CN109556441B - Abnormal plate-fin cooler - Google Patents
Abnormal plate-fin cooler Download PDFInfo
- Publication number
- CN109556441B CN109556441B CN201811638165.6A CN201811638165A CN109556441B CN 109556441 B CN109556441 B CN 109556441B CN 201811638165 A CN201811638165 A CN 201811638165A CN 109556441 B CN109556441 B CN 109556441B
- Authority
- CN
- China
- Prior art keywords
- fluid
- channel
- heat exchange
- fin cooler
- flow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000002159 abnormal effect Effects 0.000 title claims description 19
- 239000012530 fluid Substances 0.000 claims abstract description 68
- 239000012809 cooling fluid Substances 0.000 claims abstract description 58
- 238000001816 cooling Methods 0.000 claims abstract description 51
- 230000007246 mechanism Effects 0.000 claims abstract description 17
- 238000005192 partition Methods 0.000 claims abstract description 13
- 238000007789 sealing Methods 0.000 claims abstract description 3
- 238000004891 communication Methods 0.000 abstract description 3
- 238000012546 transfer Methods 0.000 description 13
- 238000000034 method Methods 0.000 description 8
- 230000008569 process Effects 0.000 description 8
- 238000013461 design Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 230000001788 irregular Effects 0.000 description 6
- 230000004048 modification Effects 0.000 description 5
- 238000012986 modification Methods 0.000 description 5
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000009792 diffusion process Methods 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 238000010008 shearing Methods 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007123 defense Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
Classifications
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F11/00—Arrangements for sealing leaky tubes and conduits
- F28F11/04—Arrangements for sealing leaky tubes and conduits using pairs of obturating elements, e.g. washers, mounted upon central operating rods
-
- 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
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses a special-shaped plate-fin cooler, which relates to the technical field of cooling equipment and comprises a cooling core body, a hot inlet end socket and a hot outlet end socket; the cooling core body comprises a plurality of channels formed by stacking a plurality of partition boards; fins are arranged in the channels; the fin comprises a plurality of pipelines; the outer diameter of the pipelines is smaller than the vertical height of the channel; the pipeline is in a bent shape; a gap for cooling fluid to circulate is reserved in the channel; one end of each pipeline is communicated with the hot inlet end socket, and the other end of each pipeline is communicated with the hot outlet end socket; the channel is provided with a sealing mechanism for separating the gap from communication with the hot inlet end socket and the hot outlet end socket; the channel is composed of upper and lower partition plates, fins and a closing mechanism. The special-shaped plate fin cooler provided by the invention has the advantages of stable structure, stronger pressure bearing capacity and long service life; the occupied volume is small; meanwhile, the heat exchange efficiency of the cooling core body can be comprehensively increased by increasing the heat exchange area, the fluid flow, the flow speed, the heat exchange coefficient and the heat exchange quantity, and the enterprise cost is reduced.
Description
Technical Field
The invention relates to the technical field of cooling equipment, in particular to a special-shaped plate-fin cooler.
Background
The plate-fin cooler is generally composed of a partition plate, fins, seals and guide vanes. The fin, the guide vane and the seal are placed between two adjacent partition boards to form a sandwich layer called a channel, the sandwich layers are stacked according to different modes of fluid, and the sandwich layers are brazed into a whole to form a plate bundle, wherein the plate bundle is the core of the plate-fin cooler. The channels include a hot channel for circulating a fluid to be cooled and a cold channel for circulating a cooling fluid; the hot channels are spaced from the cold channels. The plate-fin cooler has the advantages of high heat transfer efficiency, compact structure, light weight, firmness, high adaptability and the like, so that the plate-fin cooler is widely applied to the fields of air separation devices, petrochemical industry, power machinery, atomic energy, national defense industry and the like.
The fins are the most basic elements of the plate-fin cooler, and the heat exchange between the fluid to be cooled and the cooling fluid is mostly carried out through the fins, and the heat transfer area of the fins is about 67% -88% of the total heat transfer area of the cooler. From the heat transfer mechanism point of view, the plate-fin cooler still belongs to the shoulder-arm cooler. The main feature is that it has an extended secondary heat transfer surface (fins), so that the heat transfer process is performed not only on the primary heat transfer surface (separator) but also on the secondary heat transfer surface. Since the area of the partition plate is constant, the cooling efficiency of the plate-fin cooler is mainly determined by the heat transfer area of the fins. Common fin forms are zigzag, porous, straight, corrugated, etc. However, the existing fin type cannot fully exert the cooling effect of the fin on the cooling fluid, and the cooling efficiency cannot meet the cooling requirement of people.
Disclosure of Invention
Aiming at the problems, the invention provides the special-shaped plate-fin cooler, which solves the problem that the cooling effect of fins on cooling fluid cannot be fully exerted in the form of fins in the prior art, and increases the flow and heat exchange area of the fluid to be cooled and improves the cooling efficiency of the special-shaped plate-fin cooler through the fin structure design of a bent pipeline; has stronger practicability and economic value.
In order to achieve the above purpose, the technical scheme provided by the invention is as follows:
the invention provides a special-shaped plate-fin cooler, which comprises a cooling core body for cooling fluid to be cooled, a heat inlet end socket for the fluid to be cooled to flow in and a heat outlet end socket for the fluid to be cooled to flow out; the cooling core body comprises a plurality of channels formed by stacking a plurality of partition plates; fins are arranged in the channels; the fins comprise a plurality of pipelines for circulating fluid to be cooled; the outer diameter of the plurality of pipelines is smaller than the vertical height of the channel; the pipeline is in a bent shape; a gap for cooling fluid to circulate is reserved in the channel; one end of each pipeline is communicated with the heat inlet end socket, and the other end of each pipeline is communicated with the heat outlet end socket; the channel is provided with a sealing mechanism for isolating the gap from being communicated with the hot inlet end socket and the hot outlet end socket; the channel is composed of the upper and lower partition plates, the fins and the closing mechanism; the flowing directions of the fluid to be cooled and the cooling fluid are perpendicular to each other.
In the abnormal plate-fin cooler provided by the invention, preferably, the pipeline is of a spiral structure with a variable spiral radius.
The abnormal plate-fin cooler provided by the invention is characterized in that the pipeline preferably comprises a plurality of flow channels; the flow channel is of a spiral structure with gradually increased spiral radius; and a plurality of flow channels are connected in series to form the pipeline.
In the shaped plate-fin cooler provided by the invention, preferably, the spiral radius increasing directions of the flow channels on the pipeline are the same.
In the abnormal plate-fin cooler provided by the invention, preferably, a plurality of pipelines are arranged in parallel; the spiral radius of a plurality of flow channels on adjacent pipelines is increased in opposite directions.
In the deformed plate-fin cooler provided by the invention, preferably, the adjacent flow channels on the pipeline are sleeved with one end with a small spiral radius on one flow channel from one end with a large spiral radius on the other flow channel.
In the abnormal plate-fin cooler provided by the invention, preferably, a plurality of vertical baffles are arranged between adjacent pipelines; an included angle alpha is formed between the plate surface of the baffle plate and the flow direction of the cooling fluid, and the included angle alpha is more than 0 degrees and less than or equal to 90 degrees; the baffle is provided with a plurality of through holes for cooling fluid to circulate.
In the shaped plate-fin cooler provided by the invention, preferably, the through holes are provided with turbulence pieces for increasing turbulence of cooling fluid.
In the deformed plate-fin cooler provided by the invention, preferably, a first seal is arranged at one end of the channel, which is close to the heat inlet end socket; the first seal is provided with a plurality of first openings for communicating a plurality of pipelines with the hot inlet seal head; a second seal is arranged at one end of the channel, which is close to the hot-out seal head; the second seal is provided with a plurality of second openings for communicating a plurality of pipelines with the hot-out seal head; the first seal and the second seal form the closing mechanism.
The technical scheme has the following advantages or beneficial effects:
according to the abnormal plate-fin cooler provided by the invention, the fins are designed into the pipeline structure, the pipeline is of the spiral structure with the spiral radius changed, and the gap for cooling fluid to circulate is reserved in the channel, so that the abnormal plate-fin cooler is stable in structure, and has stronger pressure bearing capacity and longer service life; meanwhile, the heat exchange efficiency of the cooling core body can be comprehensively increased by increasing the heat exchange area, the fluid flow, the flow speed, the heat exchange coefficient and the heat exchange quantity, namely, the required heat exchange volume is smaller under the same heat load requirement; the volume of the special-shaped plate-fin cooler is reduced, and the cost of enterprises is reduced.
Drawings
The invention and its features, aspects and advantages will become more apparent from the detailed description of non-limiting embodiments with reference to the following drawings. Like numbers refer to like parts throughout. The drawings are not intended to be drawn to scale, emphasis instead being placed upon illustrating the principles of the invention.
FIG. 1 is a schematic view showing the overall structure of a profiled plate-fin cooler according to embodiment 1 or embodiment 2 of the present invention;
FIG. 2 is a top view of a profiled plate-fin cooler fin and baffle configuration provided in embodiment 1 of the present invention;
FIG. 3 is a side view of a portion of a channel of a profiled plate-fin cooler provided in either embodiment 1 or embodiment 2 of the present invention;
FIG. 4 is a schematic view of a baffle structure of a profiled plate-fin cooler according to embodiment 1 or embodiment 2 of the present invention;
FIG. 5 is a schematic view of the turbulence belt structure of the profiled plate-fin cooler according to embodiment 1 or embodiment 2 of the present invention;
fig. 6 is a top view of a shaped plate-fin cooler fin and baffle structure provided in embodiment 2 of the present invention.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is evident that the described embodiments are only some, but not all embodiments of the present invention. Accordingly, the following detailed description of the embodiments of the invention, as presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be made by a person skilled in the art without making any inventive effort, are intended to fall within the scope of the present invention.
Example 1:
as shown in fig. 1, the special-shaped plate-fin cooler provided in embodiment 1 of the present invention includes a cooling core 1 for cooling a fluid to be cooled, a heat inlet end enclosure 2 for flowing in the fluid to be cooled, and a heat outlet end enclosure 3 for flowing out the fluid to be cooled, where the cooling core 1 includes a plurality of channels 12 formed by stacking a plurality of separators 11; the channels 12 are provided with a plurality of fins 13 for circulating a fluid to be cooled; as shown in fig. 2, the fins 13 comprise a plurality of tubes 131 for the passage of the fluid to be cooled; the outer diameter of the plurality of pipes 131 is smaller than the vertical height of the channel 12; the pipe 131 is curved; a gap 14 for the passage of a cooling fluid is left in the channel 12; one end of each of the pipelines 131 is communicated with the heat inlet end socket 2, and the other end is communicated with the heat outlet end socket 3; the channel 12 is provided with a closing mechanism 4 for isolating the gap 14 from being communicated with the hot inlet end enclosure 2 and the hot outlet end enclosure 3; the channel 12 is formed by the upper and lower partition plates 11, the fins 13 and the closing mechanism 4.
Specifically, as shown in fig. 1, the side provided with the heat inlet end enclosure 2 is the left side of the cooling core 1, and the heat outlet end enclosure 3 is arranged on the right side of the cooling core 1; a heat inlet 21 for flowing in the fluid to be cooled is arranged on the heat inlet seal head 2, and the heat inlet 21 is positioned at the lower part of the heat inlet seal head 2; a heat outlet 31 for flowing out the fluid to be cooled is arranged on the heat outlet seal head 3, and the heat outlet 31 is positioned at the upper part of the heat outlet seal head 3; the flowing directions of the fluid to be cooled and the cooling fluid are perpendicular to each other. The separator 11, the fins 13 and the closing mechanism 4 are brazed. The flowing directions of the fluid to be cooled and the cooling fluid are perpendicular to each other.
According to the abnormal plate-fin cooler provided by the embodiment 1 of the invention, the fins 13 are designed into the pipeline structure, and the pressure bearing capacity of the pipeline 131 is higher than that of the traditional fins, so that the damage to the cooling core body 1 in the flowing process of fluid to be cooled can be reduced, and the service life of the abnormal plate-fin cooler is prolonged; the fins 13 are arranged into the bent pipeline, the heat exchange area is higher than that of the traditional fins, and cooling fluid flows through the gaps 14 of the channels 12, so that the heat exchange amount of the fluid to be cooled and the cooling fluid is improved; the heat exchange efficiency of the cooling core body 1 can be improved through the design, namely, the required heat exchange area is smaller under the same heat load requirement, and the cost of enterprises is saved. The design is integrated, the structure of the irregular plate-fin cooler is stable, and the irregular plate-fin cooler has stronger pressure bearing capacity; the application range of the special-shaped plate-fin cooler is enlarged; and the cost of enterprises is saved.
Preferably, as shown in fig. 2, the conduit 131 is a helical structure with varying helical radius. More preferably, as shown in fig. 2, the conduit 131 includes a plurality of flow channels 1311; the flow channel 1311 has a spiral structure with gradually increasing spiral radius; the plurality of runners 1311 are in series communication to form the conduit 131.
In the abnormal plate-fin cooler provided in embodiment 1 of the present invention, first, the pipeline 131 is designed into a spiral structure, and first, the flow of the fluid to be cooled can be increased in a limited plate surface area, so that the fluid to be cooled has higher flow heat exchange comprehensive performance in the flowing process, and the heat exchange capacity of the abnormal plate-fin cooler is increased; secondly, the heat exchange area of the fluid to be cooled is increased; the heat exchange efficiency is improved; thirdly, in the flowing process of the fluid to be cooled, the spiral structure provides centripetal force for the flowing of the fluid, so that the flow speed of the fluid is increased, on one hand, the flow speed of the fluid is high, a certain shearing force is provided, and the scaling tendency is low; on the other hand, the heat exchange coefficient of the cooling core body 1 can be increased, and the heat exchange efficiency is improved; fourth, the fluid to be cooled circulates in the spiral pipeline 131 with the spiral radius changed, so that the turbulence degree of the fluid to be cooled is increased, the heat exchange coefficient of the cooling core body 1 is increased, and the heat exchange efficiency is improved. The spiral radius of the second pipeline 131 is changed, so that the turbulence degree of the fluid to be cooled can be further increased, the heat exchange coefficient of the cooling core body 1 is increased, and the heat exchange efficiency is improved.
Through the design of the structure, the heat exchange efficiency of the cooling core body 1 can be comprehensively increased by increasing the heat exchange area, the fluid flow, the flow rate, the heat exchange coefficient and the heat exchange quantity, namely, the required heat exchange volume is smaller under the same heat load requirement; therefore, the volume of the special-shaped plate-fin cooler can be reduced, and the enterprise cost is reduced.
Specifically, the axis of the spiral structure of the flow channel 1311 is parallel to the plate surface of the partition plate 11.
Preferably, as shown in fig. 2, the spiral radius of the plurality of flow channels 1311 on the pipe 131 increases in the same direction. By setting the increasing directions of the spiral radii of the flow channels 1311 on the pipeline 131 to be in the same direction, the joint of the two flow channels 1311 is communicated with the small end of the spiral radius of one flow channel 1311 and the large end of the spiral radius of the adjacent flow channel 1311, and the difference of the spiral radii of the flow channels 1311 is the largest, so that the turbulence degree of the flow to be cooled can be increased to the greatest extent, the heat exchange coefficient is improved, and the heat exchange efficiency of the heat exchange core 1 is increased.
Preferably, as shown in fig. 2, several pipes 131 are arranged side by side; the spiral radius of the flow channels 1311 on adjacent pipes 131 increases in opposite directions. The pipelines 131 are arranged in parallel, so that the production process is simple, and the practicability is high; on the other hand, more ducts 131 may be arranged in a limited plate surface area, increasing the heat exchange efficiency of the cooling core 1. By setting the spiral radius increasing direction of the plurality of flow channels 1311 on the adjacent pipes 131 to be reverse, the compactness of the arrangement of the plurality of flow channels 1311, that is, the maximum number of the pipes 131 arranged in a limited plate surface area, increases the heat exchange efficiency of the cooling core 1, and optimizes the arrangement of the plurality of pipes 131.
Preferably, as shown in fig. 2, a plurality of vertical baffles 15 are provided between adjacent pipes 131; an included angle alpha is formed between the plate surface of the baffle 15 and the flow direction of the cooling fluid, and the angle alpha is more than 0 degrees and less than or equal to 90 degrees; as shown in fig. 4, the baffle 15 is provided with a plurality of through holes 151 through which cooling fluid flows. Specifically, the height of the baffle 15 is equal to the height of the channel 12; the baffle 15 is provided with a plurality of through holes 151 at uniform intervals.
By providing the baffle 15 with the plurality of through holes 151, first, the flow of the cooling fluid in the through holes 151 is similar to the flow around the pipe, and when the velocity of the cooling fluid is very high, the viscous diffusion boundary layer near the inner wall surface of the through holes 151 is very thin, thereby generating turbulence. By increasing the turbulence of the cooling fluid in the channels 12, the heat transfer coefficient of the profiled plate-fin cooler can be increased; the heat exchange efficiency of the heat exchange core body 1 is increased; secondly, can also provide the promotion space for increasing the velocity of flow of cooling fluid, on the one hand can improve heat exchange efficiency, on the other hand can further increase the turbulent flow degree of fluid, synthesizes the heat exchange efficiency who improves cooling core 1. Third, the through holes 151 are uniformly arranged at intervals, so that the turbulence effect on the cooling fluid is uniform, the heat exchange coefficient of the cooling core body 1 is improved to the greatest extent, and the cooling efficiency of the irregular plate-fin cooler is improved.
Preferably, as shown in fig. 4, a spoiler 152 for increasing turbulence of the cooling fluid is provided on the through hole 151. Specifically, as shown in fig. 4, the spoiler 152 includes a plurality of spoiler strips 1521; one end of the flow disturbing belt 1521 is fixed on the through hole 151, and the other end can move along with the flow of the cooling fluid; the spoiler 1521 is bendable, and the spoiler 1521 has elasticity; as shown in fig. 5, the spoiler 1521 has a spiral structure; 4 spoiler strips 1521 are uniformly arranged at intervals on the inner edge of the through hole 151.
Through setting up a plurality of vortex area 1521 on through-hole 151, vortex area 1521 can move along with the flow of cooling fluid, consequently can further increase the turbulent flow degree of cooling fluid, improve the heat transfer coefficient of cooling core 1, improve the heat exchange efficiency of abnormal plate wing cooler. Through setting up vortex area 1521 into heliciform structure, can increase the vortex effect of vortex area 1521 to the cooling fluid to a great extent, improve the heat exchange efficiency of abnormal plate wing cooler.
Preferably, as shown in fig. 1, the end of the channel 12 near the thermal head 2 is provided with a first seal 41; as shown in fig. 3, the first seal 41 is provided with a plurality of first openings 411 for communicating a plurality of pipes 131 with the heat inlet seal head 2; a second seal 42 is arranged at one end of the channel 12 close to the hot seal head 3; the second seal 42 is provided with a plurality of second openings (not shown in the figure) for communicating the plurality of pipes 131 with the heat outlet seal head 3; the first seal 41 and the second seal 42 constitute the closing mechanism 4.
With the special-shaped plate-fin cooler provided by the embodiment 1 of the invention, the fluid to be cooled enters the heat inlet seal head 2 from the heat inlet 21 at the left end of the special-shaped plate-fin cooler, then enters the fins 13 in each layer of channels 12 for spiral circulation with spiral radius conversion, then enters the heat outlet seal head 3 at the right end, and flows out of the special-shaped plate-fin cooler through the heat outlet 31; at the same time, the cooling fluid directly enters the channel 12 and circulates in the gap 14, the flowing directions of the cooling fluid and the fluid to be cooled are perpendicular to each other, and the cooling fluid and the fluid to be cooled exchange heat in the circulation process.
Example 2:
as shown in fig. 1, the special-shaped plate-fin cooler provided in embodiment 2 of the present invention includes a cooling core 1 for cooling a fluid to be cooled, a heat inlet end enclosure 2 for flowing in the fluid to be cooled, and a heat outlet end enclosure 3 for flowing out the fluid to be cooled, where the cooling core 1 includes a plurality of channels 12 formed by stacking a plurality of separators 11; the channels 12 are provided with a plurality of fins 13 for circulating a fluid to be cooled; as shown in fig. 6, the fins 13 comprise a plurality of tubes 131 for the passage of the fluid to be cooled; the outer diameter of the plurality of pipes 131 is smaller than the vertical height of the channel 12; the pipe 131 is curved; a gap 14 for the passage of a cooling fluid is left in the channel 12; one end of each of the pipelines 131 is communicated with the heat inlet end socket 2, and the other end is communicated with the heat outlet end socket 3; the channel 12 is provided with a closing mechanism 4 for isolating the gap 14 from being communicated with the hot inlet end enclosure 2 and the hot outlet end enclosure 3; the channel 12 is formed by the upper and lower partition plates 11, the fins 13 and the closing mechanism 4.
Specifically, as shown in fig. 1, the side provided with the heat inlet end enclosure 2 is the left side of the cooling core 1, and the heat outlet end enclosure 3 is arranged on the right side of the cooling core 1; a heat inlet 21 for flowing in the fluid to be cooled is arranged on the heat inlet seal head 2, and the heat inlet 21 is positioned at the lower part of the heat inlet seal head 2; a heat outlet 31 for flowing out the fluid to be cooled is arranged on the heat outlet seal head 3, and the heat outlet 31 is positioned at the upper part of the heat outlet seal head 3; the flowing directions of the fluid to be cooled and the cooling fluid are perpendicular to each other. The separator 11, the fins 13 and the closing mechanism 4 are brazed.
According to the abnormal plate-fin cooler provided by the embodiment 2, the fins 13 are designed to be of the pipeline structure, and the pressure bearing capacity of the pipeline 131 is higher than that of the traditional fins, so that the damage of the high-flow-rate fluid to be cooled to the cooling core body 1 can be reduced, and the applicable pressure bearing range of the abnormal plate-fin cooler is enlarged; the service life of the special-shaped plate-fin cooler is prolonged; the fins 13 are arranged into the bent pipeline, the heat exchange area is higher than that of the traditional fins, and cooling fluid flows through the gaps 14 of the channels 12, so that the heat exchange amount of the fluid to be cooled and the cooling fluid is improved; the heat exchange efficiency of the cooling core body 1 can be improved through the design, namely, the required heat exchange area is smaller under the same heat load requirement, and the cost of enterprises is saved. The design is integrated, the structure of the irregular plate-fin cooler is stable, and the irregular plate-fin cooler has stronger pressure bearing capacity; the application range of the special-shaped plate-fin cooler is enlarged; and the cost of enterprises is saved.
Preferably, as shown in fig. 6, the pipe 131 has a spiral structure with a varying spiral radius. More preferably, as shown in fig. 6, the conduit 131 includes a number of flow channels 1311; the flow channel 1311 has a spiral structure with gradually increasing spiral radius; the plurality of runners 1311 are in series communication to form the conduit 131.
In the special-shaped plate-fin cooler provided by the embodiment 2 of the invention, the first pipeline 131 is designed to be in a spiral structure, and the first pipeline can increase the flow of fluid to be cooled in a limited plate surface area, so that the fluid to be cooled has higher flow heat exchange comprehensive performance in the flowing process, and the heat exchange capacity of the special-shaped plate-fin cooler is increased; secondly, the heat exchange area of the fluid to be cooled is increased; the heat exchange efficiency is improved; thirdly, in the flowing process of the fluid to be cooled, the spiral structure provides centripetal force for the flowing of the fluid, so that the flow speed of the fluid is increased, on one hand, the flow speed of the fluid is high, a certain shearing force is provided, and the scaling tendency is low; on the other hand, the heat exchange coefficient of the cooling core body 1 can be increased, and the heat exchange efficiency is improved; fourth, the fluid to be cooled circulates in the spiral pipe 131, which increases the turbulence degree of the fluid to be cooled, increases the heat exchange coefficient of the cooling core 1, and increases the heat exchange efficiency. The spiral radius of the second pipeline 131 is changed, so that the turbulence degree of the fluid to be cooled can be further increased, the heat exchange coefficient of the cooling core body 1 is increased, and the heat exchange efficiency is improved.
Through the design of the structure, the heat exchange efficiency of the cooling core body 1 can be comprehensively increased by increasing the heat exchange area, the fluid flow, the flow rate, the heat exchange coefficient and the heat exchange quantity, namely, the required heat exchange volume is smaller under the same heat load requirement; therefore, the volume of the special-shaped plate-fin cooler can be reduced, and the enterprise cost is reduced.
Specifically, the axis of the spiral structure of the flow channel 1311 is parallel to the plate surface of the partition plate 11.
Preferably, as shown in fig. 6, the spiral radius of the plurality of flow channels 1311 on the pipe 131 increases in the same direction. By setting the increasing directions of the spiral radii of the flow channels 1311 on the pipeline 131 to be in the same direction, the joint of the two flow channels 1311 is communicated with the small end of the spiral radius of one flow channel 1311 and the large end of the spiral radius of the adjacent flow channel 1311, and the difference of the spiral radii of the flow channels 1311 is the largest, so that the turbulence degree of the flow to be cooled can be increased to the greatest extent, the heat exchange coefficient is improved, and the heat exchange efficiency of the heat exchange core 1 is increased.
Preferably, as shown in fig. 6, adjacent tubes 131 on the fins 13 are of a nested configuration; the end of one tube 131 with the smaller spiral radius is nested from the end of the adjacent tube 131 with the larger spiral radius. By designing adjacent tubes 131 as a nested structure, a greater number of helical tubes 131 can be connected in series on a single fin 13 within a limited baffle 11 area in the direction of fluid flow to be cooled; firstly, the flow of fluid to be cooled is increased, and the heat exchange efficiency of the cooling core body 1 is improved; second, the heat exchange area of the fins 13 is increased, and the heat exchange efficiency of the cooling core 1 is improved.
Preferably, as shown in fig. 6, a plurality of vertical baffles 15 are provided between adjacent fins 13; an included angle alpha is formed between the plate surface of the baffle 15 and the flow direction of the cooling fluid, and the angle alpha is more than 0 degrees and less than or equal to 90 degrees; as shown in fig. 4, the baffle 15 is provided with a plurality of through holes 151 through which cooling fluid flows. Specifically, α=90°, the width of the baffle 15 is equal to the width of the channel 12, and the height of the baffle 15 is equal to the height of the channel 12; the baffle 15 is provided with a plurality of through holes 151 at uniform intervals.
By providing the baffle 15 with the plurality of through holes 151, first, the flow of the cooling fluid in the through holes 151 is similar to the flow around the pipe, and when the velocity of the cooling fluid is very high, the viscous diffusion boundary layer near the inner wall surface of the through holes 151 is very thin, thereby generating turbulence. By increasing the turbulence of the cooling fluid in the channels 12, the heat transfer coefficient of the profiled plate-fin cooler can be increased; the heat exchange efficiency of the heat exchange core body 1 is increased; secondly, can also provide the promotion space for increasing the velocity of flow of cooling fluid, on the one hand can improve heat exchange efficiency, on the other hand can further increase the turbulent flow degree of fluid, synthesizes the heat exchange efficiency who improves cooling core 1. Third, the through holes 151 are uniformly arranged at intervals, so that the turbulence effect on the cooling fluid is uniform, the heat exchange coefficient of the cooling core body 1 is improved to the greatest extent, and the cooling efficiency of the irregular plate-fin cooler is improved.
Preferably, as shown in fig. 4, a spoiler 152 for increasing turbulence of the cooling fluid is provided on the through hole 151. Specifically, as shown in fig. 4, the spoiler 152 includes a plurality of spoiler strips 1521; one end of the flow disturbing belt 1521 is fixed on the through hole 151, and the other end can move along with the flow of the cooling fluid; the spoiler 1521 is bendable, and the spoiler 1521 has elasticity; as shown in fig. 5, the spoiler 1521 has a spiral structure; 4 spoiler strips 1521 are uniformly arranged at intervals on the inner edge of the through hole 151.
Through setting up a plurality of vortex area 1521 on through-hole 151, vortex area 1521 can move along with the flow of cooling fluid, consequently can further increase the turbulent flow degree of cooling fluid, improve the heat transfer coefficient of cooling core 1, improve the heat exchange efficiency of abnormal plate wing cooler. Through setting up vortex area 1521 into heliciform structure, can increase the vortex effect of vortex area 1521 to the cooling fluid to a great extent, improve the heat exchange efficiency of abnormal plate wing cooler.
Preferably, as shown in fig. 1, the end of the channel 12 near the thermal head 2 is provided with a first seal 41; as shown in fig. 3, the first seal 41 is provided with a plurality of first openings 411 for communicating a plurality of pipes 131 with the heat inlet seal head 2; a second seal 42 is arranged at one end of the channel 12 close to the hot seal head 3; the second seal 42 is provided with a plurality of second openings (not shown in the figure) for communicating the plurality of pipes 131 with the heat outlet seal head 3; the first seal 41 and the second seal 42 constitute the closing mechanism 4.
With the special-shaped plate-fin cooler provided by the embodiment 2 of the invention, the fluid to be cooled enters the heat inlet seal head 2 from the heat inlet 21 at the left end of the special-shaped plate-fin cooler, then enters the fins 13 in each layer of channels 12 for spiral circulation with spiral radius conversion, then enters the heat outlet seal head 3 at the right end, and flows out of the special-shaped plate-fin cooler through the heat outlet 31; at the same time, the cooling fluid directly enters the channel 12 and circulates in the gap 14, the flowing directions of the cooling fluid and the fluid to be cooled are perpendicular to each other, and the cooling fluid and the fluid to be cooled exchange heat in the circulation process.
In summary, according to the shaped plate-fin cooler provided by the invention, the fins are designed into the pipeline structure, the pipeline is of the spiral structure with the spiral radius changing, and the gap for cooling fluid to circulate is reserved in the channel, so that the shaped plate-fin cooler has a stable structure and strong bearing capacity; meanwhile, the heat exchange efficiency of the cooling core body can be comprehensively increased by increasing the heat exchange area, the fluid flow, the flow speed, the heat exchange coefficient and the heat exchange quantity, namely, the required heat exchange volume is smaller under the same heat load requirement; the volume of the special-shaped plate-fin cooler is reduced, and the cost of enterprises is reduced.
Those skilled in the art will appreciate that the above-described modifications may be implemented by those skilled in the art in combination with the prior art and the above-described embodiments, and are not described herein. Such modifications do not affect the essence of the present invention, and are not described herein.
The preferred embodiments of the present invention have been described above. It is to be understood that the invention is not limited to the specific embodiments described above, wherein devices and structures not described in detail are to be understood as being implemented in a manner common in the art; any person skilled in the art will make many possible variations and modifications, or adaptations to equivalent embodiments without departing from the technical solution of the present invention, which do not affect the essential content of the present invention. Therefore, any simple modification, equivalent variation and modification of the above embodiments according to the technical substance of the present invention still fall within the scope of the technical solution of the present invention.
Claims (7)
1. The abnormal plate fin cooler comprises a cooling core body for cooling fluid to be cooled, a heat inlet end socket for the fluid to be cooled to flow in and a heat outlet end socket for the fluid to be cooled to flow out, and is characterized in that the cooling core body comprises a plurality of channels formed by stacking a plurality of partition plates; fins are arranged in the channels; the fins comprise a plurality of pipelines for circulating fluid to be cooled; the outer diameter of the plurality of pipelines is smaller than the vertical height of the channel; the pipeline is in a bent shape; a gap for cooling fluid to circulate is reserved in the channel; one end of each pipeline is communicated with the heat inlet end socket, and the other end of each pipeline is communicated with the heat outlet end socket; the channel is provided with a sealing mechanism for isolating the gap from being communicated with the hot inlet end socket and the hot outlet end socket; the channel is composed of the upper and lower partition plates, the fins and the closing mechanism;
wherein a plurality of vertical baffles are arranged between adjacent pipelines; an included angle alpha is formed between the plate surface of the baffle plate and the flow direction of the cooling fluid, and the included angle alpha is more than 0 degrees and less than or equal to 90 degrees; the baffle is provided with a plurality of through holes for cooling fluid to circulate; the through holes are provided with turbulence pieces for increasing turbulence of cooling fluid; the flowing directions of the fluid to be cooled and the cooling fluid are perpendicular to each other.
2. The profiled plate-fin cooler of claim 1, wherein said tubes are of a helical configuration of varying helical radius.
3. The profiled plate-fin cooler of claim 2, wherein said conduit comprises a plurality of flow channels; the flow channel is of a spiral structure with gradually increased spiral radius; and a plurality of flow channels are connected in series to form the pipeline.
4. The profiled plate-fin cooler of claim 3, wherein the spiral radius of the plurality of flow channels on the tube increases in the same direction.
5. The profiled plate-fin cooler of claim 4, wherein a plurality of said tubes are juxtaposed; the spiral radius of a plurality of flow channels on adjacent pipelines is increased in opposite directions.
6. The profiled plate-fin cooler of claim 4, wherein adjacent said flow channels on said tube, the end of one of said flow channels having the smaller spiral radius telescoping from the end of the other of said flow channels having the larger spiral radius.
7. The profiled plate-fin cooler of claim 1, wherein a first seal is provided at an end of the channel proximate the thermal inlet head; the first seal is provided with a plurality of first openings for communicating a plurality of pipelines with the hot inlet seal head; a second seal is arranged at one end of the channel, which is close to the hot-out seal head; the second seal is provided with a plurality of second openings for communicating a plurality of pipelines with the hot-out seal head; the first seal and the second seal form the closing mechanism.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811638165.6A CN109556441B (en) | 2018-12-29 | 2018-12-29 | Abnormal plate-fin cooler |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811638165.6A CN109556441B (en) | 2018-12-29 | 2018-12-29 | Abnormal plate-fin cooler |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109556441A CN109556441A (en) | 2019-04-02 |
| CN109556441B true CN109556441B (en) | 2023-09-01 |
Family
ID=65871992
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811638165.6A Active CN109556441B (en) | 2018-12-29 | 2018-12-29 | Abnormal plate-fin cooler |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109556441B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114632847B (en) * | 2022-03-03 | 2023-09-12 | 巨翊科瑞医疗技术(上海)有限公司 | Preparation method of inner coil pipe of heat exchanger and inner coil pipe |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101435669A (en) * | 2008-11-20 | 2009-05-20 | 西安石油大学 | Internal fin flat tube shell and tube heat exchanger |
| CN101650140A (en) * | 2009-09-11 | 2010-02-17 | 西安石油大学 | Multi-strand spiral flow shell and tubular heat exchanger for fluid outside heat transfer tube |
| CN205919708U (en) * | 2016-08-26 | 2017-02-01 | 无锡博利达换热器有限公司 | Be applied to water chiller of vacuum pump |
| KR20180061905A (en) * | 2016-11-30 | 2018-06-08 | (주) 영인텍 | A multi flow heat exchanger using micro channel tube |
-
2018
- 2018-12-29 CN CN201811638165.6A patent/CN109556441B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101435669A (en) * | 2008-11-20 | 2009-05-20 | 西安石油大学 | Internal fin flat tube shell and tube heat exchanger |
| CN101650140A (en) * | 2009-09-11 | 2010-02-17 | 西安石油大学 | Multi-strand spiral flow shell and tubular heat exchanger for fluid outside heat transfer tube |
| CN205919708U (en) * | 2016-08-26 | 2017-02-01 | 无锡博利达换热器有限公司 | Be applied to water chiller of vacuum pump |
| KR20180061905A (en) * | 2016-11-30 | 2018-06-08 | (주) 영인텍 | A multi flow heat exchanger using micro channel tube |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109556441A (en) | 2019-04-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Wang et al. | Heat transfer and friction correlation for compact louvered fin-and-tube heat exchangers | |
| WO2016095872A1 (en) | Arc-shaped plate heat exchanger | |
| CN109163586B (en) | Spiral runner printed circuit board heat exchanger | |
| EP3196585A1 (en) | Heat exchanger with center manifold | |
| US11473854B2 (en) | Heat exchanger with adjacent inlets and outlets | |
| CN111059929A (en) | Novel micro-channel heat exchanger with fin structure | |
| CN111092277A (en) | Honeycomb type micro-channel cooling plate for battery thermal management and application thereof | |
| CN109556441B (en) | Abnormal plate-fin cooler | |
| CN115183609A (en) | Heat exchanger core and printed circuit board type heat exchanger comprising same | |
| CN106500532B (en) | A kind of spiral microchannel heat exchanger | |
| CN219843029U (en) | Cooling structure of cooler, battery pack and vehicle | |
| CN207540401U (en) | A kind of incorgruous finned tube baffling shell-and-tube heat exchanger | |
| CN110718727A (en) | Power battery cooling structure | |
| CN214792027U (en) | Multi-process horizontal pipe internal condensation heat exchanger capable of achieving split liquid drainage | |
| CN210838024U (en) | Power battery cooling structure | |
| CN212179365U (en) | Cooling device of air-cooled water-cooled oil cooler | |
| CN210717655U (en) | Air-lubricating oil surface type radiator | |
| CN109520353B (en) | Novel plate-fin cooler applied to combine harvester | |
| CN108955319B (en) | Box type heat exchanger | |
| CN113865383A (en) | Plate-fin air cooler structure and air cooler | |
| CN110425570B (en) | Air-lubricating oil surface type radiator | |
| CN209263756U (en) | Special-shaped strip-fin oil cooler | |
| CN219064239U (en) | Plate heat exchanger and air conditioner | |
| CN219693938U (en) | Coil pipe assembly of high-flow-velocity heat exchanger | |
| CN217654336U (en) | Air-drainage type natural convection turbulent flow inclined fin efficient cooler |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| PE01 | Entry into force of the registration of the contract for pledge of patent right | ||
| PE01 | Entry into force of the registration of the contract for pledge of patent right |
Denomination of invention: Irregular plate fin cooler Granted publication date: 20230901 Pledgee: Bank of China Wuxi Binhu sub branch Pledgor: WUXI MASHAN YONGHONG HEAT EXCHANGER Co.,Ltd. Registration number: Y2024980011059 |