CN114111393B - Heat exchange plate based on supercritical working medium, core body and printed circuit board type heat exchanger - Google Patents
Heat exchange plate based on supercritical working medium, core body and printed circuit board type heat exchanger Download PDFInfo
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- CN114111393B CN114111393B CN202111404594.9A CN202111404594A CN114111393B CN 114111393 B CN114111393 B CN 114111393B CN 202111404594 A CN202111404594 A CN 202111404594A CN 114111393 B CN114111393 B CN 114111393B
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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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0081—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element
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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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary
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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
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
- F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
- F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
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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
- F28F2215/00—Fins
- F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
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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
- F28F2215/00—Fins
- F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Cooling Or The Like Of Electrical Apparatus (AREA)
Abstract
The application discloses a heat exchange plate based on supercritical working medium, a core body and a printed circuit board type heat exchanger, belonging to the technical field of heat exchange devices, and the technical scheme is as follows: the wing-shaped fin areas, the S-shaped fin areas and the diamond-shaped fin areas are sequentially arranged according to the physical property change curve of the supercritical working medium, and fins in each fin area are arranged in a staggered mode; or sequentially arranging a basic fin area, an encryption fin area and a sparse fin area according to the physical property change curve of the supercritical working medium, wherein fins in each fin area are arranged in a staggered mode. The application sets the combined heat exchange plate structure according to the change curve of the physical properties of the supercritical fluid, is suitable for the heat exchange process of different stages when the thermal physical properties of the supercritical fluid are changed along with the temperature, and improves the comprehensive heat exchange performance of the fluid.
Description
Technical Field
The application relates to the technical field of heat exchange devices, in particular to a heat exchange plate based on supercritical working medium, a core body and a printed circuit board type heat exchanger.
Background
At present, the flow channel structure of the printed circuit board type heat exchanger comprises continuous flow channels such as straight channels, Z-shaped channels and the like, and discontinuous channels such as S-shaped channels, airfoil-shaped channels and the like. Changing the channel structure can have a great influence on the heat exchange and pressure drop performance of the printed circuit board type heat exchanger. Compared with the continuous channel, the discontinuous channel has the cost of small reduction of heat exchange performance, and the pressure drop loss is greatly reduced, so that the discontinuous channel gradually becomes a channel type with better comprehensive heat exchange performance.
The working medium generally enters a supercritical state when being heated and gasified under a high-pressure condition, the thermophysical parameters of the working medium are changed drastically near a quasi-critical point in the process, the constant-pressure specific heat capacity is increased and reduced rapidly before and after the quasi-critical temperature, the heat exchange capacity required by the fluid in the quasi-critical area is greatly increased, and higher requirements are put on the heat exchange capacity of the channel. After the fluid enters the supercritical state, the local heat exchange coefficient is reduced, and meanwhile, the density and viscosity are reduced, so that the flow speed of the fluid is increased, and further, the resistance pressure drop loss is increased, and therefore, compared with the heat exchange performance, the pressure drop loss of the channel is more concerned.
The conventional discontinuous printed circuit board type heat exchanger generally adopts the conventional channel structure with the same fins, the same spacing and the same arrangement form, the fin type and the arrangement form are single, so that the channel cannot adapt to the change of supercritical fluid, corresponding optimization cannot be provided according to the requirements of different areas of the fluid in the transcritical gasification process, the heat exchange performance of the channel is further influenced, and the integral heat exchange effect of the channel is poor or the resistance pressure drop is high.
Disclosure of Invention
Aiming at the defects existing in the prior art, the application aims to provide a heat exchange plate, a core body and a printed circuit board type heat exchanger based on a supercritical working medium, wherein a combined heat exchange board structure is arranged according to a physical property change curve of the supercritical working medium, so that the heat exchange process of different stages when the thermal physical property of the supercritical fluid working medium changes along with temperature is adapted, and the comprehensive heat exchange performance of the fluid is improved.
In order to achieve the above object, the present application is realized by the following technical scheme:
in a first aspect, an embodiment of the present application provides a heat exchange plate based on a supercritical working medium, wherein airfoil fin regions, S-shaped fin regions and diamond-shaped fin regions are sequentially arranged according to a physical property change curve of the supercritical working medium, and fins in each fin region are arranged in a staggered manner.
As a further implementation manner, the airfoil fin region is arranged in a region before the quasi-critical point, the S-shaped fin region is arranged in a region with a sharp change of physical properties of the quasi-critical point, and the diamond-shaped fin region is arranged in a region after the quasi-critical point.
As a further implementation mode, symmetrical wing-shaped fins are arranged in the wing-shaped fin area, sinusoidal S-shaped fins are arranged in the S-shaped fin area, and fish-shaped bionic fins are arranged in the diamond-shaped fin area.
In a second aspect, the embodiment of the application also provides a heat exchange plate based on the supercritical working medium, wherein the basic fin area, the encrypted fin area and the sparse fin area are sequentially arranged according to the physical property change curve of the supercritical working medium, and fins in each fin area are arranged in a staggered mode.
As a further implementation manner, the basic fin region is arranged in a region before the quasi-critical point, the encrypted fin region is arranged in a region with severe change of physical properties of the quasi-critical point, and the sparse fin region is arranged in a region after the quasi-critical point.
As a further implementation, the fins in each fin region are airfoil fins, and the degree of density of the airfoil fins in each fin region is different.
As a further implementation, the fin pitch of the encryption fin region relative to the base fin region along the flow direction is reduced by 10% -50%; the fin pitch of the sparse fin region in the flow direction is increased by 10% -50% relative to the base fin region.
In a third aspect, an embodiment of the present application further provides a heat exchange core based on a supercritical working medium, including at least one heat exchange plate based on a supercritical working medium.
As a further implementation mode, the heat exchange plate based on the supercritical working medium is fixedly laminated with the straight channel heat exchange plate or the Z-shaped channel heat exchange plate to form a core structure.
In a fourth aspect, an embodiment of the present application further provides a printed circuit board heat exchanger based on a supercritical working medium, which includes the heat exchange core based on the supercritical working medium.
The beneficial effects of the application are as follows:
(1) Compared with the traditional discontinuous channels which adopt the same fins, the same intervals and the same arrangement form in the whole process, the application can adapt to the heat exchange process of different stages when the thermal physical property of the supercritical fluid working medium changes along with the temperature, and improves the comprehensive heat exchange performance of the fluid.
(2) The application adopts the wing-shaped fins with moderate heat exchange performance in the areas with low temperature, high density and low flow rate of the fluid and slow and uniform change of physical property parameters, thereby maintaining higher heat exchange capability and lower pressure drop; near a quasi-critical point of a supercritical region with severe variation of thermal physical parameters such as density, viscosity, heat conductivity coefficient, specific heat capacity and the like, the structure of the S-shaped fins is used for strengthening fluid disturbance and damaging a thermal boundary layer, so that the heat exchange quantity of the fluid is increased, and the heat exchange quantity requirement caused by severe increase of the specific heat capacity is met, so that the heat exchange performance of the fluid is improved to the greatest extent; and diamond fins with lowest pressure drop resistance are adopted in the areas with low thermophysical parameters and stable change in high temperature, low density and high flow rate of the fluid, so that the impact effect of the working fluid on the wall surface is reduced, and the pressure drop loss caused by the high flow rate condition is reduced.
(3) The application adopts the wing-shaped fins which are arranged conventionally in the area with low temperature, high density and low flow velocity of the fluid and slow and uniform change of physical property parameters, thereby maintaining higher heat exchange capability and lower pressure drop; in the vicinity of a quasi-critical point of a supercritical region in which the thermal physical parameters such as density, viscosity, heat conductivity coefficient, specific heat capacity and the like are changed drastically, encryption is performed by reducing the fin spacing, so that the heat exchange area is increased, and the heat exchange requirement caused by the drastic increase of the specific heat capacity in the supercritical state is met; in the areas of high temperature, low density and high flow rate of the fluid, which have lower thermophysical parameters and stable change, the fin spacing is increased, the number of fins in the flowing area is reduced, the impact effect of the working fluid on the wall surface is weakened, and the pressure drop loss caused by the high flow rate condition is reduced.
(4) The channel structure of the application is flexible, when working fluid flows through wing sections, S-shaped and diamond-shaped fin areas with different structural characteristics and heat exchange and pressure drop performances, different flow pattern characteristics and disturbance forms can be generated, thereby being suitable for heat exchange processes of different stages when the thermal physical properties of the supercritical fluid working fluid are transformed along with temperature; or the fin density degree can be adjusted by freely changing the fin spacing, and the range of the encryption and sparse areas can be freely adjusted by changing the number of the encryption and sparse fins so as to be convenient for adjusting different types of fluids; the fin distance of the encryption fin area relative to the basic fin area along the flowing direction is reduced by 10% -50%; the fin spacing of the sparse fin area along the flow direction is increased by 10% -50% relative to the basic fin area, the range can improve the thermodynamic hydraulic performance under the condition that the fluid flow pattern is relatively stable, and the channel structure can have too strong or too weak influence on the flow form when exceeding the range, so that the comprehensive heat exchange performance is deteriorated.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application.
FIG. 1 is a perspective view of a first embodiment of the present application;
FIG. 2 is a plan view of a first embodiment of the application;
FIG. 3 is a perspective view of an airfoil-S-diamond fin structure for one cycle in accordance with an embodiment of the present application;
FIG. 4 is a plan view of an airfoil-S-diamond fin structure for one cycle in accordance with an embodiment of the present application;
FIG. 5 (a) is a schematic illustration of a staggered distribution of airfoil fins according to a first embodiment of the application;
FIG. 5 (b) is a schematic diagram showing staggered distribution of S-shaped fins according to the first embodiment of the application;
FIG. 5 (c) is a schematic diagram showing a staggered distribution of diamond fins according to the first embodiment of the present application;
FIG. 6 is a schematic view of an S-shaped diamond-shaped fin heat exchange plate in one cycle according to a first embodiment of the present application;
FIG. 7 is a perspective view of a second embodiment of the present application;
FIG. 8 is a plan view of a second embodiment of the present application;
FIG. 9 is a perspective view of a heat exchange plate according to a second embodiment of the present application in one cycle;
FIG. 10 is a plan view of a heat exchanger plate according to a second embodiment of the present application in one cycle;
FIG. 11 is a schematic illustration of a staggered distribution of airfoil fins according to a second embodiment of the application;
fig. 12 is a schematic view of a heat exchange core structure according to a third embodiment of the present application.
The fin comprises a wing-shaped fin area 1, an S-shaped fin area 2, a diamond-shaped fin area 3, a basic fin area 4, an encryption fin area 5, an encryption fin area 6 and a sparse fin area.
Detailed Description
Embodiment one:
the embodiment provides a heat exchange plate based on a supercritical working medium, which is a component part of a printed circuit board type heat exchanger, and as shown in fig. 1 and 2, an airfoil fin area 1, an S-shaped fin area 2 and a diamond fin area 3 are sequentially arranged according to a physical property change curve of the supercritical working medium.
Supercritical fluids are a special state between gaseous and liquid states into which a fluid enters when the fluid is at a temperature and pressure above its critical temperature and critical pressure. The physical properties of the supercritical fluid are changed drastically near the critical point, the dynamic viscosity, the thermal conductivity and the density are reduced rapidly with the increase of the temperature, and the specific heat capacity at a constant pressure is increased to a peak value suddenly and then reduced rapidly.
According to the whole-course thermophysical property change rule of the supercritical fluid working medium in the channel, a plurality of wing-shaped fins, namely wing-shaped fin areas 1, are distributed from the inlet to the near-critical point section; a plurality of S-shaped fins are distributed on the section of the physical property intense change before and after the quasi-critical point in the supercritical region, namely an S-shaped fin region 2; and a plurality of diamond-shaped fins are distributed from the quasi-critical point to the outlet section, namely diamond-shaped fin areas 3.
In this embodiment, the length direction of the heat exchange plate is the flow direction of the supercritical fluid working medium, and the fins in each fin region are arranged in a staggered manner along the length direction of the heat exchange plate and are periodically distributed along the width direction of the heat exchange plate.
Taking a flow channel structure in one period as an example for a detailed description, as shown in fig. 3 and fig. 4, the wing-shaped fins are arranged at the inlet section of the channel, and the wing-shaped fins with relatively low temperature, relatively high density, relatively low flow velocity and slow change of thermal physical parameters can be regarded as conventional single-phase heat exchange, so that the wing-shaped fins with relatively high heat exchange capability and relatively low pressure drop in the fin type are adopted.
In this embodiment, the airfoil fin is any one of the symmetrical type of the NACA series of airfoil fins, such as the NACA0025 type of airfoil fin. The wing-shaped fin has moderate heat exchange performance and pressure drop loss by virtue of a streamline structure with a wide head and a narrow tail.
The S-shaped fin is arranged in the middle section of the channel, and according to the thermal physical property change curve of the supercritical fluid working medium, the fluid is positioned near the quasi-critical point, namely, the fluid enters the supercritical region, the specific heat capacity is rapidly increased, and the heat required by temperature rise is greatly increased, so that the S-shaped fin with relatively strongest heat exchange capacity is adopted.
Preferably, the S-shaped fins are sinusoidal S-shaped fins, the sinusoidal S-shaped fins are improved based on Z-shaped channels with the bending angle of 52 degrees, and the heat exchange performance and the pressure drop loss are the highest.
The diamond fins are positioned at the outlet section of the channel, the supercritical fluid at the outlet section has higher temperature, lower density, higher flow velocity and lower heat exchange effect; to reduce the pressure drop loss due to high flow rates, diamond fins are used. The diamond fins are fish-shaped bionic fins according to the drag reduction appearance of the sisal, the head impact of the wing-shaped fins is improved, and the heat exchange performance and the pressure drop loss are the lowest. Compared with the whole process adopting wing fins, the heat exchange plate structure can raise the temperature of a heat exchange outlet by 8.15%, and the convection heat exchange coefficient by 18.72%; compared with the whole process adopting the S-shaped fins, the heat convection coefficient can be reduced by 2.99%, and the pressure drop loss can be reduced by 60.66%.
Further, the area ranges, the fin distribution number and the distribution density degree of the airfoil fin region 1, the S-shaped fin region 2 and the diamond fin region 3 can be adjusted according to the thermal property curve difference of the supercritical fluid and the emphasis on the heat exchange or pressure drop performance of the fluid.
The heat exchange plate structure shown in fig. 6 is not provided with the wing-shaped fin area 1, so that the area range of the S-shaped fin area 2 and the diamond-shaped fin area 3 is enlarged, and the temperature rise is faster and the heat exchange effect is stronger due to the S-shaped fins used in the starting section, so that the outlet temperature can be increased by 2.74% compared with the wing-shaped-S-shaped-diamond structure, the heat exchange amount per unit area can be increased by 1.96%, and the pressure drop is also increased and the increase reaches 21.25%.
Further, as shown in fig. 5 (a) -5 (c), the distance La between adjacent fins in different rows along the flow direction is the fin length, the distance Lb between adjacent fins in the same row is twice the fin length, and the distance Lc between two adjacent fins perpendicular to the flow direction is the fin width, so that the uniformity of fin arrangement and the continuity of the influence on the fluid flow are maintained.
Parameters such as La, lb, lc, fin size and the like can be increased or decreased according to the use requirement so as to encrypt or sparse fin distribution, and the purposes of enhancing heat exchange or reducing pressure drop loss are further realized.
Compared with the traditional discontinuous channels which all adopt the same fins, the same spacing and the same arrangement form in the whole process, the embodiment fully adapts to the development trend of the thermal physical properties of the supercritical fluid working medium and the development rule of flow heat exchange, and wing fins with moderate heat exchange performance are adopted in the areas with low fluid temperature, high density and low flow velocity and slow and uniform physical property parameter change, so that higher heat exchange capacity and lower pressure drop are maintained; near a quasi-critical point of a supercritical region with severe variation of thermal physical parameters such as density, viscosity, heat conductivity coefficient, specific heat capacity and the like, the structure of the S-shaped fins is used for strengthening fluid disturbance and damaging a thermal boundary layer, so that the heat exchange quantity of the fluid is increased, and the heat exchange quantity requirement caused by severe increase of the specific heat capacity is met, so that the heat exchange performance of the fluid is improved to the greatest extent; the diamond fins with the lowest pressure drop resistance are adopted in the areas with low thermophysical parameters and stable change in the high temperature, low density and high flow rate of the fluid, so that the impact effect of the working fluid on the wall surface is reduced, and the pressure drop loss caused by the high flow rate condition is reduced; further improving the comprehensive heat exchange performance of the fluid.
Embodiment two:
the embodiment provides a heat exchange plate based on a supercritical working medium, which is a component part of a printed circuit board type heat exchanger, and as shown in fig. 7 and 8, a basic fin area 4, an encryption fin area 5 and a sparse fin area 6 are sequentially arranged according to a physical property change curve of the supercritical working medium.
The fins in the basic fin region 4 defined in this embodiment are arranged conventionally, and the encrypted fin region 5 and the sparse fin region 6 are each dependent on the basic fin region 4, forming a fin distribution form from conventional to dense to sparse. Wherein the fin pitch of the encryption fin area 5 in the flow direction is reduced by 10% -50% relative to the base fin area 4; the fin pitch of the sparse fin region 6 in the flow direction is increased by 10% -50% relative to the basic fin region 4.
The encryption and sparseness above are independent of fin spacing perpendicular to the flow direction.
Preferably, the fins in each fin region are airfoil fins and are arranged in a staggered manner.
Further, the flow channel structure in one cycle is taken as an example for detailed explanation, as shown in fig. 9 and fig. 10, the basic fin area 4 is located at the inlet section of the channel, where the temperature of the working medium is relatively low, the density is high, the flow velocity is low, and the change of the thermal physical parameters is slow, so that the conventional single-phase heat exchange can be regarded as, and therefore, the conventional arrangement form with good heat exchange capability and low pressure drop is used.
The encryption fin is arranged in the middle section of the channel, and according to the thermal physical property change curve of the supercritical fluid working medium, the fluid is positioned near the quasi-critical point, namely, enters the supercritical region, the specific heat capacity is rapidly increased, and the heat required by temperature rise is greatly increased, so that the heat exchange performance can be further improved by carrying out encryption treatment on the fin.
The sparsely arranged fins are positioned at the outlet section of the channel, the supercritical fluid at the outlet section has higher temperature, lower density, higher flow velocity and lower heat exchange effect; to reduce the pressure drop loss due to high flow rates, the pressure drop is reduced by increasing the fin spacing. Compared with the existing heat exchange plate, the heat exchange plate structure of the embodiment has the advantages that the outlet temperature lifting quantity can reach 1.29%, the heat exchange coefficient lifting quantity can reach 3.64%, and meanwhile, the pressure drop lifting is accompanied by 8.62%. Compared with the pressure drop loss in the optimization of most heat exchangers, the pressure drop loss in the embodiment increases exponentially with the improvement of the heat exchange performance, and the pressure drop increase is very low, so that the overall heat exchange performance is improved.
As shown in fig. 11, the pitch of adjacent fins in different rows in the flow direction is La, the pitch of adjacent fins in the same row is Lb, and the pitch of two adjacent fins perpendicular to the flow direction is Lc. Parameters such as La, lb, lc, fin size and the like can be increased or decreased along with the use requirement so as to encrypt or sparse fin distribution. In the embodiment, la and Lb are changed to encrypt and sparse fins, so that the purposes of enhancing heat exchange or reducing pressure drop loss are further achieved.
According to the thermal physical property rule of the supercritical fluid working medium, the conventional arranged wing-shaped fins are adopted in the areas with low temperature, high density and low flow rate of the fluid and slow and uniform physical property parameter change, so that higher heat exchange capacity and lower pressure drop are maintained; in the vicinity of a quasi-critical point of a supercritical region in which the thermal physical parameters such as density, viscosity, heat conductivity coefficient, specific heat capacity and the like are changed drastically, encryption is performed by reducing the fin spacing, so that the heat exchange area is increased, the thermal boundary layer is destroyed, the heat exchange quantity is improved, the heat exchange quantity requirement caused by the drastic increase of the specific heat capacity in the supercritical state is met, and the heat exchange performance is improved to the greatest extent; in the areas of high temperature, low density and high flow rate of the fluid, which have lower thermophysical parameters and stable change, the fin spacing is increased, the number of fins in the flowing area is reduced, the impact effect of the working fluid on the wall surface is weakened, and the pressure drop loss caused by the high flow rate condition is reduced.
Embodiment III:
the embodiment provides a heat exchange core based on a supercritical working medium, which comprises at least one heat exchange plate based on the supercritical working medium as described in the first embodiment or the second embodiment.
As shown in fig. 12, after the heat exchange plates based on the supercritical working medium and the straight channel heat exchange plates or the Z-channel heat exchange plates are mutually staggered and stacked, the heat exchange core of the printed circuit board type heat exchanger is formed by using a diffusion welding technology.
Embodiment four:
the embodiment provides a printed circuit board type heat exchanger based on a supercritical working medium, which comprises the heat exchange core based on the supercritical working medium.
The above description is only of the preferred embodiments of the present application and is not intended to limit the present application, but various modifications and variations can be made to the present application by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the protection scope of the present application.
Claims (8)
1. The heat exchange plate based on the supercritical working medium is characterized in that an airfoil fin area, an S-shaped fin area and a diamond-shaped fin area are sequentially arranged according to a physical property change curve of the supercritical working medium, and fins in each fin area are arranged in a staggered mode;
the wing-shaped fin area is arranged in the area before the quasi-critical point, the S-shaped fin area is arranged in the area with the severe change of the physical properties of the quasi-critical point, and the diamond-shaped fin area is arranged in the area after the quasi-critical point.
2. The supercritical working medium-based heat exchange plate according to claim 1, wherein the wing-shaped fin area is provided with symmetrical wing-shaped fins, the S-shaped fin area is provided with sinusoidal S-shaped fins, and the diamond-shaped fin area is provided with fish-shaped bionic fins.
3. The heat exchange plate based on the supercritical working medium is characterized in that a basic fin area, an encrypted fin area and a sparse fin area are sequentially arranged according to a physical property change curve of the supercritical working medium, and fins in each fin area are arranged in a staggered mode;
the basic fin area is arranged in the area before the quasi-critical point, the encryption fin area is arranged in the area with the severe change of physical properties of the quasi-critical point, and the sparse fin area is arranged in the area after the quasi-critical point.
4. A supercritical working medium based heat exchange plate according to claim 3 wherein the fins in each fin region are airfoil fins and the degree of density of the airfoil fins in each fin region is different.
5. A supercritical working medium based heat exchange plate according to claim 3 wherein the fin pitch of the encrypted fin region relative to the base fin region in the flow direction is reduced by 10% -50%; the fin pitch of the sparse fin region in the flow direction is increased by 10% -50% relative to the base fin region.
6. A supercritical fluid based heat exchange core comprising at least one supercritical fluid based heat exchange plate according to claim 1 or 3.
7. The supercritical fluid-based heat exchange core according to claim 6, wherein the supercritical fluid-based heat exchange plate is laminated and fixed with a straight channel heat exchange plate or a Z channel heat exchange plate to form a core structure.
8. A printed circuit board heat exchanger based on supercritical working medium, characterized by comprising a heat exchange core based on supercritical working medium according to any one of claims 6-7.
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