Coolant flow matching method, system and application thereof

Abstract

The application provides a cooling liquid flow matching method and system and application thereof, and the method comprises the following steps: establishing a double-parameterized model, the double-parameterized model comprising a heat transfer correlation model between cooling liquid flow and heat transfer coefficient, and a flow resistance model between cooling liquid flow and pressure drop; determining a numerical interval of the heat transfer coefficient and a numerical interval of the pressure drop in a preset working interval of the cooling liquid flow, so as to calibrate parameters of the heat transfer correlation model and parameters of the flow resistance model by using multiple groups of cooling liquid flow values, corresponding heat transfer coefficient values and corresponding pressure drop values; and determining an optimal matching value of the cooling liquid flow based on the calibrated heat transfer correlation model, the calibrated flow resistance model and a coupling relationship between the heat transfer coefficient and the pressure drop. The application solves the problem that in the prior art, due to the fact that the test design only covers discrete flow points in a local high heat transfer area, it is difficult to directly fit the quantitative law of the cooling liquid flow, heat transfer power and pressure drop, and the optimal flow point positioning fails.

Description

Technical Field

[0001] This invention relates to the field of battery thermal management technology for new energy vehicles, and in particular to a method, system and application of coolant flow matching. Background Technology

[0002] In the battery cooling system of new energy passenger vehicles, the coolant flow rate is a key factor determining the battery's heat exchange power and pressure drop. When the refrigerant inlet pressure, inlet subcooling, outlet pressure, outlet superheat, and coolant inlet temperature remain constant, the system exhibits forced thermal equilibrium characteristics: an increase in coolant flow rate leads to an increase in the heat exchange power on the coolant side, and to maintain thermal equilibrium, the refrigerant flow rate must be increased simultaneously, thereby increasing the heat exchange power on the refrigerant side; under a fixed inlet pipe diameter, an increase in refrigerant flow rate inevitably leads to an increase in flow velocity and causes a significant increase in pressure drop.

[0003] It is important to emphasize that the above changes exhibit a strict nonlinear critical effect: within a reasonable range, increasing the coolant flow rate can simultaneously improve the refrigerant heat transfer power and pressure drop; however, if it enters an excessive range, the increase in heat transfer power will be suppressed and gradually stabilize due to the attenuation effect of the coolant-refrigerant temperature difference, while the growth rate of the frictional pressure drop in the two-phase flow will decrease sharply. This nonlinear mechanism reveals the core contradiction—when the coolant flow rate changes, the refrigerant heat transfer coefficient and pressure drop exhibit a non-cooperative evolution law. Therefore, the essence of flow rate matching is a trade-off optimization between improving heat transfer performance and the surge in flow resistance. Due to limitations in the power of the electric water pump and the flow channel resistance, the coolant flow rate operating range is generally constrained to 0~40L / min; however, existing methods have multiple defects because they ignore this contradiction: firstly, because the experimental design only covers discrete flow points in local high heat transfer zones, it is difficult to directly fit the quantitative law of coolant flow rate, heat transfer power, and pressure drop, leading to the failure of optimal flow point location; secondly, blindly increasing the flow rate results in a pump power consumption increase far exceeding the heat transfer benefit.

[0004] Therefore, it is necessary to improve the existing coolant flow matching scheme to solve the above-mentioned technical problems. Summary of the Invention

[0005] The purpose of this invention is to provide a coolant flow matching method, system and application, to solve the problem in the prior art that the experimental design only covers discrete flow points in local high heat exchange zones, making it difficult to directly fit the quantitative law of coolant flow rate and heat exchange power and pressure drop, resulting in the failure of optimal flow point positioning.

[0006] Meanwhile, the present invention can achieve an optimized balance between energy consumption and heat transfer through a precise flow matching model, thereby solving the defect of existing methods where the increase in pump power consumption far exceeds the heat exchange benefits when the flow rate is blindly increased.

[0007] To achieve the above objectives, in a first aspect, a method for matching coolant flow rate is provided, the method comprising:

[0008] A two-parameter model is established, which includes a heat transfer correlation model between coolant flow rate and heat transfer coefficient, and a flow resistance model between coolant flow rate and pressure drop;

[0009] Within a preset working range of coolant flow rate, the numerical range of the heat transfer coefficient and the numerical range of the pressure drop are determined, so as to calibrate the parameters of the heat transfer correlation model and the parameters of the flow resistance model using multiple sets of coolant flow rate values, corresponding heat transfer coefficient values, and corresponding pressure drop values.

[0010] The optimal matching value of coolant flow rate is determined based on the calibrated heat transfer correlation model, the calibrated flow resistance model, and the coupling relationship between the heat transfer coefficient and the pressure drop.

[0011] As a further improvement of the present invention, determining the numerical range of the heat transfer coefficient and the numerical range of the pressure drop within a preset operating range of the coolant flow rate includes:

[0012] Multiple flow points are selected within the preset working range to measure the heat exchange power and pressure drop corresponding to each flow point;

[0013] The heat transfer coefficient corresponding to each flow point is determined based on the heat exchange power, the numerical range of the heat transfer coefficient is determined based on the heat transfer coefficient of each flow point, and the numerical range of the pressure drop is determined based on the pressure drop of each flow point.

[0014] As a further improvement of the present invention, the parameters of the heat transfer correlation model and the parameters of the flow resistance model are calibrated using multiple sets of coolant flow rate values, corresponding heat transfer coefficient values, and corresponding pressure drop values, including:

[0015] Substitute the heat transfer coefficient values ​​corresponding to different flow points into the heat transfer correlation model to obtain the parameter values ​​of the heat transfer correlation model.

[0016] Substitute the pressure drop values ​​corresponding to different flow points into the flow resistance model to obtain the parameter values ​​of the flow resistance model.

[0017] As a further improvement of the present invention, the heat transfer correlation model is as follows:

[0018] ,

[0019] in, h ( m () represents the heat transfer coefficient corresponding to different cooling flow rates. m Indicates coolant flow rate. a This represents the maximum heat transfer coefficient to be calibrated. b This represents the heat transfer sensitivity coefficient to be calibrated.

[0020] As a further improvement of the present invention, the flow resistance model is as follows:

[0021] ,

[0022] Wherein, △p( m () indicates the pressure drop corresponding to different coolant flow rates. c Indicates the secondary drag coefficient to be calibrated. d Indicates the second-order correction factor to be calibrated. g This represents the linear drag coefficient to be calibrated.

[0023] As a further improvement of the present invention, the optimal matching value of the coolant flow rate is determined based on the calibrated heat transfer correlation model, the calibrated flow resistance model, and the coupling relationship between the heat transfer coefficient and the pressure drop, including:

[0024] By simultaneously solving the calibrated heat transfer correlation model, the calibrated flow resistance model, and the coupling relationship, the optimal matching value of the coolant flow rate is determined.

[0025] The coupling relationship between the heat transfer coefficient and the pressure drop is as follows:

[0026] ,

[0027] in, h 0 represents the baseline heat transfer coefficient. Indicates the reference voltage drop, f ( m The maximum coolant flow rate m As the optimal matching traffic.

[0028] Secondly, a coolant flow matching system is provided, comprising:

[0029] The model building unit is used to build a two-parameter model, which includes a heat transfer correlation model between coolant flow rate and heat transfer coefficient, and a flow resistance model between coolant flow rate and pressure drop.

[0030] The data processing unit is used to determine the numerical range of the heat transfer coefficient and the numerical range of the pressure drop within a preset working range of the coolant flow rate, so as to calibrate the parameters of the heat transfer correlation model and the parameters of the flow resistance model using multiple sets of coolant flow rate values, corresponding heat transfer coefficient values, and corresponding pressure drop values.

[0031] The flow matching unit is used to determine the optimal matching value of the coolant flow rate based on the calibrated heat transfer correlation model, the calibrated flow resistance model, and the coupling relationship between the heat transfer coefficient and the pressure drop.

[0032] Thirdly, a coolant flow matching method is provided for use in new energy vehicles to achieve thermal balance in the coordinated cooling system of the vehicle's power battery pack and drive motor. The coolant flow matching method for the battery cooler is based on the method described in the first aspect.

[0033] Fourthly, a battery cooler for new energy vehicles is provided, wherein the coolant flow matching method of the battery cooler is performed based on the steps described in the first aspect.

[0034] Fifthly, a terminal device is provided, comprising: a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the computer program, when executed by the processor, implements the steps of the method described in the first aspect.

[0035] A sixth aspect provides a computer-readable storage medium on which a computer program is stored, the computer program being executed by a processor to implement the steps of the method described in the first aspect.

[0036] The beneficial effects of this invention are as follows:

[0037] The coolant flow matching method of this invention constructs a dual-parameter model (heat transfer correlation model and flow resistance model) and coordinates the parameters of the two models within a preset working range. Finally, it combines the calibrated dual-parameter model with a coupled decision function of heat transfer coefficient and pressure drop to accurately locate the optimal coolant flow matching value. Thus, this invention not only locates the optimal coolant flow point by fitting the quantitative relationship between coolant flow rate, heat transfer power, and pressure drop through a dual-parameter model established within a preset working range of coolant flow rate, but also achieves an optimized balance between energy consumption and heat transfer through a precise flow matching model. Furthermore, it solves the problem of high experimental costs associated with existing coolant flow matching methods. Attached Figure Description

[0038] Figure 1 This is a schematic flowchart illustrating a coolant flow matching method according to an embodiment of the present invention;

[0039] Figure 2 This is a schematic flowchart illustrating a coolant flow matching method according to another embodiment of the present invention;

[0040] Figure 3 This is a schematic flowchart illustrating a coolant flow matching method according to another embodiment of the present invention;

[0041] Figure 4 This is a schematic diagram showing the relationship between heat transfer coefficient and coolant flow rate;

[0042] Figure 5 This is a schematic diagram showing the relationship between pressure drop and coolant flow rate.

[0043] Figure 6 This is a structural block diagram of a coolant flow matching system according to an embodiment of the present invention;

[0044] Figure 7 This is a schematic structural block diagram of a device for matching coolant flow in a battery cooler, according to an embodiment of the present invention.

[0045] Figure 8 This is a topological diagram of a computer-readable storage medium disclosed in this invention. Detailed Implementation

[0046] The present invention will now be described in detail with reference to the embodiments shown in the accompanying drawings. However, it should be noted that these embodiments are not intended to limit the present invention. Equivalent changes or substitutions in function, method, or structure made by those skilled in the art based on these embodiments are all within the scope of protection of the present invention.

[0047] The technical solutions provided by the various embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

[0048] Example 1:

[0049] like Figure 1 As shown, this embodiment provides a coolant flow rate matching method to solve the problem in the prior art where the experimental design only covers discrete flow rate points in local high heat transfer zones, making it difficult to directly fit the quantitative relationship between coolant flow rate and heat transfer power and pressure drop, leading to the failure of optimal flow rate point location. The method includes:

[0050] Step 101. Establish a two-parameter model, which includes a heat transfer correlation model between coolant flow rate and heat transfer coefficient, and a flow resistance model between coolant flow rate and pressure drop.

[0051] It should be understood that the coolant flow rate of the battery cooler has different functional relationships with the heat transfer coefficient and pressure drop, and each functional relationship has its own parameters to be calibrated in order to determine the heat transfer correlation model and flow resistance model for the corresponding vehicle model based on the calibrated parameters. The heat transfer correlation model is shown in Equation 1:

[0052] , (Formula 1),

[0053] in, h ( m () represents the heat transfer coefficient corresponding to different cooling flow rates. m This indicates the coolant flow rate, in L / min. ，a This represents the maximum heat transfer coefficient to be calibrated. b This represents the heat transfer sensitivity coefficient to be calibrated.

[0054] The flow resistance model is shown in Equation 2:

[0055] , (Formula 2),

[0056] Wherein, △p( m () indicates the pressure drop corresponding to different coolant flow rates. c Indicates the secondary drag coefficient to be calibrated. d Indicates the second-order correction factor to be calibrated. g This represents the linear drag coefficient to be calibrated.

[0057] Step 102. Determine the numerical range of the heat transfer coefficient and the numerical range of the pressure drop within the preset working range of the coolant flow rate, so as to calibrate the parameters of the heat transfer correlation model and the flow resistance model using multiple sets of coolant flow rate values, corresponding heat transfer coefficient values, and corresponding pressure drop values.

[0058] In this embodiment, a test coolant flow rate point is selected within the range of optimal heat exchange performance based on the actual operating range of the battery coolant. The heat exchange power and pressure drop are then tested at the selected flow rate point. Specifically, the operating range of the battery coolant flow rate in this embodiment is 0-40 L / min, with optimal heat exchange performance within the range of 5-24 L / min. It should be noted that the operating range of the coolant flow rate may vary for different vehicle models. This embodiment only uses the operating range of the coolant flow rate for a specific vehicle model as an example to illustrate the principle of coolant flow rate matching; the specific values ​​are not limited to the range defined in this embodiment.

[0059] like Figure 2 As shown, the specific operations for "determining the numerical range of the heat transfer coefficient and the numerical range of the pressure drop within the preset operating range of the coolant flow rate" include:

[0060] Step 201. Select multiple flow points within the preset working range to measure the heat exchange power and pressure drop corresponding to each flow point.

[0061] Under the premise of keeping the test parameters such as refrigerant inlet pressure and temperature, outlet pressure and temperature, and coolant inlet temperature constant, the battery coolant flow rate points at equal intervals were selected within the flow rate range with better heat exchange performance for testing. In this embodiment, 5, 10, 15, and 20 L / min were selected as coolant flow rate points for testing, and each flow rate point was measured at least three times. The test results are shown in Table 1.

[0062] Table 1. Average measured values ​​of heat exchange power and pressure drop under different coolant flow rates:

[0063] Coolant flow rate (L / min) 5 10 15 20 Heat exchange power (W) 6210.2 9542.1 11355.1 12577.3 Pressure drop (kPa) -32.6 -71.7 -96.3 -117.3 .

[0064] Step 202. Determine the heat transfer coefficient corresponding to each flow point based on the heat exchange power, determine the numerical range of the heat transfer coefficient based on the heat transfer coefficient of each flow point, and determine the numerical range of the pressure drop based on the pressure drop of each flow point.

[0065] As shown in Table 1, based on the results of the refrigerant heat transfer power corresponding to different coolant flow rates, the heat transfer coefficients of the refrigerant under different coolant flow rates can be calculated to be 3118, 4408, 5060, and 5653 W / (m³). 2 (·℃), thus, the numerical range of the heat transfer coefficient can be determined as [3118, 5653]. Similarly, according to the test results in Table 1, the numerical range of the pressure drop can be determined as [-117.3, -32.6]. It should be noted that different flow points can be selected within the preset working range to obtain different heat transfer coefficients and pressure drops, but all should be within the numerical ranges of the heat transfer coefficient and pressure drop corresponding to the two endpoints of the preset working range. By limiting the numerical ranges of the heat transfer coefficient and pressure drop, it is convenient to calculate the parameters of the heat transfer correlation model and the flow resistance model in subsequent steps without being limited to the few test points limited in this embodiment.

[0066] like Figure 3 As shown, the specific method for "calibrating the parameters of the heat transfer correlation model and the flow resistance model using multiple sets of coolant flow rate values, corresponding heat transfer coefficient values, and corresponding pressure drop values" in step 102 includes:

[0067] Step 301. Substitute the heat transfer coefficient values ​​corresponding to different flow points into the heat transfer correlation model to obtain the parameter values ​​of the heat transfer correlation model.

[0068] Since the heat transfer coefficient obtained in step 202 has a numerical range of [3118, 5653], it has 4 point values. That is, the number of heat transfer coefficients (4) is greater than the parameter to be calibrated (i.e., the maximum heat transfer coefficient to be calibrated). a and the heat transfer sensitivity coefficient to be calibrated b The number of [missing information] is determined by combining the heat transfer coefficients at different coolant flow rates in pairs, resulting in a total [missing information]. Substitute 6 groups into Formula 1, solve each group separately, and then calculate the arithmetic mean to obtain the undetermined coefficients: a =5706.2, b =-0.1447, from which the calibrated heat transfer correlation model can be obtained as shown in Equation 3:

[0069] , (Formula 3),

[0070] Thus, the relationship between coolant flow rate and heat transfer coefficient is fitted according to Formula 3, as follows: Figure 4 As shown, the heat transfer coefficient increases with the increase of coolant flow rate.

[0071] Step 302. Substitute the pressure drop values ​​corresponding to different flow points into the flow resistance model to obtain the parameter values ​​of the flow resistance model.

[0072] Similarly, since the number of pressure drop test results (4) in Table 1 is greater than the parameter to be calibrated (the secondary resistance coefficient to be calibrated), c Secondary correction coefficients to be calibrated d The linear drag coefficient to be calibrated g The number of [unclear], therefore, the pressure drop under different coolant flow rates is combined in three groups, totaling [unclear]. =4 groups, substitute into Formula 2, solve each one and then take the arithmetic mean, we can get c=1.1385, d=0.01346, g=2.26, that is, the functional relationship between coolant flow rate and pressure drop in this embodiment is as shown in Formula 4:

[0073] , (Formula 4),

[0074] Thus, the relationship between coolant flow rate and heat transfer coefficient is fitted according to Formula 4, as follows: Figure 5 As shown, the pressure drop decreases as the coolant flow rate increases.

[0075] Step 103. Determine the optimal matching value of the coolant flow rate based on the calibrated heat transfer correlation model, the calibrated flow resistance model, and the coupling relationship between the heat transfer coefficient and pressure drop. The coupling relationship between the heat transfer coefficient and pressure drop is as follows:

[0076] , (Formula 5),

[0077] in, h 0 represents the baseline heat transfer coefficient. This represents the reference pressure drop. In this embodiment, the reference heat transfer coefficient... h 0 represents the heat transfer coefficient at a coolant flow rate of 5 L / min, and the reference pressure drop. This represents the pressure drop at a coolant flow rate of 5 L / min.

[0078] Since the coolant flow rate has opposite effects on the heat transfer coefficient and pressure drop, coordinated matching is required. This means ensuring a large heat transfer coefficient at the optimal flow rate matching value to be determined, while also ensuring a small pressure drop. Generally, the coupling relationship between the heat transfer coefficient and pressure drop is established by determining the maximum ratio of the heat transfer coefficient to the pressure drop or the minimum ratio of the pressure drop to the heat transfer coefficient.

[0079] In this embodiment, the ratio of heat transfer coefficient to pressure drop is used. f As an evaluation indicator, in f Coolant flow rate at maximum value m To achieve optimal traffic matching, the specific operation process is as follows:

[0080] (1) Calculation formula 5 f ( m ) right m The derivative of is denoted as . f ′( m );

[0081] (2) Assume the derivative is zero and solve the equation: f ′( m ) = 0, find m Value, at this time m The value represents the optimal matching traffic.

[0082] Thus, the battery cooler flow rate can be obtained. m At 18.21 L / min f The maximum value is 1.132. At this point, the refrigerant heat exchange power is 5296.95W and the pressure drop is 110.26kPa. In this embodiment, the optimal coolant flow rate is 18.2L / min, which ensures a large heat transfer coefficient and a small pressure drop under this optimal flow rate, so as to accurately achieve an optimized balance between energy consumption and heat transfer.

[0083] Therefore, the coolant flow matching method in this embodiment constructs a dual-parameter model (heat transfer correlation model and flow resistance model) and coordinates the parameters of the two models within a preset working range. Finally, it combines the calibrated dual-parameter model with a coupled decision function of heat transfer coefficient and pressure drop to accurately locate the optimal coolant flow matching value. Thus, this embodiment, through the method of undetermined coefficients, can not only fit the relationship between coolant flow rate, heat exchange power, and pressure drop based on the dual-parameter model established within the preset working range of coolant flow rate, thereby obtaining the optimal coolant flow rate with the best overall heat exchange performance, solving the deficiency of existing matching schemes in being insufficient to locate the optimal coolant flow rate point, but also accurately achieves the optimized balance between energy consumption and heat transfer, while also solving the problem of high experimental costs in existing coolant flow matching methods.

[0084] It is worth noting that the "specific values ​​or ranges (operating range of coolant, range of heat transfer coefficient, range of pressure drop, etc.)" involved in the coolant flow matching method described in this embodiment are only for the convenience of explaining the matching principle of coolant flow, and their specific values ​​are not limited to the values ​​or ranges defined in this embodiment.

[0085] Example 2:

[0086] like Figure 6As shown, this embodiment also provides a coolant flow matching system 600, which includes: a model building unit 601, used to build a dual-parameter model, the dual-parameter model including a heat transfer correlation model 6011 between coolant flow and heat transfer coefficient, and a flow resistance model 6012 between coolant flow and pressure drop; a data processing unit 602, used to determine the numerical range of heat transfer coefficient and pressure drop within a preset working range of coolant flow, so as to calibrate the parameters of the heat transfer correlation model and the flow resistance model using multiple sets of coolant flow values, corresponding heat transfer coefficient values, and corresponding pressure drop values; and a flow matching unit 603, used to determine the optimal matching value of coolant flow based on the calibrated heat transfer correlation model, the calibrated flow resistance model, and the coupling relationship between heat transfer coefficient and pressure drop.

[0087] The data processing unit 602 includes a data measurement unit 6021, which is used to select multiple flow points within a preset working range to measure the heat exchange power and pressure drop corresponding to each flow point; and a data determination unit 6022, which is used to determine the heat transfer coefficient corresponding to each flow point based on the heat exchange power, to determine the numerical range of the heat transfer coefficient based on the heat transfer coefficient of each flow point, and to determine the numerical range of the pressure drop based on the pressure drop of each flow point.

[0088] The coolant flow matching system 600 of this embodiment constructs a dual-parameter model (heat transfer correlation model and flow resistance model) through a model building unit 601, and coordinates the parameters of the two models within a preset working range through a data processing unit 602. Finally, the flow matching unit 603 accurately locates the optimal coolant flow matching value by combining the calibrated dual-parameter model with the coupled decision function of heat transfer coefficient and pressure drop. Thus, the system 600 of this embodiment, through the method of undetermined coefficients, can not only fit the relationship between coolant flow rate, heat exchange power, and pressure drop based on the dual-parameter model established within the preset working range of coolant flow rate, thereby obtaining the optimal coolant flow rate with the best overall heat exchange performance, solving the defect of existing matching schemes that are insufficient to locate the optimal flow point of coolant, but also accurately achieves the optimized balance between energy consumption and heat transfer, while solving the problem of high experimental costs of existing coolant flow matching methods.

[0089] It should be noted that the technical solutions of the coolant flow matching system 600 in this embodiment are the same as those in Embodiment 1. Please refer to Embodiment 1 for the technical solutions, which will not be repeated here.

[0090] Example 3:

[0091] This embodiment provides a coolant flow matching method for use in new energy vehicles to achieve thermal balance in the coordinated cooling system of the vehicle's power battery pack and drive motor. The coolant flow matching method for the battery cooler is based on the steps described in Embodiment 1 and can achieve the same technical effect. To avoid repetition, it will not be described again here.

[0092] Example 4:

[0093] like Figure 7 As shown, this embodiment provides a device 700 for matching the coolant flow rate of a battery cooler, comprising: a refrigerant circulation system 701 for regulating battery temperature; a controller 702 for monitoring and regulating the pressure and power of the battery cooler; and a matching system 600 based on the one described in Embodiment 2. The device 700 of this embodiment uses a dual-parameterized model established by the matching system 600 within a preset working range of the coolant flow rate to fit the relationship between the coolant flow rate, heat exchange power, and pressure drop, thereby obtaining the optimal coolant flow rate with the best overall heat exchange performance. This solves the problem that existing matching schemes are insufficient to locate the optimal coolant flow rate point, and can also accurately achieve an optimized balance between energy consumption and heat transfer. Simultaneously, it addresses the problem of high experimental costs associated with existing coolant flow rate matching methods.

[0094] Example 5:

[0095] This invention also provides a terminal device, which may include a processor, a memory, and a computer program stored in the memory and executable on the processor, wherein the computer program, when executed by the processor, implements the above-described functionality. Figure 1-3 The various processes of the coolant flow matching method embodiment shown can achieve the same technical effect, and will not be described again here to avoid repetition.

[0096] Example 6:

[0097] Combination Figure 8 As shown, this embodiment also discloses a specific implementation of a computer-readable storage medium 800. This computer-readable storage medium 800 can be configured wholly or partially in a physical computer, server, cluster server, or data center.

[0098] In this embodiment, the computer-readable storage medium 800 stores computer program instructions 801, which are read and executed by a processor 802 to perform the steps in the coolant flow matching method disclosed in Embodiment 1.

[0099] Optionally, the computer-readable storage medium 800 can be configured as a server, and the server runs on a physical device used to build a private cloud, hybrid cloud, or public cloud. The computer-readable storage medium 800 can also be configured as random access memory (RAM), read-only memory (ROM), programmable read-only memory (PROM), erasable programmable read-only memory (EPROM), electrically erasable programmable read-only memory (EEPROM), etc.

[0100] The computer-readable storage medium 800 is used to store a program, and the processor 802, upon receiving an execution instruction, executes the coolant flow matching method disclosed in Embodiment 1.

[0101] Meanwhile, the processor 802 disclosed in this embodiment may be an integrated circuit chip with signal processing capabilities. The processor 802 can be a general-purpose processor, including a central processing unit (CPU), a network processor (NP), etc.; it can also be a digital signal processor (DSP), an application-specific integrated circuit (ASIC), a field-programmable gate array (FPGA), or other programmable logic devices, discrete gate or transistor logic devices, or discrete hardware components. It can implement or execute the methods, steps, and logic block diagrams disclosed in the embodiments of this invention. The general-purpose processor can be a microprocessor or any conventional processor.

[0102] The technical solution of the same part in the computer-readable storage medium 800 disclosed in this embodiment as in Embodiment 1 and / or Embodiment 2 is described in Embodiment 1 and / or Embodiment 2, and will not be repeated here.

[0103] The detailed descriptions listed above are merely specific descriptions of feasible embodiments of the present invention, and are not intended to limit the scope of protection of the present invention. All equivalent embodiments or modifications made without departing from the spirit of the present invention should be included within the scope of protection of the present invention.

[0104] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0105] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

Claims

1. A method for matching coolant flow rates, characterized in that, The method includes: A two-parameter model is established, which includes a heat transfer correlation model between coolant flow rate and heat transfer coefficient, and a flow resistance model between coolant flow rate and pressure drop; Within a preset working range of coolant flow rate, the numerical range of the heat transfer coefficient and the numerical range of the pressure drop are determined, so as to calibrate the parameters of the heat transfer correlation model and the parameters of the flow resistance model using multiple sets of coolant flow rate values, corresponding heat transfer coefficient values, and corresponding pressure drop values. The optimal matching value of coolant flow rate is determined based on the calibrated heat transfer correlation model, the calibrated flow resistance model, and the coupling relationship between the heat transfer coefficient and the pressure drop.

2. The method according to claim 1, characterized in that, Determining the numerical range of the heat transfer coefficient and the numerical range of the pressure drop within a preset operating range of the coolant flow rate includes: Multiple flow points are selected within the preset working range to measure the heat exchange power and pressure drop corresponding to each flow point; The heat transfer coefficient corresponding to each flow point is determined based on the heat exchange power, the numerical range of the heat transfer coefficient is determined based on the heat transfer coefficient of each flow point, and the numerical range of the pressure drop is determined based on the pressure drop of each flow point.

3. The method according to claim 2, characterized in that, The parameters of the heat transfer correlation model and the flow resistance model are calibrated using multiple sets of coolant flow rate values, corresponding heat transfer coefficient values, and corresponding pressure drop values, including: Substitute the heat transfer coefficient values ​​corresponding to different flow points into the heat transfer correlation model to obtain the parameter values ​​of the heat transfer correlation model. Substitute the pressure drop values ​​corresponding to different flow points into the flow resistance model to obtain the parameter values ​​of the flow resistance model.

4. The method according to any one of claims 1-3, characterized in that, The heat transfer correlation model is as follows: ； in, h ( m ) represents the heat transfer coefficient corresponding to different cooling flow rates, m represents the coolant flow rate, a represents the maximum heat transfer coefficient to be calibrated, and b represents the heat transfer sensitivity coefficient to be calibrated.

5. The method according to claim 4, characterized in that, The flow resistance model is as follows: ； in, denoted by , c represents the pressure drop corresponding to different coolant flow rates, d represents the secondary resistance coefficient to be calibrated, g represents the secondary correction coefficient to be calibrated, and g represents the linear resistance coefficient to be calibrated.

6. The method according to claim 5, characterized in that, The coupling relationship between the heat transfer coefficient and the pressure drop is as follows: ； in, h 0 represents the baseline heat transfer coefficient. The reference pressure drop is represented by the coolant flow rate m corresponding to the maximum coupling relationship f(m), which is taken as the optimal matching flow rate.

7. A coolant flow matching system, characterized in that, The system includes: The model building unit is used to build a two-parameter model, which includes a heat transfer correlation model between coolant flow rate and heat transfer coefficient, and a flow resistance model between coolant flow rate and pressure drop. The data processing unit is used to determine the numerical range of the heat transfer coefficient and the numerical range of the pressure drop within a preset working range of the coolant flow rate, so as to calibrate the parameters of the heat transfer correlation model and the parameters of the flow resistance model using multiple sets of coolant flow rate values, corresponding heat transfer coefficient values, and corresponding pressure drop values. The flow matching unit is used to determine the optimal matching value of the coolant flow rate based on the calibrated heat transfer correlation model, the calibrated flow resistance model, and the coupling relationship between the heat transfer coefficient and the pressure drop.

8. A coolant flow matching method for achieving thermal balance in a coordinated cooling system for the vehicle's power battery pack and drive motor in new energy vehicles, characterized in that... The method for matching the coolant flow rate of the battery cooler is performed based on the method described in any one of claims 1-6.

9. A terminal device, comprising: A memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the computer program, when executed by the processor, implements the steps of the method as described in any one of claims 1-6.

10. A computer-readable storage medium storing a computer program thereon, the computer program, when executed by a processor, implementing the steps of the method as described in any one of claims 1-6.

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