Rectangular sawtooth fin heat exchange flow resistance performance test acquisition system and simulation method

Abstract

The invention belongs to the field of rectangular sawtooth fin performance simulation, and relates to a rectangular sawtooth fin heat exchange flow resistance performance test acquisition system and a simulation method. Comprising a flow resistance test unit, a heat exchange test unit and a heat source. Basic data are acquired through a rectangular sawtooth fin heat exchange flow resistance performance test acquisition system, and then heat exchange flow resistance simulation simplification is carried out on the rectangular sawtooth fin through a porous medium. The error between the result of the simulation simplification method and the test result of the plate-fin cold plate and the heat exchanger can be controlled within 10%, the requirements of engineering design analysis can be met, and simulation technical support is provided for scheme design accuracy and rapid iteration.

Description

TECHNICAL FIELD

[0001] The application belongs to the field of rectangular sawtooth fin performance simulation, and relates to a rectangular sawtooth fin heat exchange flow resistance performance test collection system and a simulation method. BACKGROUND

[0002] With the continuous development of chemical industry, shipbuilding, electronic information technology and other industries, the demand for heat exchange is increasing, and the requirement for heat exchange is also increasing. As a commonly used cold plate and internal heat transfer enhancement structure of a heat exchanger, the rectangular sawtooth fin has the advantages of compact structure and good heat transfer performance. With the development of technology, the weight, flow resistance, volume, heat exchange, volume and other indicators of products in various fields are simultaneously proposed. The design precision of the rectangular sawtooth fin is required to be high. However, when the mainstream simulation software is used to directly simulate the rectangular sawtooth fin at present, the number of single-layer fin grids is large (generally more than 50 million under the size of 300mm*350mm*7mm), and the number of multi-layer fin grids is multiplied. The simulation is difficult and the calculation time is long. SUMMARY

[0003] PURPOSE OF THE INVENTION A rectangular sawtooth fin heat exchange flow resistance performance test collection system is proposed, and a rectangular sawtooth fin heat exchange flow resistance performance simulation simplification method with less grid number, high simulation efficiency and small simulation result error is proposed based on the test collection system. The basic data obtained by the rectangular sawtooth fin heat exchange flow resistance performance test collection system is used to simplify the heat exchange flow resistance simulation of the rectangular sawtooth fin through the porous medium.

[0004] TECHNICAL SCHEME A rectangular sawtooth fin heat exchange flow resistance performance test collection system, comprising a flow resistance test unit, a heat exchange test unit and a heat source. The flow resistance test unit comprises a bent panel assembly 6, an O-shaped ring 5, a bent sealing strip 7, an O-shaped ring 5, a bent panel 8 arranged in sequence and tightened by bolts, and a flow resistance fin 9 arranged in the hollow position in the middle of the bent sealing strip 7; the bent panel assembly 6 is provided with a flow resistance working medium inlet end and a flow resistance working medium outlet end; The heat exchange test unit comprises a panel assembly 1, an O-shaped ring 5, a frame sealing strip 2, a partition plate 4, a frame sealing strip 2, an O-shaped ring 5, a panel assembly 1 arranged in sequence and tightened by bolts, and a heat exchange fin 3 arranged in the hollow position in the middle of the frame sealing strip 2; the two side panel assemblies 1 are respectively provided with a cold side working medium inlet end and a cold side working medium outlet end, a hot side working medium inlet end and a hot side working medium outlet end; The working medium inlet enters the flow resistance working medium inlet end on the flow resistance test unit, the front end of the flow resistance working medium inlet end is provided with a flow meter G, and differential pressure sensors ΔP1 are arranged in front and behind the flow resistance test unit; the working medium enters the cold side working medium inlet end of the heat exchange test unit through the flow resistance working medium outlet end, the cold side working medium inlet end is provided with a temperature sensor t0 in front, the working medium flows out through the cold side working medium outlet end, enters the hot side working medium inlet end through the heat source, the cold side working medium outlet end is provided with a temperature sensor t1, the hot side working medium inlet end is provided with a temperature sensor t2, differential pressure sensors ΔP2 are arranged on the two sides of the cold side working medium inlet end and the cold side working medium outlet end, the working medium flows out through the hot side working medium outlet end, enters the working medium outlet, the hot side working medium outlet end is provided with a temperature sensor t3, and differential pressure sensors ΔP3 are arranged on the two sides of the hot side working medium inlet end and the hot side working medium outlet end.

[0005] Further, the selected material of the partition plate 4 should be consistent with the required equivalent fin or have a similar thermal conductivity coefficient; Further, the specifications of the flow resistance fin 9 and the heat exchange fin 3 should be consistent with the required equivalent fin specifications; Further, the hollowed-out positions of the frame sealing strip 2 include the heat exchange fin 3 mounting area and the liquid accumulation cavity, the hollowed-out positions of the bending sealing strip 7 include the flow resistance fin 9 mounting area and the liquid accumulation cavity, the widths of the hollowed-out positions should be consistent with the fin width, and the length of the liquid accumulation cavity should be not less than 1.5 times the diameter of the working medium inlet and outlet; Further, the length of the heat exchange fin 3 and the flow resistance fin 9 should be not less than 20 times the fin dispersion degree, the width of the hollowed-out position of the frame sealing strip 2 and the bending sealing strip 7 in the heat exchange test unit and the flow resistance test unit should be about 3 times the diameter of the working medium inlet and outlet, so as to avoid the influence of uneven flow on the test results; Further, the average thickness of the frame sealing strip 2 and the bending sealing strip 7 should be lower than the height of the heat exchange fin 3 and the flow resistance fin 9 by (0-0.02) mm, so as to avoid the influence of incomplete contact between the fin and the panel on the heat exchange and flow resistance data; Further, the outer dimensions of the panel assembly 1, the frame sealing strip 2 and the partition plate 4 are consistent, the outer dimensions of the bending panel assembly 6, the bending sealing strip 7 and the bending panel 8 are consistent, and it is ensured that the heat exchange test unit and the flow resistance test unit do not leak or have cavity connection after assembly.

[0006] A rectangular sawtooth fin heat exchange and flow resistance performance simulation simplification method, comprising the following steps: The cavity flow resistance of the heat exchange test unit and the flow resistance test unit at different flow rates is measured when the heat exchange fin 3 and the flow resistance fin 9 are not installed in the heat exchange test unit and the flow resistance test unit respectively; The fin-containing flow resistance and heat exchange data of the heat exchange test unit and the flow resistance test unit at different flow rates are measured when the heat exchange fin 3 and the flow resistance fin 9 are installed; According to the cold and hot side working medium inlet and outlet temperature (t0, t1, t2, t3) of the heat exchange test unit, working medium flow (G), size data of the heat exchange fin 3, the volume heat exchange coefficient of the fin of this specification at different flow rates is calculated, and then the Jeng steel formula and the weting formula of the fin of this specification are corrected according to the volume heat exchange coefficient, and the volume heat exchange coefficient of the fin at all flow rates is calculated according to the corrected function, and the above results are assigned to the porous medium; According to the difference between the cavity flow resistance and the fin-containing flow resistance of the heat exchange test unit and the length of the heat exchange fin 3, the corresponding relationship between the flow resistance and the volume flow rate in the flow direction of the fin at a unit size is calculated, and the corresponding relationship between the flow resistance and the volume flow rate in the vertical flow direction is calculated according to the cavity flow resistance, the fin-containing flow resistance and the corresponding relationship between the flow resistance and the volume flow rate in the flow direction of the flow resistance test unit, and the above results are assigned to the porous medium; The porosity of the porous medium is calculated by the flow area / windward area, the density is the fin material density*porosity, the X and Y direction thermal conductivity of the porous medium is the fin thermal conductivity*porosity, and the Z direction thermal conductivity is set to 10000W / m / k; A simulation model is established for the flow resistance test unit, and the flow resistance fin 9 in the simulation model is converted into a solid model with the same outer size, and the porous medium properties calculated above are assigned; and the simulation is performed according to different working conditions of the flow resistance test unit; According to the measured fin-containing flow resistance of the flow resistance test unit at different flow rates, the vertical flow direction flow resistance of the porous medium is corrected; The rectangular zigzag fin in the required simulation plate fin cold plate or heat exchanger is simplified to a solid model with the same outer size, the above corrected porous medium properties are assigned, and the boundary conditions such as inlet and outlet temperature, flow rate, pressure are set, mesh is drawn and simulation is solved.

[0007] The application has the following beneficial effects: The heat exchange characteristic data and the flow resistance characteristic data of the rectangular zigzag fin in each flow direction can be accurately obtained by the performance test collection system built by the flow resistance test unit and the heat exchange test unit, and the performance simulation of the rectangular zigzag fin is simplified; when the original simulation method is used, the number of grids drawn for the single-layer rectangular zigzag fin with the size of 300mm*350mm*7mm is generally more than 50 million, and the simulation time is more than 10 hours, which is time-consuming, but after the simplified method is used, the number of grids drawn for the single-layer rectangular zigzag fin with the size of 300mm*350mm*7mm can be controlled to be about 100 million, and the simulation time can be controlled to be about 30 minutes; in the original simulation scheme, the large multi-layer plate-fin heat exchanger cannot be simulated, and after the simplification, the number of grids can be controlled to be 100-200 million, and the simulation time is 1-2 hours; the simplified scheme can greatly reduce the number of grids and the simulation time of the rectangular zigzag fin in the simulation of the heat exchange and flow resistance performance of the cold plate and the heat exchanger, and improve the simulation feasibility; the error of the simulation simplified method and the test results of the plate-fin cold plate and the heat exchanger can be controlled to be within 10%, which can meet the demand of engineering design analysis and provide simulation technical support for the accuracy and rapid iteration of the scheme design. BRIEF DESCRIPTION OF DRAWINGS

[0008] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the following will briefly introduce the drawings needed to be used in the embodiments of the present application. Obviously, the drawings described below are only some embodiments of the present application, and other drawings can be obtained by those skilled in the art without creative labor on the basis of these drawings.

[0009] Figure 1 is a schematic diagram of a rectangular zigzag fin structure.

[0010] Figure 2 is a flowchart of the embodiment of the present application.

[0011] Figure 3 is a model diagram of a flow resistance test unit.

[0012] Figure 4 is a model diagram of a heat exchange test unit.

[0013] Figure 5 is a test principle diagram of a rectangular zigzag fin heat exchange and flow resistance performance test collection system.

[0014] Figure 6 is a comparison of the flow resistance test data and the simulation results of a heat exchanger.

[0015] Figure 7 is a comparison of the heat exchange test data and the simulation results of a heat exchanger.

[0016] The panel assembly 1, the frame seal 2, the heat exchange fin 3, the baffle 4, the O-shaped ring 5, the bent panel assembly 6, the bent seal 7, the panel 8, and the flow resistance fin 9. DETAILED DESCRIPTION

[0017] In order to make the purpose, technical scheme and advantages of the present application clearer, the technical scheme in the embodiments of the present application will be described in more detail below in combination with the embodiments of the present application. In the examples, the same or similar reference signs represent the same or similar elements or elements having the same or similar functions throughout. The described embodiments are part of the embodiments of the present application, rather than all the embodiments. The examples described below are exemplary and are intended to explain the present application, and cannot be understood as a limitation of the present application. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application. The embodiments of the present application will be described in detail below.

[0018] The present application will be described in detail below in combination with the embodiments with reference to the accompanying drawings.

[0019] S01, a flow resistance test unit is established according to the rectangular sawtooth fin to be simulated, the width of the flow resistance fin 9 in the flow resistance test unit is about three times the diameter of the working medium inlet and outlet of the flow resistance test unit, and the total length of the flow resistance fin 9 is not less than the fin dispersion degree*20; S02, the width of the hollowed-out position of the bent seal 7 is consistent with the width of the flow resistance fin 9, and the length of the liquid accumulation cavity area at both ends of the hollowed-out position of the bent seal 7 should be not less than 1.5 times the diameter of the working medium inlet and outlet; S03, the bent panel assembly 6, the O-shaped ring 5, the bent seal 7, the O-shaped ring 5, and the bent panel 8 are arranged in sequence and tightened by bolts; S04, a heat exchange test unit is established according to the rectangular sawtooth fin to be simulated, the width of the heat exchange fin 3 in the heat exchange test unit is about three times the diameter of the working medium inlet and outlet of the flow resistance test unit, and the total length of the heat exchange fin 3 is not less than the fin dispersion degree*20; S05, the panel assembly 1, the O-shaped ring 5, the frame seal 2, the baffle 4, the frame seal 2, the O-shaped ring 5, and the panel assembly 1 are arranged in sequence and tightened by bolts; S06, the thickness of the bent seal 7 and the frame seal 2 should be consistent, the average thickness of the frame seal 2 and the bent seal 7 should be lower than the height of the heat exchange fin 3 and the flow resistance fin 9 by (0-0.02) mm; the materials selected for the baffle 4, the flow resistance fin 9, and the heat exchange fin 3 should be consistent with the required equivalent fin or have a similar thermal conductivity; S07, as Figure 5As shown, according to the working fluid inlet, flow resistance test unit, heat exchange test unit cold end, heat source, heat exchange test unit hot end, working fluid outlet is connected in turn, flow meter G is required to be arranged in front of the flow resistance test unit, temperature sensors are respectively arranged at the inlet and outlet of the heat exchange test unit cold end and the inlet and outlet of the heat exchange test unit cold end, and are marked as cold end inlet t0, cold end outlet t1, hot end inlet t2 and hot end outlet t3; and a differential pressure sensor is arranged to measure the inlet and outlet pressure difference of the flow resistance test unit (ΔP1), the heat exchange test unit cold end (ΔP2) and the heat exchange test unit hot end (ΔP3); S08, test and record the values of ΔP1, ΔP2 and ΔP3 at different flow rates, and the flow rate range should start from close to 0, and the maximum value should not be less than 4 times the average flow rate calculated in the required simulation project; S09, arrange flow resistance fins 9 and heat exchange fins 3 in the flow resistance test unit and the heat exchange test unit respectively; according to Figure 5 As shown in the test principle diagram, the cold end inlet t0, the cold end outlet t1, the hot end inlet t2, the hot end outlet t3, the flow resistance test unit flow resistance (ΔP1), the heat exchange test unit cold end flow resistance (ΔP2) and the heat exchange test unit hot end flow resistance (ΔP3) are tested and recorded again at different flow rates; S10, calculate the volumetric heat exchange coefficient at different flow rates according to the cold end inlet t0, the cold end outlet t1, the hot end inlet t2 and the hot end outlet t3; the specific calculation process is as follows: calculate the heat exchange according to the inlet and outlet temperatures of the cold and hot sides, calculate the heat transfer effectiveness of the heat exchange test unit according to the heat exchange, and calculate the volumetric heat exchange coefficient according to the heat transfer effectiveness and the heat capacity of the cold and hot sides; and the range of flow rate and volumetric heat exchange coefficient is expanded by correcting the above calculation data according to the Rongshen steel formula and the weting formula; S11, according to the cavity flow resistance of the heat exchange test unit tested in S08 and the flow resistance containing fins tested in S09, the difference between the two is calculated to obtain the flow resistance per unit length in the flow direction at different flow rates; S12, according to the flow resistance results of the flow resistance test unit tested in S08 and S09, the flow resistance perpendicular to the flow direction is preliminarily estimated at different flow rates; S13, the above volumetric heat exchange coefficient and flow resistance at different flow rates are given to the porous medium of FLOEFD, and the porosity of the porous medium is calculated as follows: porosity=((fin height-thickness)*(pitch-thickness)) / (height*pitch); the thermal conductivity in the flow direction and the perpendicular flow direction: porous medium thermal conductivity=fin material thermal conductivity*porosity, the Z direction thermal conductivity is 10000 W / (m*k); S14, establish a simulation model for the flow resistance test unit, wherein the fins are equivalent to entities with the same size, and are given the properties of the porous medium; compare the different flow rates and flow resistance test results used in S09 to modify the flow resistance perpendicular to the flow direction of the porous medium; S15, a simulation model of the required simulated finned plate-fin heat exchanger or cold plate is established, wherein the fins are equivalent to entities with the same outer dimensions, the above-mentioned corrected porous medium properties are given, the required boundary conditions are given, and meshing and simulation calculation are performed, and the output results are obtained; S16, the above-mentioned flow resistance correlation data and volume heat exchange coefficient correlation data are given to the porous medium properties of FLOEFD, the boundary conditions are set, and the performance of the rectangular zigzag fin is simulated.

[0020] S17, the heat exchange and flow resistance test and simulation results of a plate-fin heat exchanger are compared, and the results and deviations are as shown in Figure 6 Figure 7 The outer dimensions of the plate-fin heat exchanger are 358mm*146mm*112.3mm, wherein the core size is 264mm*90mm*80.3mm, there are 43 layers, and the fin specifications are 1.5mm-1mm-1mm-0.15mm (fin height-pitch-dispersion-thickness) and 1.2mm-1mm-1mm-0.15mm (fin height-pitch-dispersion-thickness). When the original scheme is used to draw the mesh only for a single layer of fins, the number of meshes is 15 million; after simplification using the method, the number of heat exchanger meshes is 750,000, and the simulation of a heat exchange flow resistance working condition point only takes 52 minutes. The heat exchange and flow resistance test data of the cold and hot sides from a flow rate of 100L / h to 900L / h are tested, and the flow rate is tested every 50L / h. According to the inlet temperature and flow rate data during the test, the simulation model is brought into the simulation to obtain the simulation results, which are compared with the test results. The error between the heat exchange simulation results and the test results is within 4%, the error between the cold and hot side flow resistance test and simulation results is within 7%, and the error is small, which can meet the needs of simulation verification in the design stage.

[0021] ​In addition, unless otherwise defined, technical terms or scientific terms used in the description of the application shall be understood as having the common meaning to those of ordinary skill in the art to which the application belongs. The words "upper", "lower", "left", "right", "center", "vertical", "horizontal", "inner", "outer" and the like used in the description of the application indicate relative directions or positional relationships, and are not intended to imply that the device or element must have a particular orientation, be constructed and operated in a particular orientation, and the relative positional relationship may change accordingly when the absolute position of the described object changes, and therefore cannot be understood as a limitation on the application. The "first", "second", "third" and the like used in the description of the application are only for the purpose of description, and are used to distinguish different components, and cannot be understood as indicating or implying relative importance. The "one", "a" or "the" and the like used in the description of the application should not be understood as an absolute limitation on the quantity, but should be understood as the presence of at least one. The "includes" or "contains" and the like used in the description of the application means that the elements or objects appearing before the word are covered by the elements or objects listed after the word and their equivalents, and other elements or objects are not excluded.

[0022] In addition, it should be further pointed out that, unless otherwise specified and limited, the "installation", "connection", "connection" and the like used in the description of the application should be understood in a broad sense, for example, the connection can be fixed connection, or detachable connection, or integral connection; can be mechanical connection, or electrical connection; can be directly connected, or indirectly connected through intermediate medium, or the internal communication of two elements, and those skilled in the art can understand the specific meaning of the above-mentioned terms in the application according to the specific circumstances.

[0023] The above is only a specific embodiment of the application and is not used to limit the application. Any skilled person in the art can use the disclosed technical content to make changes or modifications to equivalent embodiments applied to other fields within the spirit and principles of the application, but any simple modification, equivalent change and improvement made to the above embodiments according to the technical essence of the application shall be included in the protection scope of the application.

Claims

1. A test and data acquisition system for the heat transfer resistance performance of rectangular serrated fins, characterized in that, Includes a flow resistance testing unit, a heat exchange testing unit, and a heat source; The flow resistance test unit includes a bent panel assembly, an O-ring, a bent seal, and a bent panel arranged in sequence and tightened with bolts. The flow resistance fins are located in the hollowed-out position in the middle of the bent seal. The bent panel assembly is provided with a flow resistance working fluid inlet end and a flow resistance working fluid outlet end. The heat exchange test unit includes a panel assembly, an O-ring, a frame seal, a partition, a frame seal, an O-ring, and a panel assembly arranged in sequence and tightened with bolts. The frame seal has heat exchange fins in the hollowed-out position in the middle. The two side panel assemblies are respectively provided with a cold side working fluid inlet end and a cold side working fluid outlet end, and a hot side working fluid inlet end and a hot side working fluid outlet end. The working fluid enters the flow resistance working fluid inlet of the flow resistance test unit. A flow meter G is installed at the front end of the flow resistance working fluid inlet. A differential pressure sensor ΔP1 is installed before and after the flow resistance test unit. The working fluid enters the cold side working fluid inlet of the heat exchange test unit through the flow resistance working fluid outlet. A temperature sensor t0 is installed before the cold side working fluid inlet. After flowing out of the cold side working fluid outlet, the working fluid enters the hot side working fluid inlet via a heat source. A temperature sensor t1 is installed at the cold side working fluid outlet. A temperature sensor t2 is installed at the hot side working fluid inlet. Differential pressure sensors ΔP2 are installed on both sides of the cold side working fluid inlet and outlet. After flowing out of the hot side working fluid outlet, the working fluid enters the working fluid outlet. A temperature sensor t3 is installed after the hot side working fluid outlet. Differential pressure sensors ΔP3 are installed on both sides of the hot side working fluid inlet and outlet.

2. The system as described in claim 1, characterized in that, The material selected for the partition should be the same as or have a thermal conductivity close to that of the equivalent fins.

3. The system as described in claim 1, characterized in that, The specifications of the flow resistance fins and heat exchange fins should be consistent with the specifications of the equivalent fins.

4. The system as described in claim 1, characterized in that, The cutouts in the frame seal include the heat exchange fin installation area and the liquid accumulation cavity; the cutouts in the bent seal include the flow resistance fin installation area and the liquid accumulation cavity; the width of the cutouts should be consistent with the fin width; the length of the liquid accumulation cavity should be no less than 1.5 times the diameter of the working fluid inlet and outlet.

5. The system as described in claim 1, characterized in that, The length of the heat exchange fins and flow resistance fins should not be less than fin dispersion * 20; the width of the cutout position of the frame seal and bending seal in the heat exchange test unit and flow resistance test unit should be 3 times the diameter of the working fluid inlet and outlet.

6. The system as described in claim 1, characterized in that, The average thickness of the frame seal and the bent seal should be lower than the height of the heat exchange fins and the flow resistance fins.

7. The system as described in claim 1, characterized in that, The panel assembly, frame seal, and partition have the same outer dimensions. The bent panel assembly, bent seal, and bent panel have the same outer dimensions. It is ensured that the heat exchange test unit and flow resistance test unit do not leak or cross-contamination after assembly.

8. A simplified method for simulating the heat transfer resistance performance of a rectangular sawtooth fin system as described in any one of claims 1-7, characterized in that, Includes the following steps: The cavity flow resistance of the heat exchange test unit and the flow resistance test unit was measured at different flow rates when no heat exchange fins or flow resistance fins were installed in the heat exchange test unit and the flow resistance test unit, respectively. Heat exchange fins and flow resistance fins were installed in the heat exchange test unit and the flow resistance test unit with fins to measure the flow resistance and heat exchange data at different flow velocities. Based on the inlet and outlet temperatures t0, t1, t2, and t3 of the working fluid on the hot and cold sides of the heat exchange test unit, the working fluid flow rate, and the size data of the heat exchange fins, the volumetric heat exchange coefficient of this specification of fin at different flow rates is calculated. Then, the Hinoki Steel formula and Weting formula for this specification of fin are corrected according to the volumetric heat exchange coefficient. The volumetric heat exchange coefficient of this fin at all flow rates is calculated based on the corrected function extension. The above results are then assigned to the porous medium. Based on the difference between the cavity flow resistance and the finned flow resistance of the heat exchange test unit and the length of the heat exchange fin 3, the corresponding relationship between the volumetric flow rate and flow resistance per unit size along the flow direction is calculated; and based on the corresponding relationship between the cavity flow resistance, the finned flow resistance, and the volumetric flow rate and flow resistance along the flow direction of the flow resistance test unit, the corresponding relationship between the volumetric flow rate and flow resistance along the vertical flow direction is calculated; and the above results are assigned to the porous medium. The porosity of the porous medium is calculated by dividing the flow area by the windward area. The density is the density of the fin material multiplied by the porosity. The thermal conductivity of the porous medium in the X and Y directions is the thermal conductivity of the fin multiplied by the porosity. The thermal conductivity in the Z direction is set to 10000 W / m / k. A simulation model of the flow resistance test unit was established, and the flow resistance fins were converted into a solid model with the same outer dimensions as the flow resistance fins, and the porous medium properties calculated above were assigned to them; simulations were performed according to different working conditions of the flow resistance test unit. The vertical flow resistance of porous media is corrected based on the measured finned flow resistance at different flow velocities in the flow resistance test unit. The rectangular serrated fins in the required simulated plate-fin cold plate or heat exchanger are simplified into solid models with consistent outer dimensions. The modified porous media properties are then assigned, and boundary conditions such as inlet and outlet temperature, flow rate, and pressure are set, meshed, and simulated for solution.

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