Design method of plate-fin evaporator based on evaporation heat absorption

Abstract

The invention discloses a plate-fin evaporator design method based on evaporation heat absorption, and relates to the technical field of heat exchanger design. Presetting structural data of the evaporator according to performance requirements; the Reynolds number is calculated according to the fin structure parameters and the medium parameters; calculating the total heat transfer coefficient according to the total heat transfer area, heat transfer coefficient, surface efficiency and partition plate thermal resistance of the evaporator; calculating logarithmic heat transfer temperature difference according to performance requirements; under the condition that the required refrigerating capacity is met, the effective heat exchange area needed by the evaporator is calculated according to the logarithm heat transfer temperature difference and the total heat transfer coefficient; and if the effective heat transfer area is smaller than the effective heat exchange area required by the evaporator, adjusting the structural data until the effective heat transfer area is not smaller than the effective heat exchange area required by the evaporator. According to the method, the phase change heat transfer characteristic relational expression and the non-phase-change plate-fin heat exchanger design model are mutually coupled, and the problem that calculation is complex in the plate-fin evaporator design process is solved.

Description

Technical Field

[0001] The present application relates to the technical field of heat exchanger design, and in particular to a design method for a plate-fin evaporator based on evaporative heat absorption. Background Art

[0002] An evaporator is a heat-absorbing device. The refrigerant in a liquid boils at a relatively low temperature, transforming into vapor. This vapor absorbs heat from the object or space being cooled, achieving the cooling effect. Depending on the type of medium being cooled, evaporators are primarily categorized as air-cooling evaporators and liquid-cooling evaporators. Air-cooling evaporators typically use a serpentine tube structure, while liquid-cooling evaporators typically use a shell-and-tube structure. Because traditional evaporators typically utilize a tubular heat transfer structure, this structure is not fully suitable for applications with limited installation space and high cooling requirements.

[0003] Plate-fin heat exchangers feature a fin structure that allows for secondary heat transfer, resulting in a compact structure, large heat transfer area per unit volume, and high heat transfer efficiency. Therefore, when designing an evaporator, using a plate-fin heat transfer structure can further improve the evaporator's cooling efficiency. Plate-fin heat exchangers can also be customized to meet customer specifications, making them suitable for a variety of complex scenarios.

[0004] However, the plate-fin evaporator contains a channel for the cooled medium and a channel for the refrigerant. The cooled medium is a medium without phase change, such as air or liquid to be cooled, while the refrigerant absorbs heat through evaporation phase change. During the evaporator design process, it is necessary to consider both the cooled medium without phase change and the refrigerant with evaporation phase change, which makes the calculations during the design process more complicated. Summary of the Invention

[0005] The embodiment of the present application provides a design method for a plate-fin evaporator based on evaporative heat absorption, which is used to solve the problem of complex calculation caused by considering both the cooled medium without phase change and the refrigerant with evaporative phase change during the evaporator design process in the prior art.

[0006] The present application provides a design method for a plate-fin evaporator based on evaporative heat absorption, including: Obtain design requirements, including medium parameters and performance requirements; Preset the structural data of the evaporator according to the performance requirements, the structural data including the fin structural parameters and the partition structural parameters; Calculate the minimum free flow area and equivalent diameter based on the fin structure parameters; Calculate the mass flow rate based on the minimum free flow area; Calculate the Reynolds number based on the mass flow rate and equivalent diameter; Calculate the heat transfer coefficient of the refrigerant based on the medium parameters; The heat transfer coefficient of the cooled medium is calculated based on the Prandtl number, mass flow rate and medium parameters, and the fin efficiency is calculated based on the heat transfer coefficients of the refrigerant and the cooled medium; Calculate the total heat transfer area based on the primary heat transfer area and secondary heat transfer area of ​​the evaporator; Calculate the effective heat transfer area based on the primary heat transfer area, secondary heat transfer area and fin efficiency; Calculate surface efficiency based on secondary heat transfer area, total heat transfer area and fin efficiency; Calculate the wall thermal resistance based on the partition structure parameters and the primary heat transfer area; Calculate the total heat transfer coefficient based on the surface efficiency, total heat transfer area, wall thermal resistance, heat transfer coefficient of the refrigerant and the heat transfer coefficient of the cooled medium; Calculate the logarithmic heat transfer temperature difference based on performance requirements; Under the condition of meeting the required cooling capacity, the effective heat exchange area required by the evaporator is calculated based on the logarithmic heat transfer temperature difference and the total heat transfer coefficient; Compare the effective heat transfer area with the effective heat exchange area required by the evaporator. If the effective heat transfer area is smaller than the effective heat exchange area required by the evaporator, adjust the structural data until the effective heat transfer area is greater than or equal to the effective heat exchange area required by the evaporator.

[0007] The design method of a plate-fin evaporator based on evaporative heat absorption in this application has the following advantages: 1. The phase change heat transfer characteristic relationship is coupled with the design model of the plate-fin heat exchanger without phase change to solve the problem of complex calculation in the design process of the plate-fin evaporator.

[0008] 2. It improves the cooling efficiency of the evaporator and is applicable to various complex spatial scenarios.

[0009] 3. The plate-fin heat exchanger is used for evaporative cooling, which expands the application field of the plate-fin heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0010] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0011] Figure 1 A flow chart of a design method for a plate-fin evaporator based on evaporative heat absorption provided in an embodiment of the present application.

[0012] Figure 2 This is a schematic structural diagram of the plate-fin evaporator designed in accordance with an embodiment of the present application.

[0013] Figure 3 Schematic diagram of the fin arrangement on the refrigerant side provided in an embodiment of the present application.

[0014] Figure 4 Schematic diagram of the fin arrangement on the cooled medium side provided in an embodiment of the present application. DETAILED DESCRIPTION

[0015] The following will be combined with the drawings in the embodiments of this application to clearly and completely describe the technical solutions in the embodiments of this application. Obviously, the embodiments described are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0016] Figure 1 This is a flow chart of a design method for a plate-fin evaporator based on evaporative heat absorption provided in an embodiment of the present application. This embodiment of the present application provides a design method for a plate-fin evaporator based on evaporative heat absorption, including: S100: Obtain design requirements, which include medium parameters and performance requirements.

[0017] Exemplarily, the medium parameters include the type of medium, evaporation temperature, flow rate, density, specific heat capacity at constant pressure, thermal conductivity, dynamic viscosity, latent heat of vaporization, tension, and dryness, etc. Since the evaporator in the embodiment of the present application includes a cooled medium side and a refrigerant side, it is necessary to obtain the medium parameters of the cooled medium and the refrigerant separately.

[0018] The performance requirements are for the entire evaporator, which mainly include inlet and outlet temperatures, inlet and outlet flow rates, inlet and outlet pressure differences and other data.

[0019] S101, presetting structural data of the evaporator according to performance requirements, the structural data including fin structural parameters and partition structural parameters.

[0020] For example, the fin structural parameters mainly include the fin form, fin pitch, fin height, fin spacing, fin layer number and fin thickness, while the partition structural parameters mainly include partition spacing and partition thickness.

[0021] In addition to the above two parameters, the cover thickness and seal width also need to be obtained.

[0022] The hot side of the evaporator, i.e., the medium being cooled, undergoes no phase change, while the medium on the cold side, i.e., the refrigerant, undergoes a phase change due to evaporation. The refrigerant absorbs heat from the medium being cooled by evaporation, and since the refrigerant primarily absorbs heat through evaporation, its flow pattern has minimal impact on heat transfer. Therefore, straight fins are used on this medium side. Since the medium being cooled transfers heat by convection, the fin type used on this side should be appropriately selected based on the cooling requirements. Specifically, serrated fins are recommended for media with high viscosity and low flow rates, while straight fins are recommended for media with low viscosity and high flow rates.

[0023] S102: Calculate the minimum free flow area and equivalent diameter based on the fin structure parameters.

[0024] For example, the hydraulic radius Defined as the minimum free flow area With wet peritoneum Ratio:

[0025] in, is the width of the fin channel, is the height of the fin channel.

[0026] Equivalent diameter Defined as 4 times the ratio of the minimum free flow area to the wetted perimeter: Straight fins:

[0027] Serrated fins:

[0028] in, is the fin pitch, is the fin height, is the minimum thickness of the fin, is the discontinuity length of the serrated fin.

[0029] Pore ​​size Defined as the minimum free flow area and windward area Ratio:

[0030] S103: Calculate the mass flow rate according to the minimum free flow area.

[0031] For example, the mass flow rate As shown below:

[0032] in, is the mass flow rate.

[0033] S104: Calculate the Reynolds number based on the mass flow rate and the equivalent diameter.

[0034] For example, the Reynolds number As shown below:

[0035] in, is the dynamic viscosity of the fluid.

[0036] S105: Calculate the heat transfer coefficient of the refrigerant according to the medium parameters.

[0037] For example, the heat transfer coefficient of the refrigerant Expressed as:

[0038] in, is the liquid specific heat capacity, is the heat flux density, is the latent heat of vaporization, For pressure, is the liquid phase thermal conductivity, is the liquid density, is the gas phase density.

[0039] S106 , calculating the heat transfer coefficient of the cooled medium according to the Prandtl number, the mass flow rate, and the medium parameters, and calculating the fin efficiency according to the heat transfer coefficients of the refrigerant and the cooled medium.

[0040] For example, the Prandtl number As shown below:

[0041] in, is the specific heat capacity of the fluid, is the thermal conductivity of the fluid.

[0042] Heat transfer coefficient of the cooled medium Expressed as: or

[0043] in, j is the heat transfer factor, Nu is the Nusselt number.

[0044] Fin efficiency As shown below:

[0045] in, is the fin parameter, is the fin height.

[0046] Straight fins:

[0047] Serrated fins:

[0048] in, for and A general term for is the thermal conductivity of the material.

[0049] S107: Calculate the total heat transfer area based on the primary heat transfer area and the secondary heat transfer area of ​​the evaporator.

[0050] For example, the total heat transfer area Expressed as:

[0051] Among them, the primary heat transfer area It is the heat transfer area between the cold and hot fluids between the partitions. The primary heat transfer area of ​​the cold fluid and the hot fluid are the same in value. Secondary heat transfer area That is the area over which hot and cold fluids transfer heat through the fins.

[0052] S108, calculating the effective heat transfer area according to the primary heat transfer area, the secondary heat transfer area, and the fin efficiency.

[0053] For example, the effective heat transfer area Expressed as:

[0054] S109, calculating the surface efficiency based on the secondary heat transfer area, the total heat transfer area, and the fin efficiency.

[0055] For example, the surface efficiency Expressed as:

[0056] S110, calculating the wall thermal resistance based on the partition structure parameters and the primary heat transfer area.

[0057] For example, the wall thermal resistance Expressed as:

[0058] in, is the thickness of the partition, is the thermal conductivity of the partition.

[0059] S111, calculating a total heat transfer coefficient based on the surface efficiency, the total heat transfer area, the wall thermal resistance, the heat transfer coefficient of the refrigerant, and the heat transfer coefficient of the cooled medium.

[0060] For example, the overall heat transfer coefficient K The calculation formula is:

[0061] S112, calculating the logarithmic heat transfer temperature difference according to performance requirements.

[0062] For example, the logarithmic heat transfer temperature difference Expressed as:

[0063] in, is the inlet temperature of the cooled medium, is the outlet temperature of the cooled medium, is the evaporation temperature of the refrigerant.

[0064] S113 , when the required cooling capacity is met, the effective heat exchange area required by the evaporator is calculated according to the logarithmic heat transfer temperature difference and the total heat transfer coefficient.

[0065] For example, the required cooling capacity It can be expressed as:

[0066] in, The effective heat exchange area required by the evaporator to meet the required cooling capacity.

[0067] S114 , comparing the effective heat transfer area with the effective heat exchange area required by the evaporator. If the effective heat transfer area is smaller than the effective heat exchange area required by the evaporator, adjusting the structural data until the effective heat transfer area is greater than or equal to the effective heat exchange area required by the evaporator.

[0068] For example, the effective heat exchange area required by the evaporator when the required cooling capacity is met is calculated by the formula in S108. , then compare ,like , then the design of the evaporator meets the requirements, if , adjust the fin size and partition spacing and redesign and calculate until .

[0069] Furthermore, after adjusting the fin size and baffle spacing, the flow resistance on the cooled medium side also needs to be calculated. Because the refrigerant side primarily undergoes a phase transition process called evaporation, and the refrigerant changes from liquid to gas, the gaps between molecules increase dramatically, leading to a sharp increase in internal pressure. Therefore, it is difficult to accurately calculate the flow resistance on the refrigerant side.

[0070] Flow resistance on the cooled medium side The calculation is as follows:

[0071] in, is the specific volume, is the friction factor, is the flow length.

[0072] Furthermore, after the effective heat transfer area is greater than or equal to the effective heat exchange area required by the evaporator, the thickness of the fins is checked, the thickness of the partitions is checked, and the width of the seal is checked.

[0073] The thickness check of the fin includes: Get the maximum pressure resistance corresponding to the fin material; Calculate the minimum fin thickness based on the maximum pressure resistance, fin structural parameters and allowable stress of the fin material:

[0074] in, is the maximum withstand pressure, is the allowable stress, is the opening weakening coefficient (1 for straight and serrated fins), The additional amount for wall thickness.

[0075] Compare the thickness data in the fin structure parameters with the minimum fin thickness. If the thickness data in the fin structure parameters is greater than the minimum fin thickness, the fin thickness check is passed.

[0076] The calculation methods for the allowable stress of fin materials include: Obtain the fin ultimate strength corresponding to the fin material. The fin ultimate strength includes the fin tensile strength and the fin yield strength. According to the fin tensile strength and fin yield strength and the corresponding safety factors, the fin tensile allowable stress and fin yield allowable stress corresponding to the fin tensile strength and fin yield strength are calculated respectively:

[0077]

[0078] in, and are the fin tensile stress and fin yield stress, respectively. is the fin tensile strength, is the fin yield strength, and are the safety factors of tensile strength and yield strength, respectively.

[0079] The smaller value between the fin tensile allowable stress and the fin yield allowable stress is selected as the final allowable stress.

[0080] Checking the thickness of the partition includes: Get the maximum pressure resistance corresponding to the partition material; Calculate the minimum thickness of the partition according to the maximum pressure resistance, fin structural parameters and allowable stress of the partition material :

[0081] Compare the thickness data in the partition structure parameters with the minimum thickness of the partition. If the thickness data in the partition structure parameters is greater than the minimum thickness of the partition, the thickness check of the partition is passed.

[0082] Checking the width of the seal includes: Get the maximum pressure resistance corresponding to the seal material; Calculate the minimum seal width based on the maximum pressure resistance, seal structural parameters and allowable stress of the seal material :

[0083] in, s is the thickness of the seal.

[0084] Compare the width data in the seal structure parameters with the minimum seal width. If the width data in the seal structure parameters is greater than the minimum seal width, the seal width check is passed.

[0085] Furthermore, the allowable stress calculation method for the partition and seal materials includes: Obtain the material ultimate strength corresponding to the partition and seal materials; Calculate the allowable stress based on the ultimate strength of the material and the corresponding safety factor.

[0086] Design examples: 1. Design requirements Evaporator hot side medium: 65# coolant, flow rate 300L / min, outlet temperature 49.5℃.

[0087] Evaporator cold side medium: R134a, flow rate 0.42kg / s, inlet dryness 0.481, evaporating temperature 44.5℃, superheat 1℃.

[0088] Evaporator heat exchange capacity: ≥35kW.

[0089] Refrigerant side: airtight pressure ≥3.5MPa, withstand pressure ≥5.25MPa.

[0090] Cooling medium side: airtight pressure ≥ 0.86MPa, pressure resistance ≥ 1.29MPa.

[0091] Evaporator structure Figure 2 shown.

[0092] 2. Evaporator core preset structure data According to the performance and size requirements of the hot and cold sides of the evaporator, the evaporator core structure is preset, see Table 1.

[0093] Table 1 Evaporator core structure dimensions

[0094] 3. Medium parameters The physical properties of the cooled medium and refrigerant are shown in Table 2.

[0095] Table 2 Medium parameters under extreme working conditions

[0096] 4. Calculation results Subscript 1 indicates the cooled medium side, and subscript 2 indicates the refrigerant side. The calculation results are as follows: Equivalent diameter: .

[0097] Minimum free circulation area: .

[0098] Mass flow rate: .

[0099] Reynolds number: .

[0100] Prandtl number: .

[0101] According to Weiting's empirical relationship between heat transfer and pressure drop of serrated fins, the heat transfer factor is calculated as: ; Fanning friction factor: .

[0102] Heat transfer coefficient: ; .

[0103] Fin efficiency: .

[0104] Total heat transfer area: .

[0105] Effective heat transfer area: .

[0106] Surface efficiency: .

[0107] Overall heat transfer coefficient: K =3610.4 .

[0108] Logarithmic mean temperature difference: .

[0109] The effective heat exchange area required by the evaporator when the required cooling capacity is met .

[0110] Flow resistance along the way: .

[0111] Conclusion: Comparison and It can be found that > Therefore, the evaporator structure design meets the heat exchange index.

[0112] 5. Strength verification The evaporator's baffles, covers, and seals are made of 3A21-H18 steel, and the fins are made of 3003-H16. Their ultimate strengths are referenced in GB / T 3880.2, "Aluminum and aluminum alloy plates and strips for general industrial use - Part 2: Mechanical properties," as shown in Table 3 below. According to GB 150.1, "Pressure Vessels - Part 1: General Requirements," the safety factors for the tensile strength and yield strength of aluminum alloys are 3.0 and 1.5, respectively.

[0113] Table 3 Ultimate strength of aluminum alloy materials

[0114] Allowable stress of partitions, covers and seals: MPa Allowable stress of fin: MPa MPa Take the minimum value between the two, which is the allowable stress of the fin = =56.67MPa.

[0115] 5.1 Fin thickness check The fins are made of 3003-H16. Based on GB / T 3198 "Aluminum and Aluminum Alloy Foil", the thickness tolerance of aluminum foil with a thickness of 0.009mm to 0.2mm is 5%. The thickness is calculated as follows:

[0116] Where: P The value is 5.25MPa, The value is 1.35mm, The value is 56.67MPa, The value is 1.

[0117] The thickness data in the fin structure parameters is 0.15mm, and the strength meets the requirements.

[0118] 5.2. Check of partition thickness The partition is made of 3A21-H18. Based on GB / T 3880.3 "Aluminum and aluminum alloy sheets and strips for general industrial use - Part 3: Dimensional deviations", the processing deviation of sheets with a thickness of 0.6mm to 0.8mm is 0.05mm. Therefore, the wall thickness correction factor is 0.05mm. The thickness is calculated as follows:

[0119] Where: P The value is 5.25MPa, The value is 1.5mm, The value is 61.67MPa, The value is 0.05mm.

[0120] The thickness data in the partition structure parameters is 0.5mm, and the strength meets the requirements.

[0121] 5.3. Seal width verification The seal is 3A21-H18. Based on GB / T 3880.3 "Aluminum and aluminum alloy sheets and strips for general industrial use - Part 3: Dimensional deviations", the processing deviation of sheets with a thickness of 1.8mm to 2.0mm is 0.09mm. Therefore, the wall thickness correction factor is 0.09mm. The thickness is calculated as follows:

[0122] Where: P The value is 5.25MPa, The value is 2mm, The value is 61.67MPa, The value is 0.09mm.

[0123] The width data in the seal structure parameters is 5mm, and the strength meets the requirements.

[0124] The final designed fin arrangement on the refrigerant side and the cooled medium side is as follows: Figure 3 and 4 shown.

[0125] Although the preferred embodiments of the present application have been described, those skilled in the art may make additional changes and modifications to these embodiments once they have learned the basic creative concept. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments and all changes and modifications that fall within the scope of the present application.

[0126] Obviously, those skilled in the art may make various changes and modifications to this application without departing from the spirit and scope of this application. Thus, if these modifications and variations of this application fall within the scope of the claims of this application and their equivalents, this application is intended to include these modifications and variations.

Claims

1. A design method for a plate-fin evaporator based on evaporative heat absorption, characterized in that: include: Obtaining design requirements, wherein the design requirements include medium parameters and performance requirements; Presetting structural data of the evaporator according to the performance requirements, the structural data including fin structural parameters and baffle structural parameters; Calculating the minimum free flow area and equivalent diameter based on the fin structure parameters; calculating a mass flow rate based on the minimum free flow area; calculating a Reynolds number based on the mass flow rate and the equivalent diameter; Calculating the heat transfer coefficient of the refrigerant according to the medium parameters; Calculating the heat transfer coefficient of the cooled medium according to the Prandtl number, the mass flow rate and the medium parameters, and calculating the fin efficiency according to the heat transfer coefficients of the refrigerant and the cooled medium; Calculate the total heat transfer area based on the primary heat transfer area and secondary heat transfer area of ​​the evaporator; Calculating an effective heat transfer area according to the primary heat transfer area, the secondary heat transfer area, and the fin efficiency; Calculating surface efficiency based on the secondary heat transfer area, the total heat transfer area, and the fin efficiency; Calculating the wall thermal resistance according to the partition structure parameters and the primary heat transfer area; Calculating a total heat transfer coefficient based on the surface efficiency, the total heat transfer area, the wall thermal resistance, the heat transfer coefficient of the refrigerant, and the heat transfer coefficient of the cooled medium; Calculate the logarithmic heat transfer temperature difference based on the performance requirements; Under the condition that the required cooling capacity is met, the effective heat exchange area required by the evaporator is calculated according to the logarithmic heat transfer temperature difference and the total heat transfer coefficient; The effective heat transfer area is compared with the effective heat exchange area required by the evaporator. If the effective heat transfer area is smaller than the effective heat exchange area required by the evaporator, the structural data is adjusted until the effective heat transfer area is greater than or equal to the effective heat exchange area required by the evaporator.

2. The design method of a plate-fin evaporator based on evaporative heat absorption according to claim 1, characterized in that: The refrigerant side uses straight fins, and the cooled medium side uses serrated fins or straight fins according to the viscosity and flow rate of the cooled medium.

3. The design method of a plate-fin evaporator based on evaporation heat absorption according to claim 1, characterized in that: The calculation formula of the overall heat transfer coefficient is: in, K represents the overall heat transfer coefficient, A represents the total heat transfer area, represents the surface efficiency, represents the heat transfer coefficient on the cooled medium side, represents the wall thermal resistance, Indicates the heat transfer coefficient on the refrigerant side.

4. The design method of a plate-fin evaporator based on evaporative heat absorption according to claim 1, characterized in that: After the effective heat transfer area is greater than or equal to the effective heat exchange area required by the evaporator, the thickness of the fins is checked, the thickness of the partitions is checked, and the width of the seal is checked.

5. The design method of a plate-fin evaporator based on evaporation heat absorption according to claim 4, characterized in that: The thickness check of the fin includes: Get the maximum pressure resistance corresponding to the fin material; Calculating the minimum thickness of the fin according to the maximum pressure resistance, the fin structural parameters and the allowable stress of the fin material; The thickness data in the fin structure parameters is compared with the minimum fin thickness. If the thickness data in the fin structure parameters is greater than the minimum fin thickness, the fin thickness check is passed.

6. The design method of a plate-fin evaporator based on evaporative heat absorption according to claim 5, characterized in that: The calculation methods for the allowable stress of fin materials include: Obtaining the fin ultimate strength corresponding to the fin material, wherein the fin ultimate strength includes the fin tensile strength and the fin yield strength; Calculating the fin tensile allowable stress and the fin yield allowable stress corresponding to the fin tensile strength and the fin yield strength respectively according to the fin tensile strength and the fin yield strength and the corresponding safety factors; The smaller value between the fin tensile allowable stress and the fin yield allowable stress is selected as the final allowable stress.

7. The design method of a plate-fin evaporator based on evaporative heat absorption according to claim 4, characterized in that: Checking the thickness of the partition includes: Get the maximum pressure resistance corresponding to the partition material; Calculating the minimum thickness of the partition according to the maximum pressure resistance, the fin structural parameters and the allowable stress of the partition material; Compare the thickness data in the partition structure parameters with the minimum thickness of the partition. If the thickness data in the partition structure parameters is greater than the minimum thickness of the partition, the thickness check of the partition is passed.

8. The design method of a plate-fin evaporator based on evaporative heat absorption according to claim 7, characterized in that: Checking the width of the seal includes: Get the maximum pressure resistance corresponding to the seal material; Calculate the minimum seal width based on the maximum pressure resistance, seal structural parameters and allowable stress of the seal material; Compare the width data in the seal structure parameters with the minimum seal width. If the width data in the seal structure parameters is greater than the minimum seal width, the seal width check is passed.

9. The design method of a plate-fin evaporator based on evaporative heat absorption according to claim 8, characterized in that: The allowable stress calculation methods for partition and seal materials include: Obtain the material ultimate strength corresponding to the partition and seal materials; The allowable stress is calculated based on the ultimate strength of the material and the corresponding safety factor.

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