CN114111393A - Heat exchange plate, core and printed circuit board heat exchanger based on supercritical working medium - Google Patents
Heat exchange plate, core and printed circuit board heat exchanger based on supercritical working medium Download PDFInfo
- Publication number
- CN114111393A CN114111393A CN202111404594.9A CN202111404594A CN114111393A CN 114111393 A CN114111393 A CN 114111393A CN 202111404594 A CN202111404594 A CN 202111404594A CN 114111393 A CN114111393 A CN 114111393A
- Authority
- CN
- China
- Prior art keywords
- heat exchange
- fin
- area
- fins
- working medium
- 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.)
- Granted
Links
Images
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
- 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
-
- 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
-
- 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
-
- 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
-
- 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
Landscapes
- 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 invention discloses a heat exchange plate, a core body and a printed circuit board type heat exchanger based on supercritical working medium, belonging to the technical field of heat exchange devices, and the technical scheme is as follows: sequentially arranging an airfoil fin area, an S-shaped fin area and a diamond fin area according to a physical property change curve of a supercritical working medium, wherein fins in the fin areas are arranged in a staggered mode; or the basic fin area, the encryption 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 the fin areas are arranged in a staggered mode. The combined heat exchange plate structure is arranged according to the physical property change curve of the supercritical fluid working medium, so that the heat exchange process of different stages when the thermal physical property of the supercritical fluid working medium is changed along with the temperature is adapted, and the comprehensive heat exchange performance of the fluid is improved.
Description
Technical Field
The invention relates to the technical field of heat exchange devices, in particular to a heat exchange plate, a core body and a printed circuit board type heat exchanger based on supercritical working media.
Background
At present, the flow channel structure of the printed circuit board type heat exchanger includes a continuous flow channel such as a straight channel and a Z-shaped channel, and a discontinuous flow channel such as an S-shaped channel and an airfoil-shaped channel. Changing the channel structure will have a great impact on the heat exchange and pressure drop performance of the printed circuit board heat exchanger. Compared with a continuous channel, the discontinuous channel has the advantage that the pressure drop loss is greatly reduced at the cost of slightly reducing the heat exchange performance, so that the channel type with better comprehensive heat exchange performance is gradually formed.
The working medium generally enters a supercritical state when being heated and gasified under a high-pressure condition, and thermophysical parameters of the working medium are violently changed near a pseudo-critical point in the process, wherein the specific heat capacity at a constant pressure can be rapidly increased and decreased before and after the pseudo-critical temperature, so that the heat exchange quantity required by fluid in the pseudo-critical area is greatly increased, and higher requirements are provided for the heat exchange capacity of a channel. After the fluid enters a supercritical state, the local heat exchange coefficient is reduced, and the flow velocity of the fluid is improved due to the reduction of the density and the viscosity, so that the resistance pressure drop loss is increased, and therefore the pressure drop loss of a channel is more concerned at the position compared with the heat exchange performance.
The conventional non-continuous printed circuit board type heat exchanger usually adopts the traditional channel structure with the same fins, the same interval and the same arrangement form, the fin type and the arrangement form are single, the channel cannot adapt to the change of supercritical fluid, corresponding optimization cannot be provided according to the requirements of different areas of fluid in the transcritical gasification process, and then the heat exchange performance of the channel is influenced, so that the whole heat exchange effect of the channel is poor or the resistance pressure drop is high.
Disclosure of Invention
Aiming at the defects in the prior art, the invention aims to provide a heat exchange plate, a core body and a printed circuit board type heat exchanger based on a supercritical working medium.
In order to achieve the purpose, the invention is realized by the following technical scheme:
in a first aspect, an embodiment of the present invention provides a heat exchange plate based on a supercritical working medium, in which a wing-shaped fin region, an S-shaped fin region, and a diamond-shaped fin region 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 area is arranged in an area before the pseudo-critical point, the S-shaped fin area is arranged in a physically severe change area of the pseudo-critical point, and the diamond-shaped fin area is arranged in an area after the pseudo-critical point.
As a further implementation mode, the airfoil fin area is provided with symmetrical airfoil fins, the S-shaped fin area is provided with sine S-shaped fins, and the diamond-shaped fin area is provided with fish-shaped bionic fins.
In a second aspect, an embodiment of the present invention further provides a heat exchange plate based on a supercritical working medium, in which a basic fin region, an encryption fin region, and a sparse fin region are sequentially arranged according to a physical property variation curve of the supercritical working medium, and fins in each fin region are arranged in a staggered manner.
As a further implementation manner, the basic fin area is arranged in an area before the pseudo-critical point, the encrypted fin area is arranged in a physically severe change area of the pseudo-critical point, and the sparse fin area is arranged in an area after the pseudo-critical point.
As a further implementation manner, the fins in each fin region are airfoil fins, and the density of the airfoil fins in each fin region is different.
As a further implementation, the fin pitch of the encrypted fin region relative to the base fin region in the flow direction is reduced by 10% -50%; the sparse fin region has a 10% -50% increase in fin spacing in the flow direction relative to the base fin region.
In a third aspect, an embodiment of the present invention 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 supercritical working medium-based heat exchange plate and the straight channel heat exchange plate or the Z-shaped channel heat exchange plate are fixedly stacked to form a core body structure.
In a fourth aspect, an embodiment of the present invention further provides a printed circuit board heat exchanger based on a supercritical working medium, including the heat exchange core based on a supercritical working medium.
The invention has the following beneficial effects:
(1) compared with the traditional non-continuous channels which all adopt the same fins, the same intervals and the same arrangement form in the whole process, the combined heat exchange plate structure is arranged according to the physical property change curve of the supercritical fluid working medium, and can adapt to the heat exchange processes of different stages when the thermal property of the supercritical fluid working medium changes along with the temperature, so that the comprehensive heat exchange performance of the fluid is improved.
(2) The invention adopts the wing-shaped fin with moderate heat exchange performance in the area with low temperature, high density, low flow speed and slow and uniform change of physical parameters of the fluid, and maintains higher heat exchange capability and lower pressure drop; in the vicinity of a pseudo-critical point of a supercritical region with severely changed thermophysical parameters such as density, viscosity, heat conductivity coefficient, specific heat capacity and the like, fluid disturbance is enhanced through the structure of the S-shaped fin, and a thermal boundary layer is damaged, so that the heat exchange quantity of the fluid is increased, the heat exchange quantity requirement caused by the severely increased specific heat capacity is met, and the heat exchange performance of the fluid is improved to the maximum extent; in the areas with low fluid temperature, low density, high flow speed, low thermophysical parameters and stable change, the rhombic fins with the lowest pressure drop resistance are adopted, 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 speed condition is reduced.
(3) The invention adopts the wing fins which are arranged conventionally in the area with low temperature, high density, low flow speed and slow and uniform change of physical parameters of the fluid, and maintains higher heat exchange capability and lower pressure drop; the heat exchange area is increased by reducing the fin spacing near the quasi-critical point of the supercritical region with severely changed thermal physical parameters such as density, viscosity, heat conductivity coefficient, specific heat capacity and the like, so that the heat exchange quantity requirement caused by the severely increased specific heat capacity in the supercritical state is met; the fin spacing is increased in the areas where the fluid is low in temperature, low in density, high in flow speed and thermophysical parameters and stable in change, the number of fins in the flow 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-speed condition is reduced.
(4) The channel structure of the invention is flexible, when the working medium fluid flows through the wing-shaped, S-shaped and diamond-shaped fin areas with different structural characteristics, heat exchange and pressure drop performances, different flow pattern characteristics and disturbance forms can be generated, thereby adapting to the heat exchange process of different stages when the thermophysical property of the supercritical fluid working medium is changed along with the temperature; or the density degree of the fins can be adjusted by freely changing the fin spacing, and the range of the encryption and sparse areas can be adjusted by changing the number of the encryption and sparse fins, so that the adjustment can be conveniently carried out on different types of fluids; the fin spacing of the encryption fin area relative to the base fin area along the flow direction is reduced by 10-50%; the fin spacing of the sparse fin area along the flow direction relative to the basic fin area is increased by 10% -50%, the thermodynamic and hydraulic performance can be improved in the range of ensuring the relatively stable fluid flow pattern, and the influence of the channel structure on the flow form is too strong or too weak, and the comprehensive heat exchange performance is deteriorated.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate exemplary embodiments of the invention and together with the description serve to explain the invention and not to limit the invention.
FIG. 1 is a perspective view of a first embodiment of the present invention;
FIG. 2 is a plan view of a first embodiment of the present invention;
FIG. 3 is a perspective view of an airfoil-S-diamond fin structure of a first embodiment of the present invention during a cycle;
FIG. 4 is a plan view of a airfoil-S-diamond fin structure of a first embodiment of the present invention taken within one cycle;
FIG. 5(a) is a schematic view of a staggered arrangement of airfoil fins according to a first embodiment of the present invention;
FIG. 5(b) is a schematic view of the staggered arrangement of S-shaped fins according to the first embodiment of the present invention;
FIG. 5(c) is a schematic diagram of a staggered arrangement of diamond-shaped fins according to a first embodiment of the present invention;
FIG. 6 is a schematic diagram of the S-shaped and rhombic fin heat exchange plate in one cycle in the first embodiment of the invention;
FIG. 7 is a perspective view of a second embodiment of the present invention;
FIG. 8 is a plan view of a second embodiment of the present invention;
FIG. 9 is a perspective view of a heat exchange plate of a second embodiment of the present invention during a cycle;
fig. 10 is a plan view of a heat exchange plate of a second embodiment of the present invention in one cycle;
FIG. 11 is a schematic view of a staggered arrangement of airfoil fins according to a second embodiment of the present invention;
fig. 12 is a schematic structural view of a heat exchange core in the third embodiment of the present invention.
The fin structure comprises an airfoil fin area, an S-shaped fin area, a rhombic fin area, a basic fin area, a dense fin area and a sparse fin area, wherein the S-shaped fin area is 2, the rhombic fin area is 3, the basic fin area is 4, and the dense fin area is 5.
Detailed Description
The first embodiment is as follows:
the embodiment provides a heat exchange plate based on a supercritical working medium, which is a component 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.
A supercritical fluid is a particular state of a fluid between a gaseous state and a liquid state that the fluid enters at a temperature and pressure above its critical temperature and critical pressure. The physical properties of the supercritical fluid are drastically changed in the vicinity of the critical point, the dynamic viscosity, the thermal conductivity and the density are rapidly decreased as the temperature is increased, and the specific heat capacity at constant pressure is abruptly increased to a peak and then rapidly decreased.
According to the whole-course thermophysical property change rule of the supercritical fluid working medium in the channel, a plurality of airfoil fins, namely an airfoil fin area 1, are distributed from an inlet to a section close to a quasi-critical point; a plurality of S-shaped fins are distributed in the section with violent physical property change before and after the quasi-critical point in the supercritical region, namely an S-shaped fin region 2; a plurality of rhombic fins, namely a rhombic fin area 3, are distributed from the critical point simulation to the outlet section.
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 area 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 the flow channel structure in one period as an example for detailed description, as shown in fig. 3 and 4, the airfoil fins are arranged at the inlet section of the channel, where the working medium has relatively low temperature, high density, low flow velocity and slow change of thermophysical parameters, and can be regarded as conventional single-phase heat exchange, so that the airfoil fins with high heat exchange capacity and low pressure drop in the fin type are adopted.
In the present embodiment, the airfoil fin is any one of NACA series of symmetric airfoil fins, such as NACA0025 airfoil fin. The wing-shaped fin is of a streamline structure with a wide head and a narrow tail, and the heat exchange performance and the pressure drop loss are moderate.
The S-shaped fins are arranged in the middle section of the channel, according to the thermophysical property change curve of the working medium of the supercritical fluid, the fluid is positioned near a quasi-critical point, namely the fluid is about to enter a supercritical region, the specific heat capacity is rapidly improved, and the heat required by temperature rise is greatly increased, so that the S-shaped fins with relatively strongest heat exchange capability are adopted.
Preferably, the S-shaped fins are sine-shaped S-shaped fins, the sine-shaped S-shaped fins are formed by improving Z-shaped channels with bending angles of 52 degrees, and the heat exchange performance and the pressure drop loss are highest.
The rhombic fins are positioned at the outlet section of the channel, and the supercritical fluid at the outlet section has high temperature, low density, high flow speed and low heat exchange effect; in order to reduce the pressure drop loss caused by high flow rate, diamond-shaped fins are adopted. The rhombic fins are fish-shaped bionic fins based on the drag reduction appearance of the swordfish, the head impact of the wing-shaped fins is improved, and the heat exchange performance and the pressure drop loss are the lowest. By adopting the heat exchange plate structure of the embodiment, compared with the whole process of adopting the wing-shaped fins, the temperature of the heat exchange outlet can be increased by 8.15%, and the convective heat transfer coefficient can be increased by 18.72%; compared with the S-shaped fins adopted in the whole process, the convection heat exchange coefficient can be reduced by 2.99%, and the pressure drop loss is reduced by 60.66%.
Further, the area ranges, the fin distribution number and the distribution density degree of the airfoil fin area 1, the S-shaped fin area 2 and the diamond fin area 3 can be adjusted according to the difference of thermophysical property curves of the supercritical fluid and the emphasis on fluid heat exchange or pressure drop performance.
The heat exchange plate structure shown in fig. 6 is not provided with the airfoil fin region 1, so that the area ranges of the S-shaped fin region 2 and the rhombic fin region 3 are increased, and the starting point section uses the S-shaped fins, so that the temperature rise is faster, and the heat exchange effect is stronger, so that the outlet temperature can be increased by 2.74% compared with the airfoil-S-rhombic structure, the heat exchange capacity per unit area can be increased by 1.96%, the pressure drop is increased, and the increase is 21.25%.
Further, as shown in fig. 5(a) -5 (c), the distance La between adjacent fins in different rows in the flow direction is taken as the fin length, the distance Lb between adjacent fins in the same row is taken as twice the fin length, and the distance Lc between two adjacent fins perpendicular to the flow direction is taken as the fin width, so as to maintain the uniformity of fin arrangement and the continuity of the influence of the fin on the fluid flow.
The 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 sparsely distribute the fins, and further achieve the purpose of strengthening heat exchange or reducing pressure drop loss.
Compared with the traditional non-continuous channel which adopts the same fins, the same interval and the same arrangement form in the whole process, the embodiment fully adapts to the development trend of the thermal physical property of the working medium of the supercritical fluid and the development rule of flow heat exchange, and wing-shaped fins with moderate heat exchange performance are adopted in the region with low temperature, high density, low flow speed and slow and uniform physical property parameter change of the fluid, so that higher heat exchange capacity and lower pressure drop are maintained; in the vicinity of a pseudo-critical point of a supercritical region with severely changed thermophysical parameters such as density, viscosity, heat conductivity coefficient, specific heat capacity and the like, fluid disturbance is enhanced through the structure of the S-shaped fin, and a thermal boundary layer is damaged, so that the heat exchange quantity of the fluid is increased, the heat exchange quantity requirement caused by the severely increased specific heat capacity is met, and the heat exchange performance of the fluid is improved to the maximum extent; in the areas where the fluid is low in temperature, low in density, high in flow speed and thermophysical parameters and stable in change, the rhombic fins with the lowest pressure drop resistance are adopted, 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 speed condition is reduced; further improve the comprehensive heat exchange performance of the fluid.
Example two:
the embodiment provides a heat exchange plate based on a supercritical working medium, which is a component 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 area 4 defined in the embodiment are arranged conventionally, and the encrypted fin area 5 and the sparse fin area 6 are both determined relative to the basic fin area 4, and form a fin distribution form from conventional to dense to sparse. Wherein, the fin spacing of the encryption fin area 5 relative to the base fin area 4 in the flow direction is reduced by 10-50%; the fin spacing in the flow direction of the sparse fin region 6 relative to the base fin region 4 is increased by 10% -50%.
Both the above encryption and sparsity are independent of fin spacing perpendicular to the flow direction.
Preferably, the fins in each fin area are airfoil fins and are arranged in a staggered manner.
Further, taking the flow channel structure in one cycle as an example for detailed description, as shown in fig. 9 and 10, the basic fin region 4 is located at the inlet section of the channel, where the working medium has relatively low temperature, high density, low flow rate, and slow change of thermophysical parameters, and can be regarded as conventional single-phase heat exchange, so that a conventional arrangement form with good heat exchange capacity and low pressure drop is used.
The encryption fin is arranged in the middle section of the channel, according to the thermophysical property change curve of the working medium of the supercritical fluid, the fluid is positioned near the quasi-critical point, namely the fluid is about to enter a supercritical region, the specific heat capacity is rapidly improved, and the heat required by temperature rise is greatly increased, so that the heat exchange performance can be further improved by encrypting the fin.
The sparsely arranged fins are positioned at the outlet section of the channel, and the supercritical fluid at the outlet section has higher temperature, lower density, higher flow velocity and lower heat exchange effect; in order to reduce the pressure drop loss caused by high flow velocity, the pressure drop is reduced by increasing the distance between the fins. Compared with the existing heat exchange plate, the heat exchange plate structure of the embodiment has the advantages that the outlet temperature increase amount can reach 1.29%, the heat exchange coefficient increase amount can reach 3.64%, and meanwhile, the pressure drop increase is accompanied by 8.62%. Compared with the pressure drop loss exponentially increased along with the improvement of the heat exchange performance in the optimization of most heat exchangers, the pressure drop increase of the embodiment is very low, so that the overall heat exchange performance is improved.
As shown in fig. 11, the distance between adjacent fins in different rows in the flow direction is La, the distance between adjacent fins in the same row is Lb, and the distance between two adjacent fins perpendicular to the flow direction is Lc. Parameters such as La, Lb, Lc and fin size can be increased or decreased according to the use requirement so as to encrypt or sparsely distribute the fins. In the embodiment, La and Lb are changed to encrypt and thin fins, so that the purpose of heat exchange enhancement or pressure drop loss reduction is further achieved.
According to the thermal-physical law of the working medium of the supercritical fluid, the wing fins which are arranged conventionally are adopted in the region where the fluid is low in temperature, high in density, low in flow speed and slow and uniform in physical parameter change, so that high heat exchange capacity and low pressure drop are maintained; in the vicinity of a pseudo-critical point of a supercritical region with severely changed thermophysical parameters such as density, viscosity, heat conductivity coefficient, specific heat capacity and the like, the fin spacing is reduced for encryption, so that the heat exchange area is increased, a heat boundary layer is damaged, the heat exchange quantity is improved, the heat exchange quantity requirement caused by the severely increased specific heat capacity in a supercritical state is met, and the heat exchange performance is improved to the maximum extent; the fin spacing is increased in the areas where the fluid is low in temperature, low in density, high in flow speed and thermophysical parameters and stable in change, the number of fins in the flow 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-speed condition is reduced.
Example three:
the embodiment provides a heat exchange core body based on a supercritical working medium, which comprises at least one heat exchange plate based on the supercritical working medium 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-shaped channel heat exchange plates are stacked in a staggered manner, a heat exchange core body of the printed circuit board type heat exchanger is formed by using a diffusion welding technology.
Example four:
the embodiment provides a printed circuit board type heat exchanger based on supercritical working medium, which comprises the heat exchange core body based on supercritical working medium in the third embodiment.
The above description is only a preferred embodiment of the present application and is not intended to limit the present application, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, improvement and the like made within the spirit and principle of the present application shall be included in the protection scope of the present application.
Claims (10)
1. The heat exchange plate based on the supercritical working medium is characterized in that a wing-shaped 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.
2. The supercritical fluid-based heat exchange plate according to claim 1, wherein the airfoil fin area is located in the area before the pseudo-critical point, the S-shaped fin area is located in the physically severe change area of the pseudo-critical point, and the diamond fin area is located in the area after the pseudo-critical point.
3. The supercritical fluid-based heat exchange plate according to claim 1, wherein the airfoil fin area is provided with symmetrical airfoil 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.
4. The heat exchange plate based on the supercritical working medium is characterized in that a basic fin area, an encryption 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 the fin areas are arranged in a staggered mode.
5. The supercritical fluid-based heat exchange plate according to claim 4, wherein the base fin area is located in the area before the pseudo-critical point, the encrypted fin area is located in the physically severe change area of the pseudo-critical point, and the sparse fin area is located in the area after the pseudo-critical point.
6. The supercritical fluid-based heat exchange plate according to claim 4, wherein the fins in each fin zone are airfoil fins, and the airfoil fins have different density in each fin zone.
7. The supercritical fluid-based heat exchange plate according to claim 4, characterized in that the fin spacing in the flow direction of the encrypted fin region relative to the base fin region is reduced by 10% -50%; the sparse fin region has a 10% -50% increase in fin spacing in the flow direction relative to the base fin region.
8. Heat exchange core based on supercritical working medium, characterized in that it comprises at least one heat exchange plate based on supercritical working medium according to claim 1 or 4.
9. The supercritical fluid based heat exchange core according to claim 8 wherein the supercritical fluid based heat exchange plates are laminated with straight channel heat exchange plates or Z-channel heat exchange plates to form a core structure.
10. Printed circuit plate heat exchanger based on supercritical working fluids, characterized in that it comprises a heat exchange core based on supercritical working fluids according to any of claims 8 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111404594.9A CN114111393B (en) | 2021-11-24 | 2021-11-24 | Heat exchange plate based on supercritical working medium, core body and printed circuit board type heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111404594.9A CN114111393B (en) | 2021-11-24 | 2021-11-24 | Heat exchange plate based on supercritical working medium, core body and printed circuit board type heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114111393A true CN114111393A (en) | 2022-03-01 |
| CN114111393B CN114111393B (en) | 2023-08-29 |
Family
ID=80371996
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111404594.9A Active CN114111393B (en) | 2021-11-24 | 2021-11-24 | Heat exchange plate based on supercritical working medium, core body and printed circuit board type heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114111393B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114741961A (en) * | 2022-03-30 | 2022-07-12 | 华中科技大学 | Method and system for optimizing wing type fin arrangement structure of printed circuit board type heat exchanger |
| CN114741961B (en) * | 2022-03-30 | 2024-07-02 | 华中科技大学 | Method and system for optimizing wing-shaped fin arrangement structure of printed circuit board type heat exchanger |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102706201A (en) * | 2012-05-29 | 2012-10-03 | 浙江微智源能源技术有限公司 | Micro-channel structure of heat exchanger |
| CN202599189U (en) * | 2012-05-29 | 2012-12-12 | 浙江微智源能源技术有限公司 | Micro-channel structure of heat exchanger |
| CN105547019A (en) * | 2015-12-15 | 2016-05-04 | 西安交通大学 | High temperature and high pressure plate heat exchanger for fins distributed unevenly |
| JP2017141979A (en) * | 2016-02-08 | 2017-08-17 | 株式会社前川製作所 | Heat exchanger and heat pump system |
| CN111059929A (en) * | 2019-11-29 | 2020-04-24 | 华北电力大学 | Novel micro-channel heat exchanger with fin structure |
| CN111735328A (en) * | 2020-07-02 | 2020-10-02 | 浙江高晟光热发电技术研究院有限公司 | Heat exchanger |
| CN112378278A (en) * | 2020-11-16 | 2021-02-19 | 江苏科技大学 | Self-adaptive non-uniform fin plate bundle for heat exchanger and design method of flow channel of self-adaptive non-uniform fin plate bundle |
| CN112944996A (en) * | 2021-02-05 | 2021-06-11 | 中南大学 | Compound heat transfer runner and contain its heat transfer board based on subregion is reinforceed |
| CN113154915A (en) * | 2021-04-21 | 2021-07-23 | 上海新奥节能技术有限公司 | Discontinuous S-shaped fin heat exchange plate and PCHE core body |
-
2021
- 2021-11-24 CN CN202111404594.9A patent/CN114111393B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102706201A (en) * | 2012-05-29 | 2012-10-03 | 浙江微智源能源技术有限公司 | Micro-channel structure of heat exchanger |
| CN202599189U (en) * | 2012-05-29 | 2012-12-12 | 浙江微智源能源技术有限公司 | Micro-channel structure of heat exchanger |
| CN105547019A (en) * | 2015-12-15 | 2016-05-04 | 西安交通大学 | High temperature and high pressure plate heat exchanger for fins distributed unevenly |
| JP2017141979A (en) * | 2016-02-08 | 2017-08-17 | 株式会社前川製作所 | Heat exchanger and heat pump system |
| CN111059929A (en) * | 2019-11-29 | 2020-04-24 | 华北电力大学 | Novel micro-channel heat exchanger with fin structure |
| CN111735328A (en) * | 2020-07-02 | 2020-10-02 | 浙江高晟光热发电技术研究院有限公司 | Heat exchanger |
| CN112378278A (en) * | 2020-11-16 | 2021-02-19 | 江苏科技大学 | Self-adaptive non-uniform fin plate bundle for heat exchanger and design method of flow channel of self-adaptive non-uniform fin plate bundle |
| CN112944996A (en) * | 2021-02-05 | 2021-06-11 | 中南大学 | Compound heat transfer runner and contain its heat transfer board based on subregion is reinforceed |
| CN113154915A (en) * | 2021-04-21 | 2021-07-23 | 上海新奥节能技术有限公司 | Discontinuous S-shaped fin heat exchange plate and PCHE core body |
Non-Patent Citations (1)
| Title |
|---|
| 张明辉: "印刷板式换热器流道结构优化研究", 《化工管理》, pages 113 * |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114741961A (en) * | 2022-03-30 | 2022-07-12 | 华中科技大学 | Method and system for optimizing wing type fin arrangement structure of printed circuit board type heat exchanger |
| CN114741961B (en) * | 2022-03-30 | 2024-07-02 | 华中科技大学 | Method and system for optimizing wing-shaped fin arrangement structure of printed circuit board type heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114111393B (en) | 2023-08-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Zhang et al. | Research progress on structural optimization design of microchannel heat sinks applied to electronic devices | |
| CN108180773A (en) | A kind of interruption fin structure printed circuit board heat exchanger core body | |
| CN207866065U (en) | A kind of interruption fin structure printed circuit board heat exchanger core body | |
| CN109163586B (en) | Spiral runner printed circuit board heat exchanger | |
| CN112378278A (en) | Self-adaptive non-uniform fin plate bundle for heat exchanger and design method of flow channel of self-adaptive non-uniform fin plate bundle | |
| GB2220258A (en) | Heat exchanger | |
| CN207963600U (en) | Flat heat exchange pipe and micro-channel heat exchanger | |
| CN114353564B (en) | Grooved spindle-shaped fin printed circuit board heat exchanger core | |
| CN110864578A (en) | Variable-section airfoil-shaped efficient heat exchange channel for supercritical carbon dioxide PCHE | |
| CN202599189U (en) | Micro-channel structure of heat exchanger | |
| CN114111393B (en) | Heat exchange plate based on supercritical working medium, core body and printed circuit board type heat exchanger | |
| CN106091410B (en) | A kind of solar heat-preservation water tank | |
| CN103090713A (en) | Heat exchanger | |
| CN111397425A (en) | Composite heat exchange device with distributed grooves, convex spherical surfaces and fins | |
| Kawaguchi et al. | The heat transfer and pressure drop characteristics of finned tube banks in forced convection (comparison of the pressure drop characteristics of spiral fins and serrated fins) | |
| CN115218710A (en) | Heat exchange component, heat exchange core and heat exchange device | |
| RU2337295C2 (en) | Plates packet of heat-exchange aparatus | |
| CN204612561U (en) | Boundary layer reversion slitted fin | |
| CN102679789A (en) | Spiral corrugated pipe | |
| CN110470163B (en) | Heat exchanger core with turbulent skin structure and heat exchanger | |
| CN205897928U (en) | Lanced fin at tape alternation inclination | |
| CN105157459B (en) | It is a kind of that the right angle plate-fin heat exchanger that bur is set is condensed for non-azeotrope multicomponent mixture | |
| CN221280046U (en) | Heat exchange channel and heat exchanger | |
| CN108692589B (en) | Cross dendritic reinforced heat exchange fin heat exchanger | |
| CN220823629U (en) | Jet impact cooling micro-channel heat sink based on combination of transverse turbulence and rib column grooves |
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 |