CN111278256B - Phase change heat storage device based on convection heat transfer - Google Patents

Phase change heat storage device based on convection heat transfer Download PDF

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CN111278256B
CN111278256B CN201911417279.2A CN201911417279A CN111278256B CN 111278256 B CN111278256 B CN 111278256B CN 201911417279 A CN201911417279 A CN 201911417279A CN 111278256 B CN111278256 B CN 111278256B
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胡定华
林肯
李强
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Nanjing University of Science and Technology
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    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
    • H05K7/00—Constructional details common to different types of electric apparatus
    • H05K7/20—Modifications to facilitate cooling, ventilating, or heating
    • H05K7/2029—Modifications to facilitate cooling, ventilating, or heating using a liquid coolant with phase change in electronic enclosures
    • H05K7/20327—Accessories for moving fluid, for connecting fluid conduits, for distributing fluid or for preventing leakage, e.g. pumps, tanks or manifolds
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01S—DEVICES USING THE PROCESS OF LIGHT AMPLIFICATION BY STIMULATED EMISSION OF RADIATION [LASER] TO AMPLIFY OR GENERATE LIGHT; DEVICES USING STIMULATED EMISSION OF ELECTROMAGNETIC RADIATION IN WAVE RANGES OTHER THAN OPTICAL
    • H01S3/00—Lasers, i.e. devices using stimulated emission of electromagnetic radiation in the infrared, visible or ultraviolet wave range
    • H01S3/02—Constructional details
    • H01S3/04—Arrangements for thermal management
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01S—DEVICES USING THE PROCESS OF LIGHT AMPLIFICATION BY STIMULATED EMISSION OF RADIATION [LASER] TO AMPLIFY OR GENERATE LIGHT; DEVICES USING STIMULATED EMISSION OF ELECTROMAGNETIC RADIATION IN WAVE RANGES OTHER THAN OPTICAL
    • H01S5/00—Semiconductor lasers
    • H01S5/02—Structural details or components not essential to laser action
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Abstract

本发明公开了一种基于对流传热的相变蓄热装置及其关键参数确定方法，装置包括相变蓄热材料、相变蓄热单元体与相变蓄热装置壳体；相变蓄热单元体包括冷却循环管路、加热循环管路、盖板及肋片；多个肋片沿竖直方向上布置；肋片上设有多个通孔，冷却循环管路与加热循环管路平行地穿过肋片上的通孔并与肋片固定；冷却循环管路与加热循环管路上端固定于盖板，盖板与相变蓄热装置壳体连接；相变蓄热装置壳体内设有多个存储空腔；每个空腔内均设有蓄热单元体并填充有相变蓄热材料；不同相变蓄热单元体间的冷却循环管路之间相连、加热循环管路之间相连。通过参数确定方法可获得相变蓄热装置最轻的作为最终设计，减轻了对散热能力的需求。

Figure 201911417279

The invention discloses a phase-change heat storage device based on convection heat transfer and a method for determining key parameters thereof. The device comprises a phase-change heat-storage material, a phase-change heat-storage unit body and a phase-change heat-storage device shell; The unit body includes a cooling circulation pipe, a heating circulation pipe, a cover plate and a fin; a plurality of fins are arranged in the vertical direction; a plurality of through holes are arranged on the fin, and the cooling circulation pipe and the heating circulation pipe are parallel to each other. Pass through the through holes on the fins and are fixed with the fins; the upper ends of the cooling circulation pipeline and the heating circulation pipeline are fixed on the cover plate, and the cover plate is connected with the shell of the phase change heat storage device; storage cavities; each cavity is provided with a heat storage unit body and filled with phase change heat storage material; the cooling circulation pipelines between the different phase change heat storage unit bodies are connected and the heating circulation pipelines are connected . Through the parameter determination method, the lightest phase change heat storage device can be obtained as the final design, which reduces the demand for heat dissipation capacity.

Figure 201911417279

Description

Phase change heat storage device based on convection heat transfer
Technical Field
The invention belongs to the field of phase change heat storage, and particularly relates to a phase change heat storage device based on convective heat transfer and a key parameter determination method thereof.
Background
With the rapid development of laser and electronic equipment, the volume of the equipment is reduced, the heat productivity is gradually increased, and the instantaneous heat flux density of the surface of the equipment can reach 100W/cm at the power peak value2～1000W/cm2If the heat dissipation is not performed in time, the temperature of the equipment is rapidly increased and the equipment fails. Meanwhile, because the space between the laser and the electronic equipment is limited, the temperature difference between the laser and the environment is small during working, the heat dissipation device is difficult to meet the peak heat dissipation requirement, and one heat dissipation device is required to be added in the heat dissipation processA heat storage device to reduce the requirement for heat dissipation capacity. Phase change thermal storage is an efficient thermal storage method, has the advantages of large thermal storage density and small temperature difference in the phase change process compared with the traditional thermal storage method, and is considered to be an excellent method for solving the peak heat dissipation problem of laser and electronic equipment.
Phase change heat storage is a heat storage technology which enables a material to heat up and cross over a self phase change temperature point in the heat absorption process, and a large amount of heat is absorbed due to the change of the state of the material in the heating process, so that a large amount of heat storage is realized. In addition, the temperature of the material is kept relatively constant in the phase change process, and meanwhile, the phase change latent heat of the material is far larger than the specific heat capacity of the same material, so that the material has high heat storage density. In the phase change heat storage device disclosed in patent No. 201720508512.8, since only a single circulation path exists in the heat storage device, both the heat storage process and the heat release process are slow, and a large device size and a large working temperature range are required, which cannot meet the requirements of miniaturization and rapid heat dissipation of laser and electronic equipment.
Disclosure of Invention
The invention aims to provide a phase-change heat storage device based on convective heat transfer and a key parameter determination method thereof, so as to achieve the purpose of temporarily storing input heat flows with large input power, short duration and long input intervals in the device and converting the input heat flows into low input power, long duration and continuously input heat flows by utilizing a convective heat transfer method and phase-change heat storage characteristics under the condition of low heat transfer temperature difference.
The technical solution for realizing the purpose of the invention is as follows:
a phase change heat storage device based on convection heat transfer comprises a phase change heat storage material, a phase change heat storage unit body and a phase change heat storage device shell;
the phase change heat storage unit body comprises a cooling circulation pipeline, a heating circulation pipeline, a cover plate and fins; the fins are arranged at equal intervals along the vertical direction; the fins are provided with a plurality of through holes at equal intervals, and the cooling circulation pipeline and the heating circulation pipeline parallelly penetrate through the through holes in the fins and are fixed with the fins; the upper ends of the cooling circulation pipeline and the heating circulation pipeline are fixed on a cover plate, and the cover plate is connected with the phase change heat storage device shell; the inlet and outlet of the cooling circulation pipeline and the heating circulation pipeline are both positioned at the upper end of the cover plate; the cooling circulation pipeline is surrounded by the heating circulation pipeline; a plurality of storage cavities are formed in the shell of the phase change heat storage device; each cavity is internally provided with a heat storage unit body and filled with a phase change heat storage material; the cooling circulation pipelines and the heating circulation pipelines among different phase change heat storage unit bodies are connected.
Compared with the prior art, the invention has the following remarkable advantages:
(1) by respectively arranging circulation loops for the heating process and the cooling process of the phase-change heat storage material in the phase-change heat storage device, different requirements of the phase-change heat storage device on the heating cycle and the cooling cycle are met;
(2) by arranging the heat exchange tubes in parallel, the space between the heat exchange tubes is greatly reduced, the utilization rate of the phase change heat storage material filled in the phase change heat storage device is improved, and the volume of the whole device is reduced;
(3) the enhanced heat conduction method of arranging the fins in the phase-change heat storage device greatly improves the heat conduction coefficient of the phase-change heat storage material, and achieves the purposes of quickly absorbing and releasing heat;
(4) through the design of the phase change heat storage unit body, the phase change heat storage device has good detachability and is convenient to maintain and manufacture.
Drawings
Fig. 1 is an assembly view of a phase change thermal storage device.
Fig. 2 is a schematic diagram of a phase change heat storage unit.
Fig. 3 is a diagram of a phase change heat storage device casing.
Fig. 4 is a schematic diagram of the phase change heat storage device.
FIG. 5 is a diagram showing the relationship between the thickness of the molten layer of the phase-change heat storage material and the total weight of the phase-change heat storage device according to the embodiment.
Detailed Description
The invention is further described with reference to the following figures and embodiments.
With reference to fig. 1 to 3, the present invention is a phase change thermal storage device based on convective heat transfer, including a phase change thermal storage material 6, a phase change thermal storage unit body 7, and a phase change thermal storage device housing 8;
the phase change heat storage unit body 7 comprises a cooling circulation pipeline 1, a heating circulation pipeline 2, a cover plate 3 and fins 5; a plurality of fins 5 are arranged at equal intervals in the vertical direction; the fins 5 are provided with a plurality of through holes at equal intervals, and the cooling circulation pipeline 1 and the heating circulation pipeline 2 parallelly penetrate through the through holes on the fins 5 and are tightly welded with the fins 5; the upper ends of the cooling circulation pipeline 1 and the heating circulation pipeline 2 are fixed on a cover plate 3, the edge of the cover plate 3 is provided with a counter bore 4 and a fastening screw 9, and the cover plate 3 and a phase change heat storage device shell 8 are tightly connected through the fastening screw 9; the inlet and outlet of the cooling circulation pipeline 1 and the heating circulation pipeline 2 are both positioned at the upper end of the cover plate 3; the cooling circulation pipeline 1 is surrounded by a heating circulation pipeline 2; a plurality of storage cavities are arranged in the phase change heat storage device shell 8; each cavity is internally provided with a heat storage unit body 7 filled with phase change heat storage materials 6, and the edge of each storage cavity is provided with a threaded hole matched with a fastening screw 9 to be connected with the heat storage unit body.
Furthermore, the inlet and outlet of the cooling circulation pipeline 1 and the heating circulation pipeline 2 in the phase change heat storage unit bodies 7 are both provided with threads, and the cooling circulation pipeline 1 and the heating circulation pipeline 2 between different phase change heat storage unit bodies 7 are connected by using the connecting pipes 10, so that the cooling circulation pipeline 1 and the heating circulation pipeline 2 in a split design form a complete circulation.
Furthermore, a filling hole 11 and a sewage draining hole 13 are formed in the phase change heat storage device shell 8. The filling hole 11 is positioned at the top of the phase change heat storage device shell 8 and is arranged in parallel with the cover plate 3, and a top cover 12 with a liquid level scale is arranged on the filling hole 11; the blowdown hole 13 is located at the bottom of the phase change heat storage device case 8 and is provided with a sealing cover 14. Before the phase change heat storage device is used, the phase change heat storage material 6 is injected from the filling hole 11 to the scale position on the liquid level scale 12, the phase change heat storage material 6 is drained from the sewage draining hole 13 when the phase change heat storage device is maintained, the phase change heat storage device is cleaned, and new phase change heat storage material 6 is refilled from the filling hole 11.
Furthermore, the cooling circulation pipeline 1 and the heating circulation pipeline 2 in the phase change heat storage device both adopt red copper heat exchange pipes, the outer diameter of each heat exchange pipe is 3-80 mm, and the space between the heat exchange pipes is 3-50 mm; circulating media of a cooling circulating pipeline 1 in the phase-change heat storage device are various low-temperature refrigerants, and circulating media of a heating circulating pipeline 2 are water added with anti-freezing liquid; the phase change heat storage material 6 is mainly used for enhancing heat transfer through the fins 5, and the volume ratio of the added fins 5 to the filled phase change heat storage material 6 is about 5-30%. The enhanced phase change heat storage material 6 has the heat storage capacity of about 120 kJ/kg-200 kJ/kg and the heat conductivity of about 10W/(mK) -50W/(mK). Referring to fig. 4, the cooling circulation line 1 transfers heat in the phase change heat storage material 6 out of the apparatus and discharges it to the outside; the heating circulating pipeline 2 transfers heat from a heating source into the device and is absorbed by the phase change heat storage material 6; the cooling circulation pipeline 1 has low heat flux density and small heat load; the duration is long; the heating circulating pipeline 2 has high heat flow density, large heat load and short duration. The tube pass numbers of the two circulation pipelines are respectively matched with the heating heat load and the cooling heat load so as to adapt to different requirements of a phase change heating process and a phase change cooling process. The pulse heat load is input from the heating circulation pipeline by taking water added with the anti-freezing liquid as a medium, temporarily stored in the phase change heat storage material in the phase change heat storage device and finally slowly taken away by the cooling circulation pipeline by taking a low-temperature refrigerant as a medium. Through the heat absorption and heat release processes, the phase change heat storage device stabilizes instantaneous heat load into stable heat load, and reduces the requirement on heat dissipation capacity.
A method for determining key parameters of a phase change heat storage device based on convection heat transfer comprises the following steps:
step 1, calculating the phase change point of the phase change heat storage material 6
Determining the phase change point T of the phase change heat storage material 6 according to the following formula0：
Figure BDA0002351514760000041
Wherein:
T1inputting temperature for the heating circulation pipeline 2;
n 12 pipes of the heating circulating pipeline;
t1is the heating cycle time;
T2inputting temperature for the cooling circulation pipeline 1;
n2the number of the cooling circulation pipeline is 1;
t2is the cooling cycle time;
step 2, calculating the size of the circulating pipeline
The cooling circulation pipeline 1 and the heating circulation pipeline 2 adopt the same red copper heat exchange tubes, the wall thickness t of the heat exchange tubes is selected according to the following formula, and the wall thickness t is less than 0.25mm, namely 0.25 mm:
Figure BDA0002351514760000042
wherein:
p is the working pressure of the heat exchange tube;
d2the outer diameter of the heat exchange tube;
σaallowable stress for the wall material of the heat exchange tube;
a is the processing and corrosion allowance of the heat exchange tube wall;
inner diameter d of heat exchange tube1Comprises the following steps:
d1＝d2-2t
step 3, calculating the volume of the required phase change heat storage material 6
The volume V of the phase change heat storage material 6 to be filled in the phase change heat storage device is calculated according to the following formula:
Figure BDA0002351514760000043
wherein:
q1inputting power for the heating cycle;
C1the amount of heat stored per unit volume of the phase change heat storage material 6;
step 4, calculating the total heat transfer coefficient h of the heating circulation pipeline 2H
Given the thickness e of the molten layer of the phase change heat storage material 6 and the fins in the phase change heat storage material 6The volume ratio f, the total heat transfer coefficient h of the heating circulation line 2 is calculated according to the following formulaH：
Figure BDA0002351514760000051
Wherein:
μHis the dynamic viscosity of the fluid in the heating circulation pipeline 2;
cHthe fluid in the circulating pipeline 2 is heated and has constant pressure specific heat capacity;
λHthe heat conductivity coefficient of the fluid in the heating circulation pipeline 2;
vHis the flow rate of the fluid line in the heating circulation pipeline 2;
ρHis the density of the fluid in the heating circulation pipeline 2;
h2is the fouling heat transfer coefficient of the phase change heat storage material 6;
λ1the thermal conductivity of the material used for the tube wall of the heat exchange tube;
λ2the thermal conductivity of the phase change heat storage material 6;
λ3the thermal conductivity of the fins 5;
step 5, calculating the total heat transfer coefficient h of the cooling circulation pipeline 1C
The total heat transfer coefficient h of the cooling circulation line 1 according to the following formulaC：
Figure BDA0002351514760000052
Wherein:
μCis the dynamic viscosity of the fluid in the cooling circulation pipeline 1;
cCthe constant pressure specific heat capacity of the fluid in the cooling circulation pipeline 1;
λCthe coefficient of heat conductivity of the fluid in the cooling circulation pipeline 1;
vCis the linear flow velocity of the fluid in the cooling circulation pipeline 1;
ρCto be circulated for coolingThe fluid density in the loop pipe 1;
step 6, calculating the total length L of the heating circulating pipeline 2H
The total length L of the heating circulation line 2 is calculated according to the following formulaH：
Figure BDA0002351514760000053
Step 7, checking and calculating the total length L of the cooling circulation pipeline 1C
The actual total length L of the cooling circulation line 1 in the phase-change heat storage device is calculated according to the following formulaC1
Figure BDA0002351514760000061
The required total length L of the cooling circulation line 1 in the phase change heat storage device is calculated according to the following formulaC2
Figure BDA0002351514760000062
If L isC1≥LC2If the phase change heat storage device is calculated to pass, taking LC＝LC1. Otherwise, the volume ratio f of the fins 5 in the phase change heat storage material is increased, and the calculation is started from the step 4 again.
Step 8, adjusting the thickness e of the melting layer of the phase change heat storage material 6, repeating the steps 4 to 7, forming various design schemes of the phase change heat storage device, outputting the thickness e of the melting layer of the phase change heat storage material 6, the volume ratio f of the fins 5 and the total length L of the cooling circulation pipeline 1, which are key parameters of the phase change heat storage device in different schemesCAnd the total length L of the heating circulation pipeline 2HThe phase change thermal storage device masses in the different versions are formed and compared, and the lightest of them is selected as the final design result.
Examples
The present embodiment is implemented on the premise of the technical solution of the present invention, and a detailed implementation manner and a specific operation process are given, but the scope of the present invention is not limited to the following embodiments.
The design conditions were 300kW peak heat load, 6s duration, 100s interval. The input temperature of the heating circulation pipeline is 10 ℃, and the input temperature of the cooling circulation pipeline is-25 ℃.
And calculating parameters of the phase change heat storage device according to the calculating steps.
Step 1, calculating and integrating to obtain a phase change point T of the phase change heat storage material 60Should be-15 deg.C;
step 2, selecting the outer diameter d of the heat exchange tube2The thickness t of the heat exchange tube is calculated to be 0.25mm when the thickness t of the heat exchange tube is 3 mm;
step 3, calculating that the volume V of the phase change heat storage material 6 to be filled is 11.6L;
step 4, selecting the thickness e of the melting layer of the phase change heat storage material 6 as 2.1mm, the volume ratio f of the fins 5 as 6.5%, and calculating to obtain the total heat transfer coefficient h of the heating circulation pipeline 2HIs 1.78 kW/(m)2*K)；
Step 5, calculating the total heat transfer coefficient h of the cooling circulation pipeline 1CIs 3.36 kW/(m)2*K)；
Step 6, calculating the total length L of the heating circulation pipeline 2HIs 1818 m;
step 7, calculating the actual total length L of the cooling circulation pipelineC1280m, a total length L is requiredC2The total length L of the cooling circuit 1 was calculated to be 259mCIs 280 m;
and 8, adjusting the thickness of the phase change heat storage material melting layer, and calculating the total weight of the phase change heat storage device, wherein the result is shown in fig. 5.
In summary, the optimal thickness of the phase change heat storage material melting layer in the phase change heat storage device is 2.1mm, the volume ratio of the fins 5 is 6.5%, the total length of the heating circulation pipeline 2 is 1818m, the total length of the cooling circulation pipeline 1 is 280m, the total weight of the phase change heat storage device is 70kg, and the volume is 40L;
the device realizes the purpose of converting the pulse heat load of 300kW, lasting 6s and interval 100s into the stable heat load output of 18kW, and reduces the requirement of heat dissipation capacity.

Claims (2)

1.一种基于对流传热的相变蓄热装置，其特征在于，包括相变蓄热材料、相变蓄热单元体与相变蓄热装置壳体；1. A phase-change heat storage device based on convection heat transfer, characterized in that it comprises a phase-change heat-storage material, a phase-change heat-storage unit body and a phase-change heat-storage device housing; 所述相变蓄热单元体包括冷却循环管路、加热循环管路、盖板及肋片；多个肋片沿竖直方向上作等间隔的布置；所述肋片上等间隔的设有多个通孔，所述冷却循环管路与加热循环管路平行地穿过肋片上的通孔并与肋片固定；所述冷却循环管路与加热循环管路上端固定于盖板，所述盖板与相变蓄热装置壳体连接；所述冷却循环管路与加热循环管路的进、出口均位于盖板上端；所述冷却循环管路由加热循环管路包围；所述相变蓄热装置壳体内设有多个存储空腔；每个空腔内均设有蓄热单元体并填充有相变蓄热材料；不同相变蓄热单元体间的冷却循环管路之间相连、加热循环管路之间相连；The phase-change heat storage unit body includes a cooling cycle pipeline, a heating cycle pipeline, a cover plate and fins; a plurality of fins are arranged at equal intervals along the vertical direction; a through hole, the cooling circulation pipeline and the heating circulation pipeline pass through the through holes on the fins in parallel with the fins and are fixed to the fins; the upper ends of the cooling circulation pipeline and the heating circulation pipeline are fixed on the cover plate, and the cover The plate is connected to the shell of the phase-change heat storage device; the inlet and outlet of the cooling cycle pipeline and the heating cycle pipeline are located at the upper end of the cover plate; the cooling cycle pipeline is surrounded by the heating cycle pipeline; the phase-change heat storage A plurality of storage cavities are arranged in the device shell; each cavity is provided with a heat storage unit body and is filled with a phase change heat storage material; the cooling circulation pipes between the different phase change heat storage unit bodies are connected and heated connected between the circulation pipes; 该相变蓄热装置关键参数的设计方法，包括以下步骤：The design method of the key parameters of the phase change heat storage device includes the following steps: 步骤1、计算相变蓄热材料相变点；Step 1. Calculate the phase change point of the phase change heat storage material; 步骤2、计算循环管路尺寸：
Figure FDA0003156240830000011
Step 2. Calculate the size of the circulating pipeline:
Figure FDA0003156240830000011
 其中P为换热管工作压力；d2为换热管外径；σa为换热管壁材料许用应力；a为换热管壁的加工与腐蚀余量；换热管内径d1为：where P is the working pressure of the heat exchange tube; d 2 is the outer diameter of the heat exchange tube; σ a is the allowable stress of the heat exchange tube wall material; a is the processing and corrosion allowance of the heat exchange tube wall; the inner diameter of the heat exchange tube d 1 is : d1＝d2-2td 1 =d 2 -2t 步骤3、计算需要的相变蓄热材料体积V：
Figure FDA0003156240830000012
Step 3. Calculate the required volume V of the phase change heat storage material:
Figure FDA0003156240830000012
 其中q1为加热循环输入功率；C1为相变蓄热材料的单位体积储热量；where q 1 is the input power of the heating cycle; C 1 is the heat storage per unit volume of the phase change heat storage material; 步骤4、计算加热循环管路的总传热系数hH：Step 4. Calculate the total heat transfer coefficient h H of the heating circulation pipeline:
Figure FDA0003156240830000013
Figure FDA0003156240830000013
 其中μH、cH、λH、vH、ρH分别为加热循环管路内流体动力粘度、等压比热容、导热系数、线流速、密度；h2为相变蓄热材料的污垢传热系数；λ1为换热管管壁所用材料的导热系数；λ2为相变蓄热材料的导热系数；λ3为肋片的导热系数；f为肋片的体积比；Among them μ H , c H , λ H , v H , ρ H are the fluid dynamic viscosity, isobaric specific heat capacity, thermal conductivity, linear velocity and density in the heating circulation pipeline, respectively; h 2 is the fouling heat transfer of the phase change heat storage material coefficient; λ 1 is the thermal conductivity of the material used for the heat exchange tube wall; λ 2 is the thermal conductivity of the phase change heat storage material; λ 3 is the thermal conductivity of the fins; f is the volume ratio of the fins; 步骤5、计算冷却循环管路的总传热系数hC：Step 5. Calculate the total heat transfer coefficient h C of the cooling circulation pipeline:
Figure FDA0003156240830000014
Figure FDA0003156240830000014
 其中μC、cC、λC、vC、ρC分别为冷却循环管路内流体动力粘度、等压比热容、导热系数、线流速、密度；where μ C , c C , λ C , v C , and ρ C are the fluid dynamic viscosity, isobaric specific heat capacity, thermal conductivity, linear velocity, and density in the cooling circulation pipeline, respectively; 步骤6、计算加热循环管路总长LH：
Figure FDA0003156240830000021
Step 6. Calculate the total length of the heating circulation pipeline L H :
Figure FDA0003156240830000021
 步骤7、验算冷却循环管路总长LC：Step 7. Check and calculate the total length L C of the cooling circulation pipeline: 计算相变蓄热装置中冷却循环管路的实际总长LC1：Calculate the actual total length L C1 of the cooling circulation pipeline in the phase change heat storage device:
Figure FDA0003156240830000022
Figure FDA0003156240830000022
 计算相变蓄热装置中冷却循环管路)的需要总长LC2：Calculate the required total length L C2 of the cooling circulation pipeline in the phase change heat storage device:
Figure FDA0003156240830000023
Figure FDA0003156240830000023
 若LC1≥LC2，取LC＝LC1；否则，提高相变蓄热材料中肋片的体积比f，自步骤4开始重新计算。If L C1 ≥ L C2 , take L C =L C1 ; otherwise, increase the volume ratio f of the fins in the phase-change heat storage material, and recalculate from step 4. 2.根据权利要求1所述的相变蓄热装置，其特征在于，其关键参数的设计方法，还包括以下步骤：2. The phase change heat storage device according to claim 1, wherein the design method of its key parameters further comprises the following steps: 调整相变蓄热材料熔融层的厚度e，重复步骤4至步骤7，形成多种尺寸组合；选择其中相变蓄热装置质量最轻的作为最终设计结果。Adjust the thickness e of the molten layer of the phase change heat storage material, repeat steps 4 to 7 to form multiple size combinations; select the phase change heat storage device with the lightest mass as the final design result.
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