CN114777542B - Manifold shell-and-tube heat exchanger - Google Patents
Manifold shell-and-tube heat exchanger Download PDFInfo
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- CN114777542B CN114777542B CN202210547750.5A CN202210547750A CN114777542B CN 114777542 B CN114777542 B CN 114777542B CN 202210547750 A CN202210547750 A CN 202210547750A CN 114777542 B CN114777542 B CN 114777542B
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- cold fluid
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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
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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
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/08—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being otherwise bent, e.g. in a serpentine or zig-zag
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
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- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention provides a heat exchange capillary structure and a manifold shell-and-tube heat exchanger thereof, wherein the capillary structure comprises a heat exchange capillary force layer, the heat exchange capillary force layer comprises a hot fluid capillary force layer and a cold fluid capillary force layer, the hot fluid capillary force layer and the cold fluid capillary force layer are not communicated with each other, and heat exchange is carried out on hot fluid and cold fluid through the heat exchange capillary force layer. The invention provides a heat exchange capillary structure capable of realizing heat exchange of cold and hot fluid, which can ensure uniform distribution of the fluid and countercurrent of the cold and hot fluid and improve heat exchange efficiency.
Description
Technical Field
The invention relates to a heat exchanger technology, in particular to a heat pipe heat exchanger, and belongs to the field of F28d15/02 heat pipes.
Background
A heat exchanger is a device that exchanges heat with a hot and cold fluid, also known as a heat exchanger. Heat exchangers are widely used in many fields. In the fields such as electronics, petrifaction, communication, aerospace and the like, the special requirements on the size and the weight of the heat exchanger are met because the working scene is special, and the heat exchange capability is required to be stronger. In 1981, a learner proposed to utilize a micro-channel to dissipate heat, so that the volume of the heat exchanger can be reduced, and the heat exchange capacity of the heat exchanger can be greatly improved by utilizing the higher specific surface area of the micro-channel. However, although the heat exchange capacity is strong, the overall pressure loss is also high due to the small hydraulic diameter of the microchannels.
A great deal of researches show that the micro-channel heat exchanger also has the problem of uneven temperature distribution, and in 1991, a learner proposes a manifold type micro-channel heat exchanger based on the micro-channel heat exchanger and greatly reduces the overall pressure loss. However, extensive research has shown that the distribution of fluid within the manifold microchannels is not uniform, resulting in a non-uniform temperature distribution.
Patent CN201811088661.9 discloses a manifold type jet micro-channel heat exchanger, which promotes heat exchange by jet enhanced disturbance and improves the temperature distribution characteristic of the bottom thereof. Patent CN202010760271.2 discloses a manifold type microchannel heat exchanger with high aspect ratio, which improves heat exchange area and effectively reduces pressure drop. Patent 2021104191686 discloses a manifold type diamond microchannel heat exchanger which meets the requirement of high heat density heat dissipation. However, the above-mentioned prior art can remove heat of a certain hot spot, but cannot realize heat exchange of cold and hot fluid.
In order to overcome the defects, the invention improves the prior heat exchanger and provides a manifold type micro-channel heat exchanger capable of realizing heat exchange of cold and hot fluid. The pressure loss of the whole body can be reduced, the advantages of manifold impact jet flow can be achieved, and the fluid disturbance and heat exchange are enhanced. Meanwhile, the uniform distribution of the fluid and the countercurrent of the cold and hot fluid can be ensured, and the heat exchange efficiency is improved.
Disclosure of Invention
The invention aims to provide a manifold type micro-channel heat exchanger capable of realizing heat exchange of cold and hot fluid. The pressure loss of the whole body can be reduced, the advantages of manifold impact jet flow can be achieved, and the fluid disturbance and heat exchange are enhanced. Meanwhile, the uniform distribution of the fluid and the countercurrent of the cold and hot fluid can be ensured, and the heat exchange efficiency is improved.
In order to achieve the above object, the technical scheme of the present invention is as follows:
the heat exchange capillary structure comprises a heat exchange capillary force layer, wherein the heat exchange capillary force layer comprises a hot fluid capillary force layer and a cold fluid capillary force layer, the hot fluid capillary force layer and the cold fluid capillary force layer are respectively positioned on two opposite surfaces of the capillary structure, the hot fluid capillary force layer and the cold fluid capillary force layer are not communicated with each other, and heat exchange is carried out on hot fluid and cold fluid through the heat exchange capillary force layer.
Preferably, the wicking layer is a microchannel structure.
Preferably, the capillary force layer is arranged with the capillary force in a direction perpendicular to the plate-like structure.
Preferably, mao Xili of the cold fluid capillary force layer intermediate positions is greater than Mao Xili of the cold fluid inlet manifold and the cold fluid outlet manifold.
Preferably, mao Xili of the thermal fluid capillary force layer intermediate is greater than Mao Xili proximate to the thermal fluid inlet and outlet manifolds.
The utility model provides a manifold shell-and-tube heat exchanger, includes the shell, set up hot fluid manifold layer, cold fluid manifold layer and heat transfer capillary force structure in the shell, the capillary force structure is preceding capillary force structure, and wherein heat transfer capillary force layer includes hot fluid capillary force layer and cold fluid capillary force layer, and cold fluid manifold layer laminating is in cold fluid capillary force layer, and hot fluid manifold layer laminating is in hot fluid capillary force layer.
Preferably, the thermal fluid manifold layer comprises a thermal fluid inlet manifold, a thermal fluid outlet manifold, a thermal fluid inlet manifold and a thermal fluid outlet manifold, the thermal fluid inlet manifold being in communication with the thermal fluid inlet manifold, the thermal fluid outlet manifold being in communication with the thermal fluid outlet manifold, the thermal fluid inlet manifold and the thermal fluid outlet manifold being in communication by the thermal fluid capillary force layer.
Preferably, the thermal fluid manifold layer comprises a plurality of folded plate-like structures forming a thermal fluid inlet manifold on one side and a thermal fluid outlet manifold on the other side, the thermal fluid inlet manifold and the thermal fluid outlet manifold not being in direct communication.
Preferably, the cold fluid manifold layer comprises a cold fluid inlet manifold, a cold fluid outlet manifold, a cold fluid inlet manifold and a cold fluid outlet manifold, the cold fluid inlet manifold being in communication with the cold fluid inlet manifold, the cold fluid outlet manifold being in communication with the cold fluid outlet manifold, the cold fluid inlet manifold and the cold fluid outlet manifold being in communication by the cold fluid capillary force layer.
Preferably, the cold fluid manifold layer comprises a plurality of folded plate-like structures forming a cold fluid inlet manifold on one side and a cold fluid outlet manifold on the other side, the cold fluid inlet manifold and cold fluid outlet manifold not being in direct communication.
Compared with the prior art, the invention has the following advantages:
1) The invention improves the current manifold heat exchanger, not only can reduce the integral pressure loss, but also has the advantages of manifold impact jet flow, and strengthens the fluid disturbance and heat exchange. Meanwhile, the uniform distribution of the fluid and the countercurrent of the cold and hot fluid can be ensured, and the heat exchange efficiency is improved.
2) The capillary force layer capillary suction force is arranged along the direction vertical to the plate-shaped structure, so that fluid enters the outlet manifold from the inlet manifold vertical to the plate-shaped structure, on one hand, the flow of the fluid can be quickened, the fluid is uniformly distributed, on the other hand, the capillary force layer capillary suction force can be vertical to the plate-shaped structure, the plate-shaped result is similar to a plate-shaped fin, and the heat exchange coefficient is further improved.
3) According to the invention, through Mao Xili arrangement, the capillary suction force at the middle position is maximized, the capillary suction force near the inlet collecting pipe and the outlet collecting pipe is reduced, and the fluid is concentrated at the middle part for heat exchange, so that the heat exchange efficiency is improved as a whole.
Drawings
FIG. 1 is a block diagram of the heat exchanger of the present invention;
FIG. 2 is a hierarchical block diagram of a heat exchanger according to the present invention;
FIG. 3 is a block diagram of a thermal fluid manifold layer of a heat exchanger of the present invention;
FIG. 4 is a block diagram of a cold fluid manifold layer of a heat exchanger according to the present invention;
FIG. 5 is a schematic view of a preferred embodiment of a heat exchange microchannel layer structure of a heat exchanger according to the present invention;
FIG. 6 is a schematic diagram of the flow of a hot fluid manifold of the present invention;
FIG. 7 is a schematic diagram of cold fluid manifold layer flow;
fig. 8 is a schematic overall flow diagram of the present invention.
Reference numerals:
fig. 1:1, a shell; 2 a thermal fluid manifold layer; 3 a cold fluid manifold layer; 4, a heat exchange micro-channel layer;
fig. 2:1 a shell, 11 a hot fluid inlet, 12 a hot fluid outlet, 13 a cold fluid inlet, 14 a cold fluid outlet; a hot fluid manifold layer, a hot fluid inlet manifold, a hot fluid outlet manifold, a hot fluid inlet manifold, and a hot fluid outlet manifold, respectively, 2, 21, 22, 23, 24; 3 a cold fluid manifold layer, 31 a cold fluid inlet header, 32 a cold fluid outlet header, 33 a cold fluid inlet manifold, 34 a cold fluid outlet manifold; 4. a heat exchange microchannel layer;
fig. 3:2 thermal fluid manifold layer, 21 thermal fluid inlet manifold, 22 thermal fluid outlet manifold, 23 thermal fluid inlet manifold, 24 thermal fluid outlet manifold
Fig. 4:3 a cold fluid manifold layer, 31 a cold fluid inlet header, 32 a cold fluid outlet header, 33 a cold fluid inlet manifold, 34 a cold fluid outlet manifold;
fig. 5:4 heat exchange capillary force layers, 41 heat exchange capillary force layers, 411 hot fluid capillary force layers and 412 cold fluid capillary force layers;
fig. 6: a 11 hot fluid inlet, a 12 hot fluid outlet, a 21 hot fluid inlet manifold, a 22 hot fluid outlet manifold, a 23 hot fluid inlet manifold, a 24 hot fluid outlet manifold;
fig. 7:13 cold fluid inlet, 14 cold fluid outlet, 31 cold fluid inlet header, 32 cold fluid outlet header, 33 cold fluid inlet manifold, 34 cold fluid outlet manifold;
fig. 8:411 hot fluid microchannels, 412 cold fluid microchannels.
Detailed Description
The following describes the embodiments of the present invention in detail with reference to the drawings.
Figures 1-8 disclose a manifold shell-and-tube heat exchanger. As shown in fig. 1, the manifold shell-and-tube heat exchanger comprises a shell 1, wherein a hot fluid manifold layer 2, a cold fluid manifold layer 3 and a heat exchange capillary force layer 4 are arranged in the shell 1. As shown in fig. 2, the heat exchange capillary force layer comprises a hot fluid capillary force layer 411 and a cold fluid capillary force layer 412, the cold fluid manifold layer 3 is attached to the cold fluid capillary force layer 412, the hot fluid manifold layer 2 is attached to the hot fluid capillary force layer 411, and the hot fluid capillary force layer 411 and the cold fluid capillary force layer 412 are not communicated with each other, that is, the hot fluid and the cold fluid cannot be mixed, and the hot fluid and the cold fluid exchange heat through the heat exchange capillary force layer 4.
The invention provides a manifold type micro-channel heat exchanger capable of realizing heat exchange of cold and hot fluid, which only aims at a certain hot spot to dissipate heat in the prior art. The cold and hot fluid can exchange heat through the heat exchange capillary force layer 4. The structure has the characteristics of heat exchange of two fluids of the heat exchanger, is compatible with the advantages of the manifold type micro-channel heat exchanger, can reduce the integral pressure loss, has the advantages of manifold impact jet flow, and strengthens the fluid disturbance and heat exchange. Meanwhile, the uniform distribution of the fluid and the countercurrent of the cold and hot fluid can be ensured, and the heat exchange efficiency is improved.
Preferably, as shown in fig. 3, the thermal fluid manifold layer 2 includes a thermal fluid inlet manifold 21, a thermal fluid outlet manifold 22, a thermal fluid inlet manifold 23 and a thermal fluid outlet manifold 24, the thermal fluid inlet manifold 21 being in communication with the thermal fluid inlet manifold 23, the thermal fluid outlet manifold 22 being in communication with the thermal fluid outlet manifold 24, the thermal fluid inlet manifold 23 and the thermal fluid outlet manifold 24 not being in direct communication with each other, the fluid communication being achieved by the thermal fluid capillary force layer 411. The capillary force of the fluid through the thermal fluid capillary layer causes the thermal fluid to flow from the thermal fluid inlet manifold 23 to the thermal fluid outlet manifold 24.
Preferably, as shown in fig. 3, the thermal fluid manifold layer 2 comprises a plurality of bent plate-like structures, one side of which forms a thermal fluid inlet manifold 23 and the other side forms a thermal fluid outlet manifold 24, said thermal fluid inlet manifold 23 and thermal fluid outlet manifold 24 not being in direct communication. The capillary force of the fluid through the thermal fluid capillary layer causes the thermal fluid to flow from the thermal fluid inlet manifold 23 to the thermal fluid outlet manifold 24.
Preferably, as shown in fig. 4, the cold fluid manifold layer 3 comprises a cold fluid inlet manifold 31, a cold fluid outlet manifold 32, a cold fluid inlet manifold 33 and a cold fluid outlet manifold 34, the cold fluid inlet manifold 31 being in communication with the cold fluid inlet manifold 33, the cold fluid outlet manifold 32 being in communication with the cold fluid outlet manifold 34, the cold fluid inlet manifold 33 and the cold fluid outlet manifold 34 being in communication through the cold fluid capillary layer 412. The capillary force of the fluid through the cold fluid capillary layer causes cold fluid to flow from the cold fluid inlet manifold 33 to the cold fluid outlet manifold 34.
Preferably, as shown in fig. 4, the cold fluid manifold layer 3 comprises a plurality of bent plate-like structures forming on one side a cold fluid inlet manifold 33 and on the other side a cold fluid outlet manifold 34, said cold fluid inlet manifold and cold fluid outlet manifold not being in direct communication. The capillary force of the fluid through the cold fluid capillary layer causes cold fluid to flow from the cold fluid inlet manifold 33 to the cold fluid outlet manifold 34.
Preferably, the cold fluid inlet header 31 and the cold fluid outlet header 32 are designed in a tapered structure, and the flow passage area is smaller and smaller along the flow direction of the fluid in the cold fluid inlet header, and larger along the flow direction of the fluid in the cold fluid outlet header.
The hot fluid inlet manifold 21 and the hot fluid outlet manifold 22 are designed to have a tapered structure, and the flow passage area is smaller and smaller along the flow direction of the fluid in the hot fluid inlet manifold, and the flow passage area is larger and larger along the flow direction of the fluid in the hot fluid outlet manifold.
This ensures uniform distribution of fluid in the hot fluid microchannels 411 and the cold fluid microchannels 412, which improves heat transfer efficiency and reduces overall pressure drop.
Preferably, the bent plate-like structure is a V-shaped structure or a trapezoid structure. The heat exchange micro-channels can be designed more in the same width, the heat exchange area is increased, and the whole heat exchange capacity is improved while the volume is reduced.
Preferably, the hot fluid inlet and the hot fluid outlet are arranged diagonally on the hot fluid manifold layer 2. The cold fluid inlet and the cold fluid outlet are arranged diagonally on the cold fluid manifold layer 3. The arrangement can ensure the heat exchange area of the fluid and reduce the occurrence of short circuit phenomenon.
Preferably, a cold fluid outlet is provided at a position corresponding to the hot fluid inlet, and a cold fluid inlet is provided at a position corresponding to the hot fluid outlet. The arrangement can generate a countercurrent effect similar to that of a shell-and-tube heat exchanger, and improves the heat exchange efficiency.
Preferably, the capillary force layer is a microchannel structure.
Preferably, the capillary force layer is arranged with the capillary force in a direction perpendicular to the plate-like structure. Preferably, the microchannels of the microchannel structure are arranged perpendicular to the plate-like structure direction. By arranging such that the fluid passes from the inlet manifold to the outlet manifold perpendicular to the plate-like structure, the flow of fluid can be accelerated on the one hand, so that the fluid is evenly distributed, on the other hand, perpendicular to the plate-like structure, the plate-like result resembling a plate fin, and the heat exchange coefficient is further improved.
Preferably, mao Xili of the cold fluid capillary force layer intermediate is greater than Mao Xili of the cold fluid inlet and outlet headers. Mao Xili of the thermal fluid capillary force layer intermediate is greater than Mao Xili proximate to the thermal fluid inlet and outlet manifolds. Because the middle part heat exchange capacity is biggest, through above-mentioned setting for the capillary suction of intermediate position is biggest, and the capillary suction that is close to entry manifold and export manifold diminishes, makes the fluid concentrate in the middle part and carries out the heat transfer, thereby improves heat exchange efficiency on the whole.
Preferably, capillary layer capillary suction forces first become greater and then smaller from cold fluid inlet header 31 to cold fluid outlet header 32. Similarly, capillary attraction increases from the hot fluid inlet manifold 21 to the hot fluid outlet manifold 22 and then decreases. With such a progressive Mao Xili arrangement, the heat exchange efficiency can be further improved.
The hot fluid inlet manifold 21, the hot fluid outlet manifold 22, the hot fluid inlet manifold 23, the hot fluid outlet manifold 24, the cold fluid inlet manifold 31, the cold fluid outlet manifold 32, the cold fluid inlet manifold 33 and the cold fluid outlet manifold 34 are all designed to be conical, which ensures uniform distribution of fluid in the hot fluid microchannels 411 and the cold fluid microchannels 412, and can improve heat exchange efficiency and reduce overall pressure drop. Meanwhile, the hot fluid micro-channel 411 and the cold fluid micro-channel 412 in the heat exchange micro-channel layer 4 are designed into V shapes, so that more heat exchange micro-channels can be designed in the same width, the heat exchange area is increased, and the whole heat exchange capacity is improved while the volume is reduced. In addition, the hot fluid inlet manifold 23 and the cold fluid inlet manifold 33 are staggered in space in the device, and the design can realize the countercurrent flow of cold and hot fluid and further improve the overall heat exchange capacity.
The working process is as follows: the hot fluid flows into the heat exchanger through the hot fluid inlet 11, then into the hot fluid inlet manifold 21, then into the hot fluid inlet manifold 23, and impinges down into the hot fluid microchannels 411, and flows to both sides along the flow direction of the hot fluid microchannels 411, then the different direction fluids merge into the hot fluid outlet manifold 24, and after merging at the hot fluid outlet manifold 22, flows out of the heat exchanger through the hot fluid outlet 12. At the same time, the cold fluid flows into the heat exchanger through the cold fluid inlet 13, then flows into the cold fluid inlet manifold 31, then flows into the cold fluid inlet manifold 33, and impacts down into the cold fluid microchannel 412, flows to both sides along the flow direction of the cold fluid microchannel 412, and flows out of the heat exchanger in countercurrent with the hot fluid of the hot fluid microchannel 411, thereby realizing heat exchange. Cold fluid from different directions then merges into a cold fluid outlet manifold 34 and exits the heat exchanger through the cold fluid outlet 14 after merging at the cold fluid outlet header 32.
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 shell-and-tube heat exchanger comprises a shell, wherein a hot fluid manifold layer, a cold fluid manifold layer and a heat exchange capillary structure are arranged in the shell, the capillary structure comprises a heat exchange capillary force layer, the heat exchange capillary force layer comprises a hot fluid capillary force layer and a cold fluid capillary force layer, the hot fluid capillary force layer and the cold fluid capillary force layer are respectively positioned on two opposite surfaces of the capillary structure, the hot fluid capillary force layer and the cold fluid capillary force layer are not communicated with each other, and heat exchange is carried out on the hot fluid and the cold fluid through the heat exchange capillary force layer; the cold fluid manifold layer is attached to the cold fluid capillary force layer, and the hot fluid manifold layer is attached to the hot fluid capillary force layer; the hot fluid manifold layer comprises a plurality of bent plate-shaped structures, one side of each plate-shaped structure forms a hot fluid inlet manifold, the other side of each plate-shaped structure forms a hot fluid outlet manifold, and the hot fluid inlet manifolds and the hot fluid outlet manifolds are not directly communicated; the capillary force layer is a micro-channel structure; mao Xili of the cold fluid capillary force layer intermediate position is greater than Mao Xili of the cold fluid inlet manifold and the cold fluid outlet manifold.
2. The heat exchanger of claim 1, wherein the capillary force layer capillary attraction is disposed in a direction perpendicular to the plate-like structure.
3. The heat exchanger of claim 1, wherein Mao Xili of the thermal fluid capillary force layer intermediate locations is greater than Mao Xili proximate to the thermal fluid inlet and outlet headers.
4. The heat exchanger of claim 1, wherein the thermal fluid manifold layer comprises a thermal fluid inlet manifold, a thermal fluid outlet manifold, a thermal fluid inlet manifold, and a thermal fluid outlet manifold, the thermal fluid inlet manifold in communication with the thermal fluid inlet manifold, the thermal fluid outlet manifold in communication with the thermal fluid outlet manifold, the thermal fluid inlet manifold and the thermal fluid outlet manifold in communication through the thermal fluid capillary force layer.
5. The heat exchanger of claim 1, wherein the cold fluid manifold layer comprises a cold fluid inlet manifold, a cold fluid outlet manifold, a cold fluid inlet manifold, and a cold fluid outlet manifold, the cold fluid inlet manifold in communication with the cold fluid inlet manifold, the cold fluid outlet manifold in communication with the cold fluid outlet manifold, the cold fluid inlet manifold and the cold fluid outlet manifold in communication through the cold fluid capillary layer.
6. The heat exchanger of claim 5, wherein the cold fluid manifold layer comprises a plurality of bent plate-like structures forming a cold fluid inlet manifold on one side and a cold fluid outlet manifold on the other side, the cold fluid inlet manifold and cold fluid outlet manifold not being in direct communication.
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| CN202210547750.5A CN114777542B (en) | 2021-11-03 | 2021-11-03 | Manifold shell-and-tube heat exchanger |
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| CN202210547750.5A CN114777542B (en) | 2021-11-03 | 2021-11-03 | Manifold shell-and-tube heat exchanger |
| CN202111291436.7A CN113776367B (en) | 2021-11-03 | 2021-11-03 | Manifold shell-and-tube heat exchanger |
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| CN114136129B (en) * | 2021-12-20 | 2023-02-03 | 山东大学 | Manifold micro-column array flat plate heat exchanger |
| CN115289891A (en) * | 2022-07-29 | 2022-11-04 | 大连理工大学 | Manifold-fin integrated micro-channel heat exchanger |
| CN115682796B (en) * | 2022-11-04 | 2023-11-10 | 山东高等技术研究院 | 3D printing porous medium cold plate and preparation process thereof |
| CN116428897B (en) * | 2022-11-04 | 2024-01-26 | 山东大学 | Plate heat exchanger of spindle-shaped hot runner |
| CN115768045B (en) * | 2022-11-07 | 2023-10-03 | 北京大学 | Radiator and electronic equipment |
| CN116190330A (en) * | 2023-02-21 | 2023-05-30 | 华中科技大学 | Manifold microchannel radiator based on hot spot area orientation optimization |
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| US7775261B2 (en) * | 2002-02-26 | 2010-08-17 | Mikros Manufacturing, Inc. | Capillary condenser/evaporator |
| US6986382B2 (en) * | 2002-11-01 | 2006-01-17 | Cooligy Inc. | Interwoven manifolds for pressure drop reduction in microchannel heat exchangers |
| US7013956B2 (en) * | 2003-09-02 | 2006-03-21 | Thermal Corp. | Heat pipe evaporator with porous valve |
| US8210243B2 (en) * | 2008-07-21 | 2012-07-03 | International Business Machines Corporation | Structure and apparatus for cooling integrated circuits using cooper microchannels |
| US8474516B2 (en) * | 2008-08-08 | 2013-07-02 | Mikros Manufacturing, Inc. | Heat exchanger having winding micro-channels |
| ES2480765B1 (en) * | 2012-12-27 | 2015-05-08 | Universitat Politècnica De Catalunya | Thermal energy storage system combining solid heat sensitive material and phase change material |
| CN203572287U (en) * | 2013-11-08 | 2014-04-30 | 北京临近空间飞行器系统工程研究所 | Plate-fin type phase change heat exchanger |
| US9657999B2 (en) * | 2014-11-11 | 2017-05-23 | Northrop Grumman Systems Corporation | Alternating channel heat exchanger |
| CN105627808A (en) * | 2015-12-31 | 2016-06-01 | 北京航空航天大学 | Novel heat exchanger core and distribution structure |
| US20180100706A1 (en) * | 2016-10-11 | 2018-04-12 | Climate Master, Inc. | Enhanced heat exchanger |
| CN107014230A (en) * | 2017-03-30 | 2017-08-04 | 贵州永红航空机械有限责任公司 | A kind of internal deflector type multipaths plate fin type radiator |
| CN107894020A (en) * | 2017-12-06 | 2018-04-10 | 北京谷能新能源科技有限公司 | A kind of paddy electricity heat accumulating and heating device with far infrared electric heating apparatus |
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