so that the optimal heat exchange effect is realized.
Preferably, the evaporator end of the heat-releasing heat pipe is thermally connected to the auxiliary heater 4. So as to realize the auxiliary heating and heat releasing functions.
The inclined section of the heat accumulation and release heat pipe 5a is thermally connected with the auxiliary heater 4. By heating the inclined section, an external heat release function is realized.
Preferably, the cold water flow channel 1, the waste heat flow channel 2 and the phase change material 3 are arranged in concentric circles. The concentric circles can effectively save space, and more Z-shaped heat pipes are arranged to increase heat storage and release performance.
Preferably, the auxiliary heater 4 is an electric heater.
Preferably, as shown in fig. 1, the "Z" -shaped heat pipe 5 extends outward from the evaporation section to the condensation section along the center of the radial direction of the concentric circles.
The heat pipes are arranged in a central symmetry manner, so that the heat of the waste heat fluid can be absorbed more uniformly, and the heat can be released into cold water uniformly. The angled configuration of the outwardly extending portions does not affect the performance of the heat pipe, but can alter the relative position of the cold and hot source fluid and contact more phase change material over a limited height.
Preferably, as shown in fig. 2, the heat storage and release heat pipes 5a and 5b are arranged at intervals in the height direction. Preferably, referring to fig. 1, the horizontal cross section of the regenerator is viewed with the extension line of the connection line of the heat accumulating and releasing heat pipe 5a and the heat releasing heat pipe 5b passing through the center of the concentric circle.
In the synchronous heat accumulation and release process of the heat accumulator, the heat accumulation and release heat pipes have optimal working effects, and in the heat release process of the heat accumulator, the heat release heat pipes have optimal working performance, and the two heat pipes are axially arranged at intervals, so that the heat accumulator can exert maximum performance in different working modes.
Preferably, as shown in fig. 3, the heat storage and release heat pipes 5a are arranged at intervals from the heat storage heat pipes 5c in the height direction. Preferably, referring to fig. 1, the cross section of the heat accumulator is viewed, and the extension line of the connection line of the heat accumulation exothermic heat pipe 5a and the heat accumulation heat pipe 5c passes through the center of the concentric circle.
In the synchronous heat accumulation and release process of the heat accumulator, the heat accumulation and release heat pipes have optimal working effect, and in the heat release process of the heat accumulator, the heat accumulation and release heat pipes and the heat accumulation heat pipes work normally, and the two heat pipes are arranged at intervals in the axial direction, so that the heat accumulator can exert the maximum performance under different working modes.
Preferably, referring to fig. 1, the extension lines of the evaporation section and the condensation section of the heat storage and release heat pipe 5a pass through the center of the concentric circle when the cross section of the heat storage device is observed. The arrangement structure can increase the arrangement quantity of the heat accumulating and releasing heat pipes, and uniformly absorb and release heat. The heat accumulating and releasing heat pipe is in the same plane, and the bending processing technology is simple and can be formed at one time.
As a preference, referring to fig. 1, the "Z" -shaped heat pipes 5 are arranged around concentric circles, wherein each heat storage and release heat pipe 5a is collocated with one heat release heat pipe 5b or heat storage heat pipe 5c in the radial direction, wherein the heat release heat pipes 5b and the heat storage heat pipes 5c are arranged at intervals. The heat accumulator is in different working modes, the heat accumulating and releasing heat pipe 5a works together with the heat releasing heat pipe 5b or the heat accumulating heat pipe 5c, but the condition that only the heat releasing heat pipe 5b and the heat accumulating heat pipe 5c work simultaneously does not occur, wherein the heat accumulating and releasing heat pipe 5a plays an important role in all modes, so the heat accumulating and releasing heat pipe 5a is arranged in the largest quantity, and the heat releasing heat pipe 5b and the heat accumulating heat pipe 5c are arranged at intervals in order to meet the working conditions of more heat pipes simultaneously.
Preferably, the "Z" -shaped heat pipe 5 is divided into a plurality of layers in the height direction, wherein the heat storage and release heat pipe 5a is an a layer, and the heat release heat pipe 5B and the heat storage heat pipe 5c are disposed in a B layer, wherein the a layer and the B layer are arranged at intervals in the height direction. The heat accumulator is in different working modes, the heat accumulating and releasing heat pipe 5a works together with the heat releasing heat pipe 5b or the heat accumulating heat pipe 5c, but the condition that only the heat releasing heat pipe 5b and the heat accumulating heat pipe 5c work simultaneously does not occur, wherein the heat accumulating and releasing heat pipe 5a plays an important role in all modes, so the heat accumulating and releasing heat pipe 5a is arranged in the largest quantity, and the heat releasing heat pipe 5b and the heat accumulating heat pipe 5c are arranged at intervals in order to meet the working conditions of more heat pipes simultaneously.
Preferably, the heat releasing heat pipes 5B and the heat accumulating heat pipes 5c of the B layer are arranged at intervals in the circumferential direction. The heat release heat pipes 5b and the heat accumulation heat pipes 5c can be uniformly arranged in the heat accumulator by circumferentially and alternately distributed, and different heat pipes can uniformly absorb or release heat in the operation process of the heat accumulator.
Preferably, the auxiliary heater 4 is provided at the evaporation stage of the heat radiation pipe 5 b. Through setting up in the evaporation zone, can realize the heat accumulation of heat accumulator and exothermic work fast.
Preferably, a plurality of auxiliary heaters 4 are provided in the height direction, and the heating power of the auxiliary heaters gradually increases from the bottom to the top in the height direction. As an improvement, the heating power of the auxiliary heater is gradually increased from bottom to top in the height direction to be larger and larger. Through the power change of the auxiliary heater, the rapid heat accumulation and melting of the heat accumulation material can be achieved, rapid heat release is achieved, and heat accumulation and release efficiency is improved.
Preferably, the cold water flowing direction of the cold water flow channel 1 flows from top to bottom. The heating power of the auxiliary heater is gradually increased by the cold water flowing from top to bottom and simultaneously matching with the cold water flowing from bottom to top along the height direction. The heat exchange efficiency can reach the optimal requirement, and the technical effect similar to the countercurrent heat exchange of a shell-and-tube heat exchanger is formed. Meanwhile, the heating power of the auxiliary heater is gradually increased from bottom to top along the height direction, so that the heat exchange effect can be ensured to further meet the optimal requirement.
Preferably, the inner diameter of the Z-shaped heat pipe can be 10-20mm, the pipe is a copper pipe, the inclination angle of the heat accumulation and release heat pipe is 30-60 degrees, and the ratio of the vertical section to the inclination section is 1:2:1, the inclination section angle of the heat storage heat pipe and the heat release heat pipe is 30-60 degrees, and the ratio of the vertical section to the inclination section is 1:1:1. the external diameter of the waste heat runner, the external diameter of the phase change material and the external diameter of the cold water runner are in a size ratio of 1:2:2.5. the size design can enable the heat exchange and heat accumulation effect to meet the optimal requirement.
The wall thickness of the Z-shaped heat pipe is selected according to the maximum working temperature of the heat accumulator and the type of working medium in the heat pipe.
Wherein,Sthe allowable stress of the material is 67MPa; d is the outer diameter of the copper pipe, and the unit is mm;twall thickness in mm;φtaking 0.8 as a welding coefficient;Ktaking 0.67 for material stretching compensation;P max the unit is MPa for the saturation pressure of the selected working medium at the maximum temperature.
The design is also designed according to a large number of experimental optimization, and the wall thickness of the Z-shaped heat pipe is designed according to the formula, so that the heat pipe can be ensured to be safe and stable in the operation process, and the risk of pipe explosion can be avoided.
Preferably, a heat exchange method of a regenerator as described above, four different modes of operation can be performed:
synchronous heat storage and release mode: when waste heat fluid exists and needs to heat cold water, the waste heat fluid flows through the waste heat flow channel 2, the synchronous heat storage and release Z-shaped heat pipe and the heat storage Z-shaped heat pipe start to work, at the moment, the cold water flows through the cold water flow channel 1 and the condensation section of the synchronous heat storage and release Z-shaped heat pipe to perform forced convection heat exchange, and the heat transfer performance of the heat storage Z-shaped heat pipe is lower than that of the synchronous heat storage Z-shaped heat pipe due to larger heat resistance between the heat storage Z-shaped heat pipe and the phase change material 3, at the moment, most heat of the waste heat fluid is used for cold water heating, and a small part of heat is absorbed by the phase change material 3 and stored in a latent heat form;
and (3) a heat storage mode: when the waste heat fluid exists and the cold water does not need to be heated, the waste heat fluid flows through the waste heat flow channel 2, the synchronous heat storage and release Z-shaped heat pipe and the heat storage Z-shaped heat pipe start to work, at the moment, no cold water flows through the cold water flow channel 1 to cool the synchronous heat storage and release Z-shaped heat pipe, and the heat absorbed by the heat pipe can only be absorbed by the phase change material 3 and is stored in a latent heat form;
exothermic mode: when there is no waste heat fluid but there is a need to heat the cold water, and the phase change material 3 has previously accumulated sufficient heat. At the moment, the exothermic Z-shaped heat pipe starts to work, the exothermic Z-shaped heat pipe absorbs heat in the phase change material 3, cold water flows through the cold water flow channel 1 to perform forced convection heat exchange with the exothermic Z-shaped heat pipe, and the heat is transferred into the cold water from the phase change material 3;
auxiliary electric heating mode: when there is no waste heat fluid but there is a need to heat the cold water, and the phase change material 3 does not accumulate sufficient heat. At this time, the auxiliary electric heater is turned on, the heat release Z-shaped heat pipe starts to work, the heat release Z-shaped heat pipe absorbs the heat provided by the electric heater, cold water flows through the cold water flow channel 1 to perform forced convection heat exchange with the heat release Z-shaped heat pipe, and the heat is transferred into the cold water by the phase change material 3.
An embodiment is provided, which comprises a cold water flow channel 1, a waste heat flow channel 2, a phase change material 3, an auxiliary electric heater 4 and a Z-shaped heat pipe 5, wherein the Z-shaped heat pipe 5 can be divided into a synchronous heat storage and release Z-shaped heat pipe 5a, a heat release Z-shaped heat pipe 5b and a heat storage Z-shaped heat pipe 5c. The cold water flow channel 1 is arranged on the outer side, the waste heat flow channel 2 is arranged on the inner side, the phase change material 3 is arranged between the cold water flow channel 1 and the waste heat flow channel 2, and an auxiliary electric heater is arranged in the phase change material 3, so that auxiliary heating can be performed when the waste heat quality is low. The synchronous heat accumulation and release Z-shaped heat pipe 5a penetrates through the cold water flow channel 1, the waste heat flow channel 2 and the phase change material 3, a heat pipe evaporation section (namely the lower end of the heat pipe) is arranged in the waste heat flow channel 2, a heat pipe condensation section (namely the upper end of the heat pipe) is arranged in the cold water flow channel 1, and an inclined section is arranged in the phase change material 3; the heat release Z-shaped heat pipe 5b is arranged in the cold water flow channel 1 and the phase change material 3, the heat pipe evaporation section (namely the lower end of the heat pipe) is arranged in the phase change material 3, and the heat pipe condensation section (namely the upper end of the heat pipe) is arranged in the cold water flow channel 1; the heat storage Z-shaped heat pipe 5c is arranged in the waste heat flow channel 2 and the phase change material 3, the heat pipe evaporation section (i.e. the lower end of the heat pipe) is arranged in the waste heat flow channel 2, and the heat pipe condensation section (i.e. the upper end of the heat pipe) is arranged in the phase change material 3. The specific arrangement is shown in fig. 1A-A and B-B. The number of Z-shaped heat pipes is selected by the size of the heat accumulator, the liquid filling rate of the heat pipes is 20% -50%, and the heat pipes can be adjusted according to the size of the heat pipes and the quality of waste heat. The working temperature interval of the heat pipe is included in the phase change temperature of the phase change material 3, the selection of the working medium of the heat pipe and the phase change material 3 is determined by the quality of the waste heat, the combination condition is given but not limited to, when the waste heat temperature is 50-100 ℃, the working medium of the heat pipe can be selected to be R134-a, and the phase change material 3 can be selected to be paraffin with corresponding purity; when the temperature of the waste heat is 100-150 ℃, the working medium of the heat pipe can be acetone, and the phase change material 3 can be KAl (SO 4) 2.12H2O; when the temperature of the waste heat is 150-200 ℃, the working medium of the heat pipe can be deionized water, the phase change material 3 can be KNO3-NaNO2-NaNO3, and the mass ratio is (53:40:7).
As shown in fig. 4, in order to further improve the heat exchange performance of the heat pipe, the fluid and the phase change material 3, fin structures are arranged on the outer wall surface of the heat pipe, 6a is an inclined section fin structure, 6b is a vertical section fin structure, and all the fin directions of the areas should be parallel to the fluid flow direction and the gravity direction, so as to reduce the fluid flow resistance to the greatest extent and reduce the blocking effect on the natural convection of the phase change material 3.
A heat exchange method of a heat exchanger as described above, four different operation modes can be performed:
mode one: and synchronizing the heat storage and release modes. When the waste heat fluid exists and needs to heat the cold water, the waste heat fluid flows through the waste heat flow channel 2, the synchronous heat storage and release Z-shaped heat pipe 5a and the heat storage Z-shaped heat pipe 5c start to work, at the moment, the cold water flows through the cold water flow channel 1 and the condensation section of the synchronous heat storage and release Z-shaped heat pipe 5a to perform forced convection heat exchange, and the heat storage Z-shaped heat pipe 5c has lower heat transfer performance than the synchronous heat storage and release Z-shaped heat pipe 5a due to larger heat resistance between the heat storage Z-shaped heat pipe and the phase change material 3. At this time, most of heat of the waste heat fluid is used for cold water heating, and a small part of heat is absorbed by the phase change material 3 and stored in the form of latent heat.
Mode two: and a heat storage mode. When the waste heat fluid exists and the cold water does not need to be heated, the waste heat fluid flows through the waste heat flow channel 2, the synchronous heat storage and release Z-shaped heat pipe 5a and the heat storage Z-shaped heat pipe 5c start to work, at the moment, no cold water flows through the cold water flow channel 1 to cool the synchronous heat storage and release Z-shaped heat pipe 5a, and the heat absorbed by the heat pipe can only be absorbed by the phase change material 3 and stored in a latent heat form.
Mode three: exothermic mode. When there is no waste heat fluid but there is a need to heat the cold water, and the phase change material 3 has previously accumulated sufficient heat. At this time, the heat-releasing "Z" shaped heat pipe 5b starts to work, the heat-releasing "Z" shaped heat pipe 5b absorbs the heat in the phase-change material 3, the cold water flows through the cold water channel 1 to perform forced convection heat exchange with the heat-releasing "Z" shaped heat pipe 5b, and the heat is transferred from the phase-change material 3 to the cold water.
Mode four: auxiliary electric heating mode. When there is no waste heat fluid but there is a need to heat the cold water, and the phase change material 3 does not accumulate sufficient heat. At this time, the auxiliary electric heater 4 is turned on, the heat release Z-shaped heat pipe 5b starts to work, the heat release Z-shaped heat pipe 5b absorbs the heat provided by the electric heater, the cold water flows through the cold water flow channel 1 to perform forced convection heat exchange with the heat release Z-shaped heat pipe 5b, and the heat is transferred into the cold water by the phase change material 3.
While the invention has been described in terms of preferred embodiments, the invention is not so limited. Various changes and modifications may be made by one skilled in the art without departing from the spirit and scope of the invention, and the scope of the invention should be assessed accordingly to that of the appended claims.
Claims (6)
1. The sleeve type heat pipe phase change heat accumulator comprises a cold water flow passage, a waste heat flow passage, a phase change material and a Z-shaped heat pipe, wherein the Z-shaped heat pipe comprises three types, namely a heat accumulation heat release heat pipe, a heat release heat pipe and a heat accumulation heat pipe, the cold water flow passage is arranged on the outer side, the waste heat flow passage is arranged on the inner side, the phase change material is arranged between the cold water flow passage and the waste heat flow passage, the heat accumulation heat release heat pipe penetrates through the cold water flow passage, the waste heat flow passage and the phase change material, the heat release heat pipe is arranged in the cold water flow passage and the phase change material, and the heat accumulation heat pipe is arranged in the waste heat flow passage and the phase change material; the heat accumulator further comprises an auxiliary heater, and the phase change material is internally provided with the auxiliary heater; the cold water flowing direction of the cold water flow channel flows from top to bottom; the auxiliary heater is arranged at the evaporation section of the heat release heat pipe; a plurality of auxiliary heaters are arranged along the height direction, and the heating power of the auxiliary heaters is gradually increased from bottom to top along the height direction; the Z-shaped heat pipe comprises a vertical evaporation section positioned at the lower part, a vertical condensation section positioned at the upper part and an inclined section connected with the evaporation section and the condensation section, wherein the evaporation section of the heat accumulation and release heat pipe is arranged in the waste heat flow channel, the condensation section is arranged in the cold water flow channel, and the inclined section is arranged in the phase change material; the exothermic heat pipe evaporation section is arranged in the phase change material, and the condensation section is arranged in the cold water flow passage; the heat accumulation heat pipe evaporation section is arranged in the waste heat runner, and the condensation section is arranged in the phase change material.
2. The heat accumulator of claim 1, wherein when the waste heat temperature is 100-150 ℃, the heat pipe working medium is acetone, and the phase change material is KAl (SO 4) 2.12h2o; when the temperature of the waste heat is 150-200 ℃, the working medium of the heat pipe is deionized water, and the phase change material is KNO 3 -NaNO 2 -NaNO 3 The mass ratio was 53:40:7.
3. The regenerator of claim 1 in which the evaporator end of the radiant heat pipe is thermally coupled to the auxiliary heater.
4. The regenerator of claim 1 in which the cold water flow path, the waste heat flow path, and the phase change material are arranged in concentric circles.
5. The regenerator of claim 1, wherein the auxiliary heater is an electric heater.
6. A method of heat exchange in a regenerator as claimed in any one of claims 1 to 5 in which four different modes of operation are possible:
synchronous heat storage and release mode: when the waste heat fluid exists and needs to heat cold water, the waste heat fluid flows through the waste heat flow channel, the synchronous heat storage and release heat pipe and the heat storage heat pipe start to work, at the moment, the cold water flows through the cold water flow channel and the condensation section of the synchronous heat storage and release heat pipe to perform forced convection heat exchange, the heat transfer performance of the heat storage heat pipe is lower than that of the synchronous heat storage heat pipe due to larger heat resistance between the heat storage heat pipe and the phase change material, at the moment, most heat of the waste heat fluid is used for heating the cold water, and a small part of heat is absorbed by the phase change material and stored in a latent heat form;
and (3) a heat storage mode: when the waste heat fluid exists and the cold water does not need to be heated, the waste heat fluid flows through the waste heat flow channel, the synchronous heat storage and release heat pipe and the heat storage heat pipe start to work, at the moment, no cold water flows through the cold water flow channel to cool the synchronous heat storage and release heat pipe, and the heat absorbed by the heat pipe can only be absorbed by the phase change material and is stored in a form of latent heat;
exothermic mode: when the waste heat fluid does not exist but the cold water needs to be heated, and the phase change material stores enough heat before the waste heat fluid exists, the heat release heat pipe starts to work at the moment, the heat release heat pipe absorbs the heat in the phase change material, the cold water flows through the cold water flow channel to carry out forced convection heat exchange with the heat release heat pipe, and the heat is transferred into the cold water from the phase change material;
auxiliary electric heating mode: when the waste heat fluid does not exist but the cold water needs to be heated, and the phase change material does not store enough heat, the auxiliary electric heater is started at the moment, the heat release heat pipe starts to work, the heat release heat pipe absorbs the heat provided by the electric heater, the cold water flows through the cold water flow channel to carry out forced convection heat exchange with the heat release heat pipe, and the heat is transferred into the cold water by the phase change material.
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| CN202410182461.9A CN117848136A (en) | 2023-05-08 | 2023-05-08 | Auxiliary heating phase change heat accumulator |
| CN202310509137.9A CN116399147B (en) | 2023-05-08 | 2023-05-08 | Sleeve type heat pipe phase change heat accumulator |
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Citations (5)
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| JP2000171179A (en) * | 1998-12-02 | 2000-06-23 | Osaka Gas Co Ltd | Thermal storage device and fuel battery generator facility having thermal storage device |
| CN101004332A (en) * | 2007-01-25 | 2007-07-25 | 南京大学 | Heat pipe accumulator |
| CN106767082A (en) * | 2017-01-10 | 2017-05-31 | 上海海事大学 | Packaged type based on pulsating heat pipe stores heat-releasing device and its stores exothermic processes |
| CN107014235A (en) * | 2017-04-18 | 2017-08-04 | 中国矿业大学 | A kind of phase-change material and diverging heat pipe coupled tank system |
| CN217274242U (en) * | 2022-05-06 | 2022-08-23 | 上海意丰机电科技开发有限公司 | Air preheater |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2013025645A2 (en) * | 2011-08-12 | 2013-02-21 | Mcalister Technologies, Llc | Systems and methods for collecting and processing permafrost gases, and for cooling permafrost |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000171179A (en) * | 1998-12-02 | 2000-06-23 | Osaka Gas Co Ltd | Thermal storage device and fuel battery generator facility having thermal storage device |
| CN101004332A (en) * | 2007-01-25 | 2007-07-25 | 南京大学 | Heat pipe accumulator |
| CN106767082A (en) * | 2017-01-10 | 2017-05-31 | 上海海事大学 | Packaged type based on pulsating heat pipe stores heat-releasing device and its stores exothermic processes |
| CN107014235A (en) * | 2017-04-18 | 2017-08-04 | 中国矿业大学 | A kind of phase-change material and diverging heat pipe coupled tank system |
| CN217274242U (en) * | 2022-05-06 | 2022-08-23 | 上海意丰机电科技开发有限公司 | Air preheater |
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| CN116399147A (en) | 2023-07-07 |
| CN117848136A (en) | 2024-04-09 |
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