CN116734641B - Plate heat exchanger of field cooperative control cylinder density - Google Patents
Plate heat exchanger of field cooperative control cylinder density Download PDFInfo
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- CN116734641B CN116734641B CN202211068579.6A CN202211068579A CN116734641B CN 116734641 B CN116734641 B CN 116734641B CN 202211068579 A CN202211068579 A CN 202211068579A CN 116734641 B CN116734641 B CN 116734641B
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Abstract
The invention relates to a plate heat exchanger with field cooperative control of cylinder density, which is characterized in that at least one fluid input pipe is arranged for guiding cold fluid from a cavity of the plate heat exchanger, at least one fluid output pipe is arranged for guiding heated cold source out of the cavity, and a temperature sensor is also arranged for collecting temperature in the cavity of the plate heat exchanger so as to control inflow and outflow of a cold source. Through the continuously increased distribution density, the temperature difference in the whole heat exchange process is kept relatively stable, so that a technical effect similar to countercurrent heat exchange is formed, and the constant temperature difference can exceed the countercurrent heat exchange effect under the condition that the total heating power is kept unchanged, so that the optimal heat exchange efficiency is achieved.
Description
Technical Field
The invention relates to a heat exchanger technology, in particular to a flat plate type heat exchanger.
Background
The flat plate type heat exchanger is the heat exchanger with highest heat exchange efficiency in various heat exchangers at present, and has the advantages of small occupied space and convenient installation and disassembly. The heat exchanger consists of stamping formed concave-convex stainless steel plates, the concave-convex lines between two adjacent plates are combined relatively at 180 degrees, so that staggered contact points are formed by concave-convex ridge lines between the two plates of the plate heat exchanger, and after the contact points are combined in a vacuum welding mode, a high-pressure-resistant staggered circulation structure of the plate heat exchanger is formed, and the staggered circulation structures enable cold and hot fluid in the plate heat exchanger to generate strong turbulence so as to achieve a high heat exchange effect.
Flat tubes have been widely used in automotive air conditioning units and residential or commercial air conditioning heat exchangers in recent years. Such flat tubes are provided with a plurality of small channels therein through which, in use, a heat exchange fluid flows. Because the heat exchange area of the flat tube is large, the heat exchange effect can be greatly improved.
The flat plate type heat exchanger is widely applied to industries such as chemical industry, petroleum, refrigeration, nuclear energy, power and the like, and the demand for the heat exchanger in industrial production is increased and the quality requirement for the heat exchanger is also increased due to the worldwide energy crisis so as to reduce energy consumption. In recent decades, although compact heat exchangers (plate-type, plate-fin-type, pressure-welded plate-type heat exchangers, etc.), heat pipe-type heat exchangers, direct contact heat exchangers, etc. have been rapidly developed, shell-and-tube heat exchangers still occupy the dominant position of yield and usage due to high reliability and wide adaptability, and the usage of the shell-and-tube heat exchangers in the current industrial devices still accounts for about 70% of the usage of all heat exchangers according to relevant statistics.
In the indirect liquid cooling scheme, a water-cooled plate heat exchanger is used for heat exchange. The water-cooled plate is a metal heat exchange device with a flow channel structure therein, and is usually made of copper or aluminum. The heat exchange fluid is directly contacted with the bottom surface of the water cooling plate substrate, the heat of heat transfer is conducted to the water cooling plate, and then the water cooling plate and the refrigerant in the water cooling plate perform heat convection to take away the heat. The whole liquid cooling system utilizes the pump to provide power for the circulation of working medium, and compared with an air cooling system, the liquid cooling system has a more compact structure. And most of used refrigerants are media such as deionized water compatible with cold plate materials, ethylene glycol-deionized water with specified percentages, nanofluid and the like, and have higher specific heat capacity and heat conductivity coefficient than air, and the heat dissipation effect is better than that of air cooling. In addition, the noise level of the indirect liquid cooling system is significantly reduced compared to an air cooling system.
In recent years, in order to meet the heat exchange requirement, research on an indirect liquid cooling system has been developed, and various aspects of a cooling plate structure, refrigerant selection, pipeline arrangement and the like are involved, so that the influence of the cooling plate structure on the heat exchange and the power consumption of the liquid cooling system is found to be particularly remarkable. The water cooling plate can be divided into a base plate, a runner and a cover plate. The cover plate and the hose connector have no unified standard, different manufacturers have different structural forms, and the base plate and the flow channel can be configured in various ways according to equipment and heat design power consumption, which is also a main factor influencing the heat dissipation performance of the water cooling plate.
Research and engineering applications show that the flat plate type heat exchanger and the heat pipe have excellent heat exchange performance respectively. Besides, the phase change material has stable temperature in the heat absorption and release process, so that the whole system can achieve the effect of uniform temperature, and the phase change material is widely applied to the field of heat exchange.
The invention provides a novel flat plate type heat exchanger, which ensures that a heat pipe and a flat plate type heat exchanger are fully combined through the capillary force of a heat source at the lower part and the cooperation between support columns arranged at the upper part and the cooperation of a flat tube second part arranged at the upper part, so that the heat source is efficiently, uniformly and accurately radiated.
Disclosure of Invention
The present invention aims to solve at least one of the technical problems of the prior art or related art. The invention provides the plate heat exchanger which has the advantages of good integration effect, reduced processing difficulty, high heat exchange efficiency and no energy consumption.
The technical scheme of the invention is as follows: a plate heat exchanger with field cooperative control of cylinder density, characterized in that at least one fluid inlet pipe is provided for guiding cold fluid from the cavity to the plate heat exchanger, and at least one fluid outlet pipe is provided for guiding heated cold source out of the cavity, and a temperature sensor is provided for collecting the temperature in the cavity of the plate heat exchanger for controlling inflow and outflow of the cold source.
A baffle is arranged in the cavity to guide the cold source to flow.
A plate heat exchanger of field cooperative control cylinder density, the heat exchanger includes first part and second part, and the second part is located first part upper portion, first part includes upper plate and hypoplastron, set up the support column that extends downwards on the lower surface of upper plate, set up the heat source that extends upwards on the upper surface of hypoplastron, the heat source is first cylinder, the heat source constitutes first cylinder array, upper plate and hypoplastron form confined first part, its characterized in that, along the fluid flow direction in the second part, the distribution density of first cylinder increases gradually.
The distribution density of the first pillars gradually increases in magnitude along the direction of fluid flow in the second portion.
The height of the second pillars is 300-400mm, the distance between the centers of the second pillars is 30-70 μm, and the diameter of the second pillars is 80-100 μm.
The first column arrays and the support columns jointly form a liquid return part of the first part, the gaps between the support columns are larger than the gaps between the first columns, and capillary driving force is generated between the first columns; the second part comprises a box body and an end cover positioned at the upper part of the box body, and the box body comprises a second column extending upwards from the bottom wall of the box body; the end cover is provided with an inlet and an outlet.
The heat source is an electric heater.
The first cylinder is a resistive heater.
The support column is square, and first cylinder and second cylinder are circular.
The heat exchanger comprises a first part and a second part, wherein the second part is positioned at the upper part of the first part, the first part comprises an upper plate and a lower plate, the lower surface of the upper plate is provided with a support column extending downwards, the upper surface of the lower plate is provided with a heat source extending upwards, the heat source is a first column, the heat source forms a first column array, the upper plate and the lower plate form a closed first part, the first column array and the support column jointly form a liquid return part of the first part, the gap between the support columns is larger than the gap between the first columns, and capillary driving force is generated between the first columns; the second part comprises a box body and an end cover positioned at the upper part of the box body, and the box body comprises a second column extending upwards from the bottom wall of the box body; the end cover is provided with an inlet and an outlet.
Preferably, the inlet and outlet are disposed at two diagonal positions of the end cap.
Preferably, the support columns are square and the first and second columns are circular.
Preferably, the support columns are divided into groups of four, the groups of support columns being arranged in a transverse and longitudinal direction to form transverse support columns parallel to each other and longitudinal rows of support columns parallel to each other.
Preferably, the height of the second column is greater than the height of the second section.
Preferably, the second column is an elastic member, and the second column has an increasing elasticity along the direction of fluid flow in the heat exchanger.
Compared with the prior art, the invention has the following advantages:
1) Through the continuously increased distribution density, the temperature difference in the whole heat exchange process is kept relatively stable, so that a technical effect similar to countercurrent heat exchange is formed, and the constant temperature difference can exceed the countercurrent heat exchange effect under the condition that the total heating power is kept unchanged, so that the optimal heat exchange efficiency is achieved.
2) The invention provides a novel plate heat exchanger, which is characterized in that a first part and a second part are arranged, wherein the first part has the property of a heat pipe, and the second part has the property of the plate heat exchanger, so that the heat pipe and the plate heat exchanger are fully combined, and the efficient, balanced and accurate heat dissipation of a heat source is realized.
3) According to the invention, the second part is provided with the supporting columns and the cylindrical heat source arranged on the lower plate, the supporting columns do not form capillary force, the liquid mainly plays a role in condensing the liquid, then flows to the lower plate, and the liquid is pumped to the bottom of the lower plate through the capillary force between the heat sources for heating and is heated through the heat source. The arrangement can enable condensed liquid to quickly flow to the bottom heating surface, so that the effect of quick heating is achieved, and the heat exchange efficiency is improved.
4) The invention provides a novel plate heat exchanger, wherein a second column is arranged in a second part, fluid flows between the columns to absorb heat, and heat exchange efficiency is further improved.
5) According to the invention, through the cooperation between the cylindrical heat source array at the lower part of the first part and the support column arranged at the upper part, and through the cooperation between the cylindrical heat source array at the second part arranged at the upper part and the support column arranged at the second part, the efficient, balanced and accurate heat dissipation of the heat source is realized.
6) According to the invention, through the layout change of the capillary force of the first column, fluid can be uniformly distributed on the bottom part of the lower plate, so that heat exchange is balanced.
Drawings
FIG. 1 is a schematic view of a plate heat exchanger of the present invention;
FIG. 2 is a schematic view of the lower part of the upper plate of the first part of the heat exchanger according to the present invention;
FIG. 3 is a schematic view showing the upper structure of the lower plate of the first portion of the heat exchanger according to the present invention;
FIG. 4 is a schematic view of the end cap of the second portion of the heat exchanger of the present invention;
FIG. 5 is a schematic view of a second part of the structure of the case of the present invention;
fig. 6 is a schematic view of the structural optimization of the present invention.
Detailed Description
The following will make additional description on the technical solution in the embodiment of the present invention with reference to the drawings in the embodiment of the present invention.
In the plate heat exchangers put into operation at present, most machines have smaller load and smaller corresponding self-starting capacity because of the characteristics of high heat value and low moisture of heat sources; the plate heat exchanger with poor heat source has high load due to the low heat value and high water content of the heat source. The main equipment capacities of two types of plate heat exchangers which are actually operated and participate in self-starting are respectively counted, the types are different, and the self-starting capacities are also different.
Fig. 1-5 show schematic views of the plate heat exchanger according to the invention. As shown in fig. 1, a plate heat exchanger comprises a first part 1 and a second part 2, the second part 2 being located in the upper part of the first part 1, the first part 1 comprising an upper plate 11 and a lower plate 12. As shown in fig. 2 and 3, the lower surface of the upper plate 11 is provided with a supporting column 111 extending downwards, the upper surface of the lower plate 12 is provided with a heat source 121 extending upwards, the heat source 121 is a first column 121, the heat source 121 forms a first column array, the upper plate 11 and the lower plate 12 form a closed first part 1, and the first column is connected with the supporting column; the first column arrays and the support columns 111 together form a liquid return portion of the first portion, gaps between the support columns are larger than gaps between the first columns, and capillary driving force is generated between the first columns; the second part 2 comprises a box 21 and an end cover 22 positioned at the upper part of the box, wherein the box 21 comprises a second column 211 extending upwards from the bottom wall of the box 21; the end cap 22 is provided with an inlet 221 and an outlet 222.
The invention provides a novel plate heat exchanger, which is characterized in that a first part and a second part are arranged, wherein the first part has the property of a heat pipe, and the second part has the property of the plate heat exchanger, so that the heat pipe and the plate heat exchanger are fully combined, and the efficient, balanced and accurate heat dissipation of a heat source is realized.
Preferably, the gaps between the support columns 111 disposed in the upper plate are larger than the gaps between the first columns of the lower plate, the diameters of the first columns and the intervals between the first columns to generate capillary driving force. The first column array has smaller diameter and interval to increase capillary driving force, so as to raise the power of the reflux of condensed liquid in the first part, and to prevent the local high heat flux from evaporating to dryness instantaneously. And the first column body is used as a heat source, so that the evaporation phase change of the liquid working medium in the interior can be quickened, and the heat transfer resistance is reduced.
The invention provides a novel plate heat exchanger, wherein a support column is arranged on an upper plate, a first column is arranged on a lower plate, the support column does not form capillary force, mainly plays a role in condensing liquid, then the liquid flows to the lower plate, and the liquid is sucked to the bottom of the lower plate through the capillary force between the first columns for heating. The arrangement can enable condensed liquid to quickly flow to the bottom heating surface, so that the effect of quick heating is achieved, and the heat exchange efficiency is improved. The lower part is provided with the first column body, and the whole fluid can be uniformly distributed on the bottom part of the lower plate by the capillary force of the first column body, so that heat exchange is balanced. The first column body is also a heat source, and simultaneously heats surrounding fluid to enable the surrounding fluid to be evaporated rapidly, and the support columns play a role of fins and play a role of enhancing heat transfer.
Preferably, the inlet and outlet are disposed at two diagonal positions of the end cap.
Preferably, the support columns are square and the first and second columns are circular.
Preferably, the support columns are divided into groups of four, the groups of support columns being arranged in a transverse and longitudinal direction to form transverse support columns parallel to each other and longitudinal rows of support columns parallel to each other.
Preferably, the height of the second column is greater than the height of the second section.
Preferably, the height of the second pillars is 300-400mm, the spacing between the centers of the second pillars is 30-70 μm, and the diameter of the second pillars is 80-100 μm.
Gaps are arranged between the support columns, and the capillary force of the first column corresponding to the lower part of the support column 111 is smaller than that of the first column corresponding to the gaps of the support columns. Through the arrangement, the fluid can be uniformly distributed on the bottom part of the lower plate, so that heat exchange is balanced.
Preferably, the capillary force of the first column corresponding to the lower portion of the gap between the two support columns 111 is gradually increased and then gradually decreased from one support column to the other. By the arrangement, the fluid can be pumped into the gap through capillary force, and the fluid can be uniformly distributed on the bottom part of the lower plate, so that heat exchange is balanced.
Preferably, the capillary force is first of all of progressively greater magnitude and progressively smaller magnitude. The above arrangement can further improve the uniformity.
Preferably, the critical point for increasing to decreasing is the middle of the gap, i.e., from one support column to the middle of the gap, the capillary force is first increasing and then decreasing from the middle of the gap to the other support column.
Preferably, as the gap distance increases, the difference between the capillary force of the first column corresponding to the lower portion of the gap and the capillary force corresponding to the lower portion of the support column increases. Through such setting, can make more heat transfer balanced, avoid the heat transfer uneven.
Preferably, the support columns are divided into groups of four, the groups of support columns being arranged in a transverse and longitudinal direction to form transverse support columns parallel to each other and longitudinal rows of support columns parallel to each other.
Preferably, the inlet and outlet are disposed at diagonal positions of the housing.
Preferably, the heat source is an electric heater. Preferably the first cylinder is a resistive heater.
The lower plate 12 of the first portion is designed mainly for enhancing capillary driving force so that the flow rate per unit time flowing through the first columns 121 is maximized when the ratio of the first column height h to the spacing s is 4.8-5.2, preferably 5, to maximize the heat exchange effect.
Preferably, the ratio of the center interval s to the support column side length d and the ratio of the height h to the support column side length d are respectively 1.9-2.1, preferably 2, and the permeability K is the largest, and the flow resistance of the liquid working medium on the upper plate is the smallest.
Preferably, the second column is an elastic component, the elastic component can enable the second column to be flushed when fluid flows, the second column can pulsate to swing, and therefore scale removal is promoted, turbulent flow effect is caused by vibration, and heat transfer can be enhanced.
Preferably, the second cylinder may be a spring.
Preferably, the second cylinder is more and more elastic along the direction of fluid flow within the second portion. As research shows that along with the heat exchange of the fluid, the temperature of the fluid is higher and higher, the fluid is easier to scale, and the scale degree is more serious along the flowing direction of the fluid, so that the purposes of further descaling and enhancing heat transfer are achieved by increasing the elasticity degree, the heat conductor with large elasticity is reduced, and the cost is reduced.
Further preferably, the second cylinder has an increasingly greater magnitude of elasticity along the direction of fluid flow within the second portion. The change is found according to the research, accords with the scaling rule, and can further reduce the cost, improve the heat exchange efficiency and reduce the scaling.
The invention is based on the heat pipe performance of the first part, the heat source is arranged inside the first part 1, the lower plate 12 of the heat source is arranged to reduce contact thermal resistance, the second part is arranged above the upper plate 11 of the first part 1, and the fluid to be heated is introduced into the inside. When the system works, the high heat generated by the heat source causes the local temperature of the lower surface of the first part to rise, the internal working medium starts to evaporate, phase change and absorb heat, steam is generated to reach the upper plate 11 of the first part 1 under the action of gravity, condensation and heat release are started, the heat is transferred to the upper plate 11, at the moment, the condensed liquid working medium returns to the lower plate 12 through the liquid return part 9 in the first part to continue to evaporate, and the phase change circulation of the internal working medium of the first part is utilized to reach extremely high equivalent heat conductivity coefficient. At this time, the temperature of the upper plate 11 is increased and the temperature distribution is uniform, so that the heat transfer performance of the second part is improved, the cooling working medium flows through the micro-channels in the micro-channel heat exchanger, and the heat is absorbed by the cooling working medium and flows out of the whole heat dissipation structure.
According to the invention, through the cooperation between the capillary first column array at the lower part of the heat pipe and the support column arranged at the upper part, and through the cooperation of the second part arranged at the upper part, the efficient, balanced and accurate heat dissipation of the heat source is realized.
As an improvement, the heating power of the first cylinder is gradually increased along the fluid flow direction in the second section. The temperature difference is kept relatively stable in the whole heat exchange process by continuously increasing the heating power, so that a technical effect similar to countercurrent heat exchange is formed, and the constant temperature difference can exceed the countercurrent heat exchange effect under the condition that the total heating power is kept unchanged, so that the optimal heat exchange efficiency is achieved.
It is further preferred that the heating power of the first cylinder increases progressively more and more in magnitude along the direction of fluid flow in the second section. The optimal design can further ensure that the temperature difference is kept relatively stable in the whole heat exchange process, so that a more optimal heat exchange effect is achieved.
As an improvement, the resistance of the first cylinder increases gradually along the direction of fluid flow in the second portion. Through the continuous increase of the resistance, the heating power is also gradually increased, so that the temperature difference is kept relatively stable in the whole heat exchange process, the technical effect similar to countercurrent heat exchange is formed, and the constant temperature difference can exceed the countercurrent heat exchange effect under the condition that the total heating power is kept unchanged, thereby achieving the optimal heat exchange efficiency.
Further preferably, the resistance of the first cylinder increases progressively more and more in magnitude along the direction of fluid flow within the second portion. The optimal design can further ensure that the temperature difference is kept relatively stable in the whole heat exchange process, so that a more optimal heat exchange effect is achieved.
As an improvement, the distribution density of the first columns increases gradually along the direction of fluid flow in the second section. Through the continuously increased distribution density, the temperature difference in the whole heat exchange process is kept relatively stable, so that a technical effect similar to countercurrent heat exchange is formed, and the constant temperature difference can exceed the countercurrent heat exchange effect under the condition that the total heating power is kept unchanged, so that the optimal heat exchange efficiency is achieved.
Further preferably, the distribution density of the first pillars increases progressively more and more in magnitude along the direction of fluid flow in the second portion. The optimal design can further ensure that the temperature difference is kept relatively stable in the whole heat exchange process, so that a more optimal heat exchange effect is achieved.
Preferably, the heating power of the middle portion of the first cylinder is different from that of the surrounding portion. By varying the heating power, a rapid circulation of the internal fluid can be achieved. For example, the steam rises at the high power locations and the liquid drops at the low power locations, thereby creating boiler-like risers and downcomers, increasing the circulation rate within the fluid.
Preferably, the middle portion and the peripheral portion of the first cylinder may be independently controlled to heat, thereby independently controlling heating power of the middle portion and the peripheral portion.
Preferably, the heating power of the middle portion of the first cylinder is higher than the heating power of the surrounding portion. Preferably 2-3 times the heating power of the surrounding parts.
Preferably, the middle portion of the first cylinder has a different thermal resistance from the surrounding portion. The difference in heating power is achieved by the difference in thermal resistance.
Preferably, the thermal resistance of the middle portion of the first cylinder is higher than that of the surrounding portion. Preferably 1.4 to 1.7 times the thermal resistance of the surrounding portion.
Preferably, the first cylinder has a higher distribution density in the middle portion than in the surrounding portion. Preferably 2-3 times the distribution density of the surrounding portions.
By the arrangement, the fluid in the first part is evaporated in the middle part and then condensed and descends around, so that rapid circulation is formed under the condition of certain heating power, and the heating efficiency is improved.
Preferably, in order to avoid the difference of the heating power and the temperature difference of the lower wall surface of the second part and the upper wall surface of the first part, the application is improved as follows:
The first column is divided into a middle part and a peripheral part, and the middle part and the peripheral part can independently control heating, so that the heating power of the middle part and the peripheral part can be independently controlled.
The controller controls the intermittent variation of the power of the intermediate section and the peripheral section such that the intermediate section and the peripheral section alternate in heating power.
In one period T, the heating power of the surrounding part is T1, the heating power of the middle part is T2, the heating power of the surrounding part is T2 and the heating power of the middle part is T1 in the half period time of 0-T/2; wherein T2 > T1;
Preferably, T2 is 2-3 times T1.
Through the intermittent power change, the temperature difference of the lower wall surface of the second part is not too large, the situation that a certain position is always an ascending section and the temperature is too high is avoided, the ascending section and the descending section in the first part are alternately changed, the temperature difference of the lower wall surface of the second part and the upper wall surface of the first part is relatively small, and the service life of a product is prolonged while the heat exchange efficiency is improved.
Compared with the traditional configuration, the optimized heat exchanger is more complete, each part of the primary system of the station service is provided with the main protection and the backup protection, and the protection devices are tightly matched, so that the main protection dead zone is eliminated; the effective protection range of each level of protection device is defined through a clear setting principle, and the coordination among the levels of protection is reasonable, so that the requirements of relay protection reliability, selectivity, rapidity and sensitivity are met.
After optimization, the relay protection action time is greatly shortened, the requirement of relay protection on rapidity is met, and the reliability of the electric primary system is greatly improved.
The above embodiments are provided to illustrate the technical concept and features of the present invention and are intended to enable those skilled in the art to understand the content of the present invention and implement the same, and are not intended to limit the scope of the present invention. All equivalent changes or modifications made according to the spirit of the present invention should be construed to be included in the scope of the present invention.
Claims (3)
1. A plate heat exchanger for controlling column density, the heat exchanger comprising a first part and a second part, the second part being located at the upper part of the first part, the first part comprising an upper plate and a lower plate, the lower surface of the upper plate being provided with downwardly extending support columns, the upper surface of the lower plate being provided with upwardly extending heat sources, the heat sources being first columns, the heat sources forming a first column array, the upper plate and the lower plate forming a closed first part, characterized in that the first column array and the support columns together forming a liquid return part of the first part, the gap between the support columns being greater than the gap between the first columns, capillary driving force being generated between the first columns; the second part comprises a box body and an end cover positioned at the upper part of the box body, and the box body comprises a second column extending upwards from the bottom wall of the box body; an inlet and an outlet are arranged on the end cover; the distribution density of the first pillars gradually increases along the direction of fluid flow in the second portion.
2. A plate heat exchanger according to claim 1, wherein the distribution density of the first cylinders increases progressively more and more in the direction of fluid flow in the second section.
3. A plate heat exchanger according to claim 1, wherein the heat source is an electric heater.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2022103627620 | 2022-04-07 | ||
| CN202210362762 | 2022-04-07 |
Publications (2)
| Publication Number | Publication Date |
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| CN116734641A CN116734641A (en) | 2023-09-12 |
| CN116734641B true CN116734641B (en) | 2024-04-19 |
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| CN101614497A (en) * | 2008-06-27 | 2009-12-30 | 富准精密工业(深圳)有限公司 | The manufacture method of flat plate heat tube |
| CN101706226A (en) * | 2009-11-23 | 2010-05-12 | 陈盈同 | Heat dissipation structure and manufacturing method thereof |
| CN102706193A (en) * | 2012-06-28 | 2012-10-03 | 华南理工大学 | Radial gradually-wide type fin-structure grooved panel heat pipe and processing method thereof |
| CN109539826A (en) * | 2018-07-20 | 2019-03-29 | 山东大学 | A kind of shell-and-tube heat exchanger of fin height variation |
| CN111238264A (en) * | 2019-12-13 | 2020-06-05 | 山东大学 | Water-cooling plate heat exchanger capable of distributing flow according to wall surface temperature |
| CN111256498A (en) * | 2020-01-21 | 2020-06-09 | 青岛科技大学 | Method for controlling opening and closing of three valves by temperature for four-fluid heat exchanger |
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