CN111278256A - Phase change heat storage device based on convective heat transfer and key parameter determination method thereof - Google Patents

Phase change heat storage device based on convective heat transfer and key parameter determination method thereof Download PDF

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CN111278256A
CN111278256A CN201911417279.2A CN201911417279A CN111278256A CN 111278256 A CN111278256 A CN 111278256A CN 201911417279 A CN201911417279 A CN 201911417279A CN 111278256 A CN111278256 A CN 111278256A
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heat storage
phase change
change heat
storage device
circulation pipeline
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CN111278256B (en
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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
    • H01S5/024—Arrangements for thermal management
    • H01S5/02407—Active cooling, e.g. the laser temperature is controlled by a thermo-electric cooler or water cooling

Abstract

The invention discloses a phase change heat storage device based on convective heat transfer and a key parameter determination method thereof, wherein 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 phase change heat storage unit body comprises a cooling circulation pipeline, a heating circulation pipeline, a cover plate and fins; a plurality of ribs are arranged in a vertical direction; 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; a plurality of storage cavities are arranged 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. The lightest phase change heat storage device can be obtained through the parameter determination method as the final design, and the requirement on the heat dissipation capacity is reduced.

Description

Phase change heat storage device based on convective heat transfer and key parameter determination method thereof
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, 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 a heat storage device is required to be added in the heat dissipation process to reduce the requirement on the 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
The thickness e of the melting layer of the phase-change heat storage material 6 and the volume ratio f of the fins in the phase-change heat storage material 6 are given, and the total heat transfer coefficient h of the heating circulation pipeline 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
Total heat transfer of cooling circulation line 1 according to the following formulaCoefficient of heat hC：
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;
ρCis the density of the fluid in the cooling circulation pipeline 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 phase change storageRepeating the steps 4 to 7 to form 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 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 (7)

1. A phase change heat storage device based on convection heat transfer is characterized by comprising 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.
2. The phase-change thermal storage device according to claim 1, wherein the phase-change thermal storage device casing is provided with a filling hole and a blowdown hole; the filling hole is positioned at the top of the phase change heat storage device shell and is arranged in parallel with the cover plate; the sewage draining hole is arranged at the bottom of the phase change heat storage device shell and is provided with a sealing cover.
3. The phase-change thermal storage device according to claim 1, wherein a top cover with a liquid level gauge is fitted over the filler hole.
4. The phase-change heat storage device according to claim 1, wherein a red copper heat exchange tube is used for both the cooling circulation line and the heating circulation line in the phase-change heat storage device.
5. The phase-change heat storage device according to claim 1, wherein the volume ratio of the fins to the phase-change heat storage material is 5% to 30%.
6. A method of designing a phase change thermal storage device according to any one of claims 1 to 5, characterized by comprising the steps of:
step 1, calculating a phase change point of a phase change heat storage material;
step 2, calculating the size of a circulating pipeline:
Figure FDA0002351514750000011
wherein P is the working pressure of the heat exchange tube; d2The outer diameter of the heat exchange tube; sigmaaAllowable 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 V of the required phase change heat storage material:
Figure FDA0002351514750000012
wherein q is1Inputting power for the heating cycle; c1The heat storage quantity of the phase change heat storage material per unit volume is stored;
step 4, calculating the total heat transfer coefficient h of the heating circulation pipelineH：
Figure FDA0002351514750000021
Wherein muH、cH、λH、vH、ρHRespectively heating the dynamic viscosity, the isobaric specific heat capacity, the heat conductivity coefficient, the linear flow velocity and the density of the fluid in the circulating pipeline; h is2The heat transfer coefficient of the phase change heat storage material; lambda [ alpha ]1The thermal conductivity of the material used for the tube wall of the heat exchange tube; lambda [ alpha ]2The heat conductivity coefficient of the phase change heat storage material; lambda [ alpha ]3Is the thermal conductivity of the fins; f is the volume ratio of the fins;
step 5, calculating the total heat transfer coefficient h of the cooling circulation pipelineC：
Figure FDA0002351514750000022
Wherein muC、cC、λC、vC、ρCRespectively including dynamic viscosity, isobaric specific heat capacity, heat conductivity coefficient, linear flow rate and density of fluid in the cooling circulation pipeline;
step 6, calculating the total length L of the heating circulation pipelineH：
Figure FDA0002351514750000023
Step 7, checking and calculating the total length L of the cooling circulation pipelineC：
Calculating the actual total length L of the cooling circulation pipeline in the phase-change heat storage deviceC1：
Figure FDA0002351514750000024
Calculating the required total length L of the cooling circulation line in the phase-change heat storage device)C2：
Figure FDA0002351514750000025
If L isC1≥LC2Taking LC＝LC1(ii) a Otherwise, increasing the volume ratio f of the fins in the phase change heat storage material, and the steps4 start the recalculation.
7. The design method of claim 6, further comprising the steps of:
adjusting the thickness e of the phase change heat storage material melting layer, and repeating the steps 4 to 7 to form various size combinations; the final design result is selected as the one in which the phase change heat storage device is the lightest in mass.
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