A parallel flow channel cooling system and its operation control method

Abstract

The present invention discloses a parallel flow channel cooling system and an operation control method thereof. The system includes an inlet, a plurality of outlets, an inlet manifold, an outlet manifold, a plurality of parallel flow channels and a plurality of heat sources. The inlet section and the outlet section are respectively connected to the inlet manifold and the outlet manifold. Two of the outlet sections are parallel to the outlet manifold, and the remaining outlet sections are perpendicular to the outlet manifold. The parallel flow channels are perpendicular to the inlet manifold and the outlet manifold. The widths of the leftmost and rightmost parallel flow channels are the same, and the widths of the remaining parallel flow channels are the same. Valves are provided at each outlet, and different flow patterns of the system can be switched according to the opening and closing of the valves. The present invention ensures that the parallel flow channel cooling system has a small temperature difference and hot spot temperature under different operating conditions, and has the advantages of simple system structure, good strategy regulation performance, convenient implementation and strong versatility.

Description

Technical Field

[0001] The present invention relates to the field of cooling of electronic devices, and more particularly to a parallel flow channel cooling system and an operation control method thereof. Background Art

[0002] With the development of electronic technology, the integration degree of electronic devices is getting higher and higher, and the heat flux density is getting larger and larger, thus posing higher requirements for electronic heat dissipation technology. Among many cooling systems, the parallel flow channel cooling system has the advantages of compact structure and low pressure drop, and thus has been widely used in the field of electronic heat dissipation. However, the parallel flow channel structure is prone to uneven flow distribution among the flow channels, resulting in inconsistent cooling conditions in different regions, leading to higher hot spot temperatures and larger temperature differences in the electronic devices, which will affect the performance and service life of the electronic devices. Therefore, it is necessary to design an efficient parallel flow channel cooling system for electronic heat dissipation to enable the electronic devices to operate within a suitable temperature range.

[0003] Existing studies have mainly improved the cooling performance of the system by optimizing algorithms to adjust the structural parameters of the parallel cooling system. Park et al. (Park H. A design of air flow configuration for cooling lithium ion battery in hybrid electric vehicles[J]. Journal of Power Sources, 2013, 239: 30-36.) adopted a conical manifold and a second air outlet in the U-shaped parallel air-cooled battery thermal management system to obtain the required cooling performance. Chen et al. (Chen K, Chen Y M, Li Z Y, et al. Design of the cell spacings of battery pack in parallel air-cooled battery[J]. International Journal of Heat and Mass Transfer, 2018, 127: 393-401.) optimized to obtain a non-uniform parallel flow channel width, reducing the maximum temperature of the battery pack by 3.0 K and the temperature difference of the battery by more than 60%. However, optimizing the structure of the battery pack thermal management system is generally only effective for specific operating conditions and cannot be applied to all conditions during operation. Therefore, scholars have proposed using control strategies to optimize the operation of the air-cooled battery thermal management system. For example, Wang et al. (Wang S X, Li K X, Tian Y, et al. Improved thermal performance of a large laminated lithium-ion power battery by reciprocating air flow[J]. Applied Thermal Engineering, 2019, 152: 445-454.) reversed the direction of the air flow by controlling the valve in the experimental device and designed a control strategy for reciprocating air flow. When the maximum temperature difference of a single battery reached 4.9 °C, the air flow direction automatically reversed, achieving automatic regulation of the temperature difference.Liu et al. (Liu Y Z, Zhang J. Self - adapting J - type air - based battery thermal management system via model predictive control[J]. Applied Energy, 2020, 263: 114640.) switch the system flow patterns (including J - type, U - type, and Z - type) according to the difference between the specific battery temperatures max(T2, T4) and max(T7, T9), and use different flow patterns to regulate the temperature difference of the battery pack. However, this strategy regulates the flow pattern according to a specific battery temperature difference and cannot be applied to all operating conditions, and it is difficult to reduce the temperature difference of the battery pack under certain conditions. Therefore, in order to ensure that the battery pack can maintain a small temperature difference under various operating conditions, a universal and efficient parallel flow channel cooling system structure and corresponding operation control strategy need to be designed. Summary of the Invention

[0004] Aiming at the deficiencies of the existing technology, the present invention provides a parallel flow channel cooling system and its operation control method.

[0005] The present invention is achieved by at least one of the following technical solutions.

[0006] A parallel flow channel cooling system includes an inlet section, an inlet manifold, a plurality of parallel flow channels, a plurality of heat sources, an outlet manifold, and a plurality of outlet sections; the inlet section is connected to the inlet manifold, and the inlet manifold and the outlet manifold are connected by the parallel flow channels; the plurality of outlet sections are respectively connected to the outlet manifold; the plurality of parallel flow channels are distributed on the left and right sides of each heat source and are perpendicular to the inlet manifold and the outlet manifold; the inlet section is connected to the inlet manifold in parallel, the number of the plurality of outlet sections is M, where M≥3, and each outlet section is provided with a valve; the first outlet section and the M - th outlet section are respectively connected to the outlet manifold in parallel, and the second valve to the (M - 1) - th valve outlet sections are perpendicularly connected to the middle of the outlet manifold; the inlet section, the first outlet section, and the M - th outlet section are on a horizontal line, and the 2 - th to (M - 1) - th outlet sections are on a horizontal line with the parallel flow channels.

[0007] Furthermore, the widths of the left - most and right - most flow channels among the plurality of parallel flow channels are the same, and the widths of the remaining parallel flow channels are the same. The width ratio of the parallel flow channels is [C1, 1, 1,…, 1, 1, C1], where the value range of C1 is (0, 1).

[0008] Further, valves are provided at each outlet. The valve at the i-th outlet is valve i, where i = 1, 2, …, i, …, M. According to the opening and closing of the valves to switch the different flow patterns of the system, the system is divided into three flow patterns, namely J-type, U-type, and L-type. When the first valve and the M-th valve are open and the second valve to the (M - 1)-th valve are closed, the system flow pattern is J-type. When the first valve is open and the second valve to the M-th valve are closed, the system flow pattern is U-type. When the i-th valve is open, where i = 2 to M - 1, and the remaining valves are closed, the system flow pattern is L-type.

[0009] Implementing the operation control method of a parallel flow channel cooling system as described above includes the following steps:

[0010] The flow rate of the system cooling working medium is any value and changes during operation; set a temperature difference threshold T lim , a deviation Δε, and a monitoring time step Δt. Set monitoring points in each heat source, and record the temperature of each monitoring point every Δt time during operation, denoted as T1, T2, …, T N , where N is the number of heat sources;

[0011] Calculate the temperature difference ΔT between heat sources based on the temperatures at the monitoring points max = max(T1, T2, …, T N ) - min(T1, T2, …, T N ); At the initial moment, open the first valve and the M-th valve, and close the second valve to the (M - 1)-th valve; monitor the temperature difference value ΔT max at each moment. When ΔT max ≥T lim - Δε, control the opening and closing of the valves according to the following strategy:

[0012] Assume that the center line position of the i-th outlet is l i , where i = 1, 2, …, i, …, M, where l1 = 0, l M = L; The center position of the center lines l i and l i+1 of two adjacent outlets is x i = (l i + l i+1 ) / 2. Then x i divides the system into M segments: [0, x1), [x1, x2), …, [x i , x i+1 ), …, [x M-2 , x M-1 ), [x M-1 , L]. Denote the center line position of the heat source with the highest monitored point temperature as x max . Then

[0013] If 0 ≤ xmax <x1, open the first valve, close the second valve to the Mth valve, and switch to the U-shaped system;

[0014] If x i ≤x max <x i+1 , open the (i + 1)th valve, close the remaining valves, and switch to the L-shaped system;

[0015] If x M-1 ≤x max ≤L, open the first valve and the Mth valve, close the second valve to the (M - 1)th valve, and switch to the J-shaped system.

[0016] Furthermore, at the initial moment of system operation, the first valve and the Mth valve are open, the second valve to the (M - 1)th valve are closed, and the system flow pattern is J-shaped.

[0017] Furthermore, a monitoring point is arranged for each heat source, and the temperature of the monitoring point is obtained through theoretical models, numerical calculations, or experimental tests. This temperature is the temperature of a certain point of the heat source or the average temperature of a single heat source.

[0018] Furthermore, the temperature difference between heat sources is defined as the difference between the highest temperature and the lowest temperature of the monitoring points, and the expression is ΔT max =max(T1,T2,…,T N ) - min(T1,T2,…,T N ).

[0019] Furthermore, the temperature difference threshold T lim is any value greater than 0, and the monitoring time step Δt is any value greater than 0; the deviation Δε is proportional to Δt and satisfies Δε = C2Δt, where the value range of C2 is (0, T lim / Δt).

[0020] Furthermore, monitor the temperature difference value ΔT max at each moment. When ΔT max ≥T lim -Δε, through the position x max of the center line of the heat source with the highest monitoring point temperature, adopt the following strategy to control the opening and closing of the valves:

[0021] If 0 ≤ x max <x1, open the first valve, close the second valve to the Mth valve, and switch to the U-shaped system;

[0022] If x i ≤x max <x i+1 , open the (i + 1)th valve, close the remaining valves, and switch to the L-shaped system;

[0023] If x M-1 ≤x max ≤L, open the first valve and the Mth valve, close the second valve to the (M - 1)th valve, and switch to the J-type system;

[0024] where the center line position of the ith outlet is l i , i = 1, 2, …, i, …, M, where l1 = 0, l M = L; the center line l i and l i+1 of two adjacent outlets has a center position of x i =(l i +l i+1 ) / 2, then x i divides the system into M segments: [0, x1), [x1, x2), …, [x i , x i+1 ), …, [x M-2 , x M-1 ), [x M-1 , L].

[0025] Furthermore, in the operation control strategy, the working fluid flow rate in the system can change during operation, and its change range is not limited.

[0026] Compared with the prior art, the present invention has the following advantages and beneficial effects:

[0027] 1. The parallel flow channel cooling system and its operation control strategy provided by the present invention have the advantages of simple structure and good regulation performance. The system introduces non-uniformly distributed parallel flow channel widths to regulate the cooling capacities of different parallel flow channels, and cooperates with the operation control strategy to effectively control the maximum temperature and temperature difference of the system. Compared with the traditional method of only optimizing the system structure, the present invention ensures that the electronic devices (heat sources) obtain lower hot spot temperatures and temperature differences under different operating conditions.

[0028] 2. The operation control strategy of the parallel flow channel cooling system provided by the present invention has the advantage of being easy to implement. This operation control strategy adjusts the valves based on the real-time temperature distribution of the system, thereby converting the flow pattern of the system and realizing the regulation of the hot spot temperature and temperature difference of the system, which is simple and convenient to implement.

[0029] 3. The operation control strategy of the parallel flow channel cooling system provided by the present invention has the advantage of strong generality. This operation control strategy controls the valves based on the real-time temperature distribution of the system, and is independent of the type and flow rate of the cooling working fluid, the ambient temperature, the system heat load and size, etc. Therefore, the present invention can be extended and applied to similar problems and has the advantage of strong generality. Description of the Drawings

[0030] Figure 1Schematic diagram of a parallel flow channel cooling system structure of an embodiment;

[0031] Figure 2 Top view of the battery thermal management multi - outlet parallel flow channel air - cooling system according to an embodiment of the present invention;

[0032] Figure 3 Variation curve of the temperature difference of the battery pack with time in Embodiment 1 of the present invention;

[0033] Figure 4 Variation curve of the temperature difference of the battery pack with time in Embodiment 2 of the present invention;

[0034] Figure 5 Variation curve of the temperature difference of the battery pack with time in Embodiment 3 of the present invention;

[0035] Wherein, 1 - inlet section, 2 - first outlet section, 3 - the i - th outlet section, 4 - the M - th outlet section, 5 - valve 1, 6 - the i - th valve, 7 - the M - th valve, 8 - outlet manifold, 9 - inlet manifold, 10 - parallel flow channels, 11 - heat source, 12 - center line of the heat source, 13 - center line of the outlet, 14 - center line between adjacent outlets. Detailed implementation manners

[0036] The present invention will be further described in detail below in conjunction with embodiments and the accompanying drawings, but the implementation manners of the present invention are not limited thereto.

[0037] Embodiment 1

[0038] As Figure 2 shown, the three - outlet parallel air - cooled battery thermal management system of this embodiment. The heat source is a prismatic battery, and the system includes a battery pack of 12×2 prismatic batteries. The width (w in ) of the system inlet and the width (w out ) of the outlet are both 20 mm; the length (L in ) of the system inlet and the width (L out ) of the outlet are both 100 mm; the battery size is 16 mm×65 mm×151 mm, the specific heat capacity of the battery is 1542.9 J / (kg·K), the density is 1337 kg / m 3 , and the thermal conductivity is anisotropic, being 1.05, 21.1, 21.1 W / (m·K) respectively; the inlet temperature of the cooling air is 298.15 K, and the flow rate is 0.015 m 3 / s. The air-cooling system includes an inlet section 1, an inlet manifold 9, 13 parallel flow channels, 12 batteries (heat sources 11), an outlet manifold 8, a first outlet section 2, a second outlet section 3, and a third outlet section 4. The inlet manifold 9 and the outlet manifold 8 are connected by the parallel flow channels 10; the first outlet section 2, the second outlet section 3, and the third outlet section 4 of the parallel flow channel cooling system are respectively connected to the outlet manifold 8; the first outlet section 2 and the third outlet section 4 are respectively connected to the outlet manifold 8 in parallel, and the second outlet section 3 is vertically connected to the middle of the outlet manifold 8; the inlet section 1, the first outlet section 2, and the third outlet section 4 are on a horizontal line, and the second outlet section 3 and the parallel flow channels 10 are on a horizontal line; the parallel flow channels 10 are distributed on the left and right sides of each heat source 11 and are perpendicular to the inlet manifold 9 and the outlet manifold 8. In this example, C1 = 0.9, and the width distribution [d1, d2, …, d 12 , d 13 of the parallel flow channels is [2.7, 3.0, 3.0, 3.0, 3.0, 3.0, 3.0, 3.0, 3.0, 3.0, 3.0, 3.0, 2.7] in turn, with the unit of mm. The positions of the center lines 12 of the heat sources are [10.7, 29.7, 48.7, 67.7, 86.7, 105.7, 124.7, 143.7, 162.7, 181.7, 200.7, 219.7, 238.7] in turn, with the unit of mm. The positions of the center lines 13 of the outlets are l1 = 0, l2 = 115.5 mm, l3 = 231 mm respectively, and the positions of the center lines 14 of the adjacent outlets 14 are x1 = 57.75 mm and x2 = 173.25 mm respectively.

[0039] The temperature difference threshold, deviation, and monitoring time step Δt are respectively set to T lim = 1.5 K, Δε = 0.01 K, Δt = 1 s; the monitored temperature of the battery (heat source) is the average temperature, and the temperature of each monitoring point during operation is calculated by the computational fluid dynamics method, denoted as T1, T2, …, T 12 , and the temperature difference ΔT max = max(T1, T2, …, T 12 ) - min(T1, T2, …, T 12 ). The outlet valves of the system are controlled to operate by using the present invention. At the initial moment, valve 1 and valve 3 are opened, and valve 2 is closed; the temperature difference value ΔT max at each moment is monitored. When ΔT max ≥ T lim- - Δε, the opening and closing of the valves are controlled according to the following strategy:

[0040] The central positions of the three outlets are l1 = 0, l2 = 115.5 mm, and l3 = 231 mm; the central positions of adjacent two outlets are x1 = 57.75 mm and x2 = 173.25 mm, then the system is divided into three segments: [0, x1), [x1, x2), [x2, L]. Denote the central line position of the battery (heat source) with the highest average temperature as x max , then

[0041] If 0 ≤ x max < x1, open valve 1, close valve 2 and valve 3, and switch to the U-shaped system;

[0042] If x1 ≤ x max < x2, open valve 2, close valve 1 and valve 3, and switch to the L-shaped system;

[0043] If x2 ≤ x max < L, open valve 1 and valve 3, close valve 2, and switch to the J-shaped system.

[0044] Figure 3 is the change relationship of the temperature difference of the battery pack with time. The results show that under the control strategy of the present invention, the switching order of the system flow patterns is J, U, L in sequence. The temperature differences of the battery packs in the parallel flow channel width systems such as J, U, and L types are 2.8 K, 5.1 K, and 3.6 K respectively, while the present invention controls the temperature difference of the battery pack within the set temperature difference threshold of 1.5 K during the whole operation process. This example verifies the effectiveness of the present invention for the operation control of the parallel flow channel cooling system.

[0045] Embodiment 2

[0046] A parallel flow channel cooling system of this embodiment includes an inlet section, an inlet manifold, a plurality of parallel flow channels, a plurality of heat sources, an outlet manifold, and a plurality of outlet sections; the inlet section is connected to the inlet manifold, and the inlet manifold and the outlet manifold are connected through the parallel flow channels; the plurality of outlet sections are respectively connected to the outlet manifold; the plurality of parallel flow channels are distributed on the left and right sides of each heat source and are perpendicular to the inlet manifold and the outlet manifold; the inlet section is connected to the inlet manifold in parallel, the number of the plurality of outlet sections is M, where M ≥ 3, and each outlet section is provided with a valve; the first outlet section and the Mth outlet section are respectively connected to the outlet manifold in parallel, and the second valve to the (M - 1)th valve outlet sections are vertically connected to the middle of the outlet manifold; the inlet section, the first outlet section, and the Mth outlet section are on a horizontal line, and the 2nd to (M - 1)th outlet sections are on a horizontal line with the parallel flow channels.

[0047] As Figure 2 shown, the basic structure of the air-cooled battery thermal management system of this embodiment is the same as that of Embodiment 1, but the width of the flow channels and the positions of the heat source distributions are different. In this example, C1 = 0.7, and the parallel flow channel width distribution is [d1, d2,..., d12 , d 13 are [2.2, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 2.2] in sequence, with the unit of mm. The positions of the heat source center line 12 are [10.2, 29.3, 48.4, 67.5, 86.6, 105.7, 124.8, 143.9, 163, 182.1, 201.2, 220.3, 239.4], with the unit of mm. The positions of the outlet center line 13 are l1 = 0, l2 = 115.5 mm, l3 = 231 mm respectively, and the positions of the center lines 14 of adjacent outlets are x1 = 57.75 mm and x2 = 173.25 mm respectively. The temperature difference threshold, deviation and monitoring time step Δt are respectively set as T lim = 1.5 K, Δε = 0.01 K, Δt = 1 s, and the strategy for controlling the opening and closing of the valve is the same as that in Embodiment 1.

[0048] Figure 4 shows the relationship between the temperature difference of the battery pack and time. The results show that under the control strategy of the present invention, the switching order of the system flow patterns is J, U, J in sequence. The temperature differences of the battery packs in the parallel flow channel width systems such as J, U, and L types are 2.5 K, 5.5 K, and 5.2 K respectively, while the present invention controls the temperature difference of the battery pack within the set temperature difference threshold of 1.5 K during the whole operation process. This example verifies the effectiveness of the present invention for the operation control of the parallel flow channel cooling system.

[0049] Embodiment 3

[0050] As Figure 2 shown, the basic structure of the air-cooled battery thermal management system in this embodiment is the same as that in Embodiment 1, but the width of the flow channel and the position of the heat source distribution are different. In this example, C1 = 0.8, and the parallel flow channel width distribution [d1, d2, …, d 12 , d 13 are [2.5, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 3.1, 2.5] in sequence, with the unit of mm. The positions of the heat source center line 12 are [10.5, 29.6, 48.7, 67.8, 86.9, 106, 125.1, 144.2, 163.3, 182.4, 201.5, 220.6, 239.7], with the unit of mm. The positions of the outlet center line 13 are l1 = 0, l2 = 115.5 mm, l3 = 231 mm respectively, and the positions of the center lines 14 of adjacent outlets are x1 = 57.75 mm and x2 = 173.25 mm respectively. The temperature difference threshold, deviation and monitoring time step Δt are respectively set as T lim = 1.0 K, Δε = 0.01 K, Δt = 1 s, and the strategy for controlling the opening and closing of the valve is the same as that in Embodiment 1.

[0051] Figure 4 It is the variation relationship of the temperature difference of the battery pack with time. The results show that under the control strategy of the present invention, the switching sequence of the system flow pattern is J, U, J type in turn. The temperature differences of the battery packs in the parallel flow channel width systems such as J, U, and L types are 2.4K, 5.1K, and 4.3K respectively, while the present invention controls the temperature difference of the battery pack within the set temperature difference threshold of 1.0K during the whole operation process. This example verifies the effectiveness of the present invention for the operation control of the parallel flow channel cooling system.

[0052] The above is only a preferred embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any person skilled in the art within the scope disclosed by the present invention, according to the technical solution and inventive concept of the present invention, makes equivalent substitutions or changes, all belong to the protection scope of the present invention.

Claims

1. A parallel flow channel cooling system, characterized in that, It includes an inlet section, an inlet manifold, a number of parallel flow channels, a number of heat sources, an outlet manifold, and a number of outlet sections; the inlet section is connected to the inlet manifold, and the inlet manifold and the outlet manifold are connected through the parallel flow channels; the number of outlet sections are respectively connected to the outlet manifold; the number of parallel flow channels are distributed on the left and right sides of each heat source and are perpendicular to the inlet manifold and the outlet manifold; the inlet section is connected to the inlet manifold in parallel, the number of outlet sections is M, where M≥3, and each outlet section is provided with a valve; the first outlet section and the Mth outlet section are respectively connected to the outlet manifold in parallel, and the second valve to the (M - 1)th valve outlet sections are vertically connected to the middle of the outlet manifold; the inlet section, the first outlet section, and the Mth outlet section are on a horizontal line, and the 2nd to (M - 1)th outlet sections are on a horizontal line with the parallel flow channels; To implement an operation control method for a parallel flow channel cooling system, which includes the following steps: The system cooling working medium flow rate is any value and changes during operation; a temperature difference threshold T is set. lim , a deviation Δε and a monitoring time step Δt are set; monitoring points are set in each heat source, and the temperature of each monitoring point is recorded every Δt time during operation, denoted as T1, T2, …, T N , where N is the number of heat sources. Calculate the temperature difference ΔT between heat sources based on the temperatures at the monitoring points max = max(T1, T2, …, T N ) - min(T1, T2, …, T N ); At the initial moment, open the first valve and the Mth valve, and close the second valve to the (M - 1)th valve; Monitor the temperature difference value ΔT max , when ΔT max ≥ T lim - Δε, control the opening and closing of the valves according to the following strategy: Assume that the centerline position of the i-th outlet is l i , where i = 1, 2, …, i, …, M, and l1 = 0, l M = L; the center position of the centerlines l i and l i+1 of two adjacent outlets is x i = (l i + l i+1 ) / 2. Then x i divides the system into M segments: [0, x1), [x1, x2), …, [x i , x i+1 ), …, [x M-2 , x M-1 ), [x M-1 , L]. Denote the centerline position of the heat source where the temperature of the monitoring point is the highest as x max . Then If 0 ≤ x max <x1, open the first valve, close the second valve to the Mth valve, and switch to the U-shaped system; If x i ≤ x max < x i+1 , open the (i + 1)-th valve, close the remaining valves, and switch to the L-type system; If x M-1 ≤ x max ≤ L, open the first valve and the Mth valve, close the second valve to the (M - 1)th valve, and switch to the J-type system.

2. The parallel flow channel cooling system according to claim 1, wherein The widths of the leftmost and rightmost flow channels among the number of parallel flow channels are the same, and the widths of the remaining parallel flow channels are the same. The width ratio of the parallel flow channels is [C1, 1, 1, …, 1, 1, C1], where the value range of C1 is (0, 1).

3. The parallel flow path cooling system according to claim 1, characterized in that, Valves are provided at each outlet. The valve at the ith outlet is valve i, i = 1, 2, …, i, …, M. According to the opening and closing of the valves to switch different flow patterns of the system, the system is divided into three flow patterns, namely J-type, U-type, and L-type; when the first valve and the Mth valve are open and the second valve to the (M - 1)th valve are closed, the system flow pattern is J-type; when the first valve is open and the second valve to the Mth valve are closed, the system flow pattern is U-type; when the ith valve is open, where i = 2 to M - 1 and the remaining valves are closed, the system flow pattern is L-type.

4. The parallel flow channel cooling system according to claim 1, wherein, At the initial moment of system operation, the first valve and the Mth valve are opened, and the second valve to the (M - 1)th valve are closed, and the system flow pattern is J-type.

5. The parallel flow channel cooling system according to claim 1, characterized in that, Monitoring points are arranged at each heat source, and the temperature of the monitoring points is obtained through theoretical models, numerical calculations, or experimental tests. This temperature is the temperature of a certain point of the heat source or the average temperature of a single heat source.

6. The parallel flow channel cooling system according to claim 1, characterized in that, The temperature difference threshold T lim is any value greater than 0, and the monitoring time step Δt is any value greater than 0; the deviation Δε is proportional to Δt and satisfies Δε = C2Δt, where the value range of C2 is (0, T lim / Δt).

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