Heat dissipation device for driving system and control method

Abstract

The invention relates to the technical field of heat dissipation of driving systems, in particular to a heat dissipation device for a driving system, which comprises a heat exchange assembly, a second heat exchanger, a first pipe fitting, a second pipe fitting, a pressure generator and a controller, the second heat exchanger is arranged on the driving system so as to exchange heat with the heat exchange assembly when the cooling liquid flows through the first heat exchange space, and the cooling liquid is cooled. According to the heat dissipation device for the driving system, the first heat exchange space and the second heat exchange space are matched with the first pipe fitting, the second pipe fitting and the pressure generator to form a circulation flow channel of cooling liquid, and control is conducted through the controller. The problems that in the prior art, an air cooling system is low in heat dissipation efficiency and is greatly influenced by the external environment are effectively solved, the cooling liquid flows in the circulating flow channel, heat in the driving system can be rapidly taken away under the high-load condition, heat accumulation is reduced, and therefore the heat dissipation efficiency is improved.

Description

Technical Field

[0001] The invention relates to a heat dissipation device for a drive system, and in particular to a heat dissipation device for a drive system and a control method thereof. Background Art

[0002] With the widespread use of electric vehicles, hybrid vehicles and other drive systems, the power demand of the drive system is increasing, and the heating problem of the system is also increasing. Especially under high load conditions, the operating temperature of the drive system tends to rise rapidly, resulting in system performance degradation, reduced efficiency, and even possible equipment damage.

[0003] At present, most drive systems on the market use air cooling to dissipate heat. The air cooling system mainly relies on air convection to remove heat from the drive system. In addition, in some application scenarios where heat is easily accumulated, the air cooling device is often equipped with forced cooling equipment, such as cooling fans.

[0004] However, although air cooling can accelerate cooling by using cooling fans and other equipment, with the increase in the power of the drive system, the efficiency and effect of air cooling have been unable to meet the heat dissipation requirements of modern high-performance drive systems, and the air cooling device is greatly affected by the external environment, especially when the vehicle is at low speed or stopped, the air cooling effect is significantly reduced. Therefore, how to improve the heat dissipation efficiency, reduce the heat accumulation in the system, and ensure the stable operation of the drive system under high load has become a problem that continues to be solved today. Therefore, it is urgent to propose a heat dissipation device and control method for a drive system to solve the above problems. Summary of the invention

[0005] The object of the present invention is to provide a heat dissipation device which can improve heat dissipation efficiency and quickly reduce heat accumulation in a drive system.

[0006] The technical solution adopted by the present invention to solve the above problem is: a heat dissipation device for a drive system, comprising: The heat exchange component includes a first heat exchange space, so that when the coolant flows through the first heat exchange space, the coolant exchanges heat with the heat exchange component to cool the coolant.

[0007] The second heat exchanger is arranged on the driving system, and the second heat exchanger includes a second heat exchange space, so that when the coolant flows through the second heat exchange space, heat is exchanged with the driving system to increase the temperature of the coolant.

[0008] A first pipe, wherein both ends of the first pipe are respectively connected to the first heat exchange space and the second heat exchange space, so that the first heat exchange space is connected to the second heat exchange space through the first pipe.

[0009] A second pipe, two ends of which are respectively connected to the first heat exchange space and the second heat exchange space, so that the first heat exchange space is connected to the second heat exchange space through the second pipe.

[0010] A pressure generator is connected to the first pipe to allow the coolant in the first pipe to flow.

[0011] A controller is connected to the pressure generator and the heat exchange component to control the operation of the pressure generator and the heat exchange component.

[0012] The first heat exchange space in the heat exchange assembly, the second heat exchange space in the second heat exchanger, the inner space of the first pipe and the inner space of the second pipe form a circulation channel for the flow of coolant.

[0013] Preferably, the heat exchange component comprises: A first heat exchanger, wherein the first heat exchange space is arranged inside the first heat exchanger.

[0014] The radiator is arranged outside the first heat exchanger.

[0015] Preferably, the heat dissipation device further includes a first temperature sensor, which is arranged at the driving system to monitor the temperature of the driving system, and the first temperature sensor is connected to the controller.

[0016] Preferably, the driving system is arranged in the second heat exchange space.

[0017] Preferably, the heat dissipation device comprises: The fluid replenisher comprises a fluid replenishing space, and the fluid replenisher is provided with a fluid replenishing port communicated with the fluid replenishing space.

[0018] The injection valve is arranged at the fluid infusion port of the fluid infusion device to control the opening and closing of the fluid infusion port.

[0019] A third pipe, one end of which is connected to the fluid replenisher so that the interior of the third pipe is communicated with the fluid replenishing space, and the other end of the third pipe is communicated with the circulation channel.

[0020] A fourth pipe, one end of which is connected to the fluid replenisher so that the interior of the fourth pipe is communicated with the fluid replenishing space, and the other end of the fourth pipe is communicated with the circulation channel.

[0021] Wherein, the fluid replenishing space of the fluid replenisher, the inner space of the third pipe and the inner space of the fourth pipe constitute a fluid replenishing channel.

[0022] Preferably, the fluid insufflator is provided with an observation port connected to the fluid insufflation space, and a transparent sealing member is provided at the observation port.

[0023] Preferably, the heat dissipation device comprises: The second temperature sensor is arranged on the first pipe to detect the temperature of the coolant flowing through the first pipe, and the second temperature sensor is connected to the controller.

[0024] The third temperature sensor is arranged on the second pipe to detect the temperature of the coolant flowing through the second pipe, and the third temperature sensor is connected to the controller.

[0025] A pressure monitoring component is arranged on the heat dissipation device to detect the liquid pressure in the circulation channel, and the pressure monitoring component is connected to the controller.

[0026] An exhaust valve is communicated with the circulation flow channel.

[0027] An injection device is connected to the fluid replenisher through the injection valve to inject external coolant into the fluid replenisher.

[0028] In particular, a control method of a heat dissipation device includes: The initial injection amount of the coolant is determined according to the total volume of the circulation channel and the liquid replenishment channel.

[0029] The accumulated amount of gas evolution of the coolant is obtained according to the detection data of the second temperature sensor, the detection data of the third temperature sensor and the detection data of the pressure monitoring component.

[0030] The additional injection amount of the coolant is obtained according to the accumulated amount of gas precipitation of the coolant, the detection data of the second temperature sensor, the detection data of the third temperature sensor and the detection data of the pressure monitoring component.

[0031] The injection device is controlled to inject cooling liquid equal to the supplementary injection amount into the liquid replenisher.

[0032] Preferably, the cumulative amount of gas precipitation of the coolant is obtained according to the detection data of the second temperature sensor, the detection data of the third temperature sensor and the detection data of the pressure monitoring component, wherein the step of obtaining the gas precipitation amount is as follows: The initial temperature and the initial pressure of the cooling liquid are recorded, and the initial gas solubility of the cooling liquid at the initial temperature and the initial pressure is determined.

[0033] The real-time temperature is obtained through the detection data of the second temperature sensor and the detection data of the third temperature sensor, and the real-time pressure is obtained through the pressure monitoring component.

[0034] The real-time gas solubility of the coolant is determined according to the real-time temperature and the real-time pressure.

[0035] The real-time volume of the gas precipitated from the coolant is obtained according to the real-time gas solubility, the initial gas solubility and the initial injection amount of the coolant.

[0036] The accumulated amount of gas evolution is obtained according to the running time of the coolant.

[0037] Preferably, the amount of coolant to be replenished is obtained based on the amount of gas precipitated from the coolant, the detection data of the second temperature sensor, the detection data of the third temperature sensor, and the detection data of the pressure monitoring component, wherein the step of obtaining the amount of replenishment is as follows: Calculating the expansion volume of the coolant according to the real-time temperature, the initial temperature and the thermal expansion coefficient of the coolant; The replenishment injection amount of the coolant is obtained according to the accumulated amount of gas precipitation, the expansion volume of the coolant, and the total volume of the circulation channel and the liquid replenishment channel.

[0038] Beneficial effects of the embodiments of the present invention The heat dissipation device for the drive system forms a circulating flow channel for the coolant through the cooperation of the first heat exchange space and the second heat exchange space with the first pipe, the second pipe and the pressure generator, and is controlled by a controller. The technical means effectively solves the problems of low heat dissipation efficiency and greater influence of the external environment of the air cooling system in the prior art. In addition, the heat dissipation device uses liquid cooling to make the coolant flow in the circulating flow channel, which can quickly take away the heat in the drive system under high load conditions and reduce heat accumulation, thereby achieving the technical effect of improving heat dissipation efficiency, maintaining stable operation of the system, enhancing drive system performance and extending equipment service life.

[0039] The control system of the heat dissipation device for the drive system adopts a technical means to determine the initial injection amount of coolant according to the total volume of the circulation flow channel and the replenishment flow channel, and calculate the gas precipitation amount and the coolant replenishment injection amount by detecting data of the second temperature sensor, the third temperature sensor and the pressure sensor, thereby solving the problems of reduced heat dissipation efficiency, insufficient coolant and unstable system operation caused by residual gas in the coolant flow channel in the prior art, and through precise control of the coolant injection amount, the effects of gas discharge and coolant replenishment are achieved in time, thereby improving the heat dissipation efficiency, ensuring the continuous and stable operation of the drive system under high load conditions, and extending the service life of the system equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0040] Figure 1It is a front view of a heat dissipation device in one embodiment of the present invention.

[0041] Figure 2 1 is a top view of a heat dissipation device according to an embodiment of the present invention.

[0042] Figure 3 It is a rear view of the heat dissipation device in the embodiment of the present invention.

[0043] Among them: 100, heat exchange component; 110, first heat exchanger; 120, radiator; 200, second heat exchanger; 300, first pipe fitting; 400, second pipe fitting; 500, pressure generator; 600, controller; 700, fluid replenisher; 800, third pipe fitting; 900, fourth pipe fitting. DETAILED DESCRIPTION

[0044] The specific implementation of the present invention is further described in detail below in conjunction with the accompanying drawings and examples. The following examples are used to illustrate the present invention, but are not intended to limit the scope of the present invention.

[0045] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the scope of protection of the present application. In addition, the terms "first", "second", etc. are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, features defined as "first", "second", etc. may explicitly or implicitly include one or more of the features. In the description created by the present application, unless otherwise specified, "multiple" means two or more.

[0046] In the description of this application, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood by specific circumstances.

[0047] like Figure 1-Figure 3As shown, a heat dissipation device for a drive system is provided in a preferred embodiment of the present application, including a heat exchange component 100, a second heat exchanger 200, a first pipe 300, a second pipe 400, a pressure generator 500, and a controller 600, wherein the heat exchange component 100 includes a first heat exchange space, so that when the coolant flows through the first heat exchange space, the heat exchange component 100 performs heat exchange with the heat exchange component 100 to cool the coolant, the second heat exchanger 200 is arranged on the drive system, and the second heat exchanger 200 includes a second heat exchange space, so that when the coolant flows through the second heat exchange space, the heat exchange with the drive system is performed to heat up the coolant, and the two ends of the first pipe 300 are respectively connected to the first heat exchange space. The first heat exchange space is connected to the second heat exchange space so that the first heat exchange space is communicated with the second heat exchange space through the first pipe 300. Both ends of the second pipe 400 are respectively connected to the first heat exchange space and the second heat exchange space so that the first heat exchange space is communicated with the second heat exchange space through the second pipe 400. The pressure generator 500 is connected to the first pipe 300 so that the coolant in the first pipe 300 flows. The controller 600 is connected to the pressure generator 500 to control the opening and closing of the pressure generator 500. The controller 600 is electrically connected to the pressure generator 500 and the heat exchange component 100, so as to control the operation and start of the pressure generator 500 and the heat exchange component 100.

[0048] In this embodiment, the heat dissipation device for the drive system forms a circulation channel for the coolant through the cooperation of the first heat exchange space and the second heat exchange space with the first pipe 300, the second pipe 400 and the pressure generator 500, and is controlled by the controller 600. This technical means effectively solves the problems of low heat dissipation efficiency and greater influence of the external environment of the air cooling system in the prior art. The heat dissipation device uses liquid cooling, and the coolant flows in the circulation channel. It can quickly take away the heat in the drive system under high load conditions and reduce heat accumulation, thereby achieving the technical effects of improving heat dissipation efficiency, maintaining stable operation of the system, improving drive system performance and extending equipment service life.

[0049] In this embodiment, the heat exchange component 100 is specifically embodied as a heat dissipation assembly. The heat exchange component 100 includes a first heat exchanger 110 and a radiator 120. The first heat exchange space is located inside the first heat exchanger 110, and the radiator 120 is arranged outside the first heat exchanger 110. Among them, the first heat exchanger 110 can be embodied as a heat exchange device such as a cold row and a heat pipe in the implementation method, the first heat exchange space is a flow channel for the coolant to pass through the cold row or the heat pipe, and the radiator 120 is embodied as a heat dissipation fan in the implementation method. The drive system is arranged in the second heat exchanger 200, that is, the drive system is installed in the second heat exchange space. When the drive system includes a drive motor and an electronic control device, the coolant needs to select a non-conductive coolant. The coolant can be a glycol-type coolant in a specific manner. When the second heat exchanger 200 is only arranged outside the drive system and the coolant does not directly contact the components inside the drive system, the coolant can be a water-based coolant. The pressure generator 500 is specifically embodied as a water pump. In order to adapt to the water pump, the first pipe 300 can be divided into two sections. The two sections of the first pipe 300 are respectively connected to the water inlet and the water outlet of the water pump. Figure 2 As shown, it is an existing cooling control module, which is connected to the sensors described later. The controller 600 can control the operation of the radiator 120 and the pressure generator 500 according to the processing of the detection data of each sensor, and can also control the opening and closing of the exhaust valve described later and control the quantitative and precise injection of the injection device.

[0050] In some embodiments, a first temperature sensor (not shown in the figure) is installed at the drive system to monitor the real-time temperature of the drive system, and the first temperature sensor is connected to the controller 600 to feed back the detection data to the controller 600 in real time. The controller 600 can judge whether the pressure generator 500 needs to be started in advance according to the temperature data detected in real time by the first temperature sensor. When the temperature difference value received by the controller 600 from the first temperature sensor exceeds the preset difference value within the preset time, the controller 600 can control the pressure generator 500 to start, so that the coolant in the circulation channel flows. At the same time, the radiator 120 can also be controlled to operate to accelerate the cooling of the first heat exchanger 110. Moreover, when the temperature of the first temperature sensor is too high, the controller 600 receives the temperature value transmitted by the first temperature sensor and exceeds the preset value, and the power of the radiator 120 can be increased to enhance the cooling effect of the radiator 120 on the first heat exchanger 110. It can be understood that the aforementioned preset difference value and preset value should be determined according to the actual operation of the drive system and the application environment.

[0051] In some embodiments, after the heat dissipation device has been running for a period of time, the coolant inside the device will often be lost due to various factors, and the coolant in the circulation channel needs to be replenished in time. Figure 2As shown, the heat dissipation device also includes a fluid replenisher 700, an injection valve (not shown in the figure), a third pipe fitting (800) and a fourth pipe fitting (900), wherein the fluid replenisher 700 includes a fluid replenishing space, the fluid replenisher 700 is provided with a fluid replenishing port connected to the fluid replenishing space, the injection valve is installed at the fluid replenishing port of the fluid replenisher 700, and controls the precise injection of the coolant while controlling the opening and closing of the fluid replenishing port. One end of the third pipe fitting 800 is connected to the fluid replenisher 700 so that the interior of the third pipe fitting 800 is connected to the fluid replenishing space, and the other end of the third pipe fitting 800 is connected to the circulation channel, that is, the other end of the third pipe fitting 800 can be connected to any one of the first heat exchanger 110 or the second heat exchanger 200 or the first pipe fitting 300 or the second pipe fitting 400. One end of the fourth pipe fitting 900 is connected to the fluid replenisher 700 so that the interior of the fourth pipe fitting 900 is connected to the fluid replenishing space, and the other end of the fourth pipe fitting 900 is connected to the circulation channel. Furthermore, the liquid replenishing space of the liquid replenisher 700, the inner space of the third tube 800, and the inner space of the fourth tube 900 are defined as a liquid replenishing flow channel.

[0052] In this embodiment, the injection valve cooperates with the liquid replenisher 700 to controllably and accurately inject the coolant into the circulation channel to replenish the coolant consumed by the heat dissipation device during operation.

[0053] Among them, the refiller 700 is specifically embodied as a refill pot. In some embodiments, the refiller 700 is provided with an observation port (not shown in the figure) connected to the refill space, and a transparent seal (not shown in the figure) is provided at the observation port to facilitate observation of the degree of coolant consumption in the heat dissipation device.

[0054] After the heat dissipation device has been running for a period of time, the coolant undergoes multiple cycles, encountering different temperature and pressure environments during this process. These changes will cause the gas dissolved in the coolant to gradually precipitate. After the gas is precipitated, if it is not discharged in time, bubbles will form in the system, resulting in a decrease in heat dissipation efficiency and even causing gas blockage, hindering the normal circulation of the coolant. Based on the above reasons, the gas precipitated in the heat dissipation device needs to be discharged in time. In addition, during the circulation of the coolant, the coolant will also be lost, including evaporation loss, loss caused by gas precipitation and leakage loss. Among them, with regard to evaporation loss, although modern cooling systems are usually sealed, under high temperature conditions, especially water-based coolants, due to the low boiling point of water, part of the coolant may evaporate. If the sealing of the system is not perfect, the water in the coolant will escape in the form of vapor through tiny leaks or system connections, resulting in coolant loss. In addition, as the coolant temperature rises and the pressure fluctuates, the dissolved gas in the coolant will precipitate to form bubbles. When these gases are discharged from the heat sink, especially when the heat sink has an exhaust valve, the gas may take away a small amount of coolant at the same time, resulting in overall coolant loss. The seals, pipe interfaces or heat exchangers in the heat sink may have tiny leaks due to aging, damage or loose connections during long-term operation. These leaks will also cause the coolant to escape from the system in liquid or gaseous form, resulting in gradual loss of the coolant. Although the above loss factors may not be obvious in the short term, the loss of coolant will gradually accumulate after the cooling device has been running for a long time. Therefore, it is necessary to check the amount of coolant regularly and replenish it appropriately to ensure the normal operation of the cooling device.

[0055] Based on the above reasons, the heat dissipation device also includes a second temperature sensor (not shown in the figure), a third temperature sensor (not shown in the figure), a pressure monitoring component (not shown in the figure), an exhaust valve (not shown in the figure) and an injection device (not shown in the figure). The second temperature sensor is installed on the first pipe 300, and is used to detect the temperature of the coolant flowing through the first pipe 300 in real time, wherein the temperature of the coolant flowing through the first pipe 300 is defined as the first temperature, and the second temperature sensor is electrically connected to the controller 600; the third temperature sensor is installed on the second pipe 400, and is used to detect the temperature of the coolant flowing through the second pipe 400 in real time, wherein the temperature of the coolant flowing through the second pipe 400 is defined as the second temperature, and the third temperature sensor is connected to the controller 600; the pressure monitoring component is installed on the heat dissipation device, and is used to detect the temperature of the coolant flowing through the second pipe 400 in real time. The liquid pressure in the circulation channel is detected, and the pressure monitoring component is connected to the controller 600 to receive the detection data of the pressure monitoring component. The first pipe fitting 300 or the second pipe fitting 400 is constructed with a connection port connected to itself, and the exhaust valve is installed at the connection port, and the exhaust valve is connected to the controller 600. The exhaust valve is specifically embodied as an electric exhaust valve, and its operating state is controlled by the controller 600; the injection device is connected to the refiller 700 through the injection valve to inject external coolant into the refiller 700, and pass into the circulation channel through the third pipe fitting 800 or the fourth pipe fitting 900.

[0056] In some embodiments, the pressure monitoring assembly includes a plurality of pressure sensors (not shown in the figure), some of which are installed at various corners of the circulation channel, for example, gas sensors are installed at dead corners of the circulation channel or places where gas is easily gathered to detect the residual gas in real time. It should be further explained that because the gas density is much smaller than the liquid density, the precipitated gas will be suspended above the fluid. Therefore, the detection end of the pressure sensor installed at each corner should be set close to the gas suspension area at the top of the circulation channel to facilitate the detection of the low pressure area after the precipitated gas floats up. The discharge degree of the precipitated gas in the circulation channel can be judged by detecting the low pressure area at the corner of the circulation channel. The other pressure sensors are respectively installed at the first pipe 300 and the second pipe 400 to detect the fluid pressure in the circulation channel.

[0057] In some embodiments, the exhaust valve is a gas-liquid separation valve, which can discharge the gas precipitated from the coolant while limiting the discharge of the fluid, and the exhaust valve can be an electric exhaust valve, which can be connected to the controller 600 to control the opening and closing of the exhaust valve through the controller 600, thereby controlling the discharge of the precipitated gas; the fluid replenisher 700 can be a fluid replenishment pot, and the fluid replenishment space is the space inside the fluid replenishment pot; the injection device can be embodied in the implementation method as a precision liquid injection pump, a quantitative fluid replenishment device, an injection system in which an electronically controlled proportional valve and a flow meter cooperate, etc. Taking the precision liquid injection pump as an example, it is composed of a gear pump, a peristaltic pump or a plunger pump. These pump types are widely used in the industrial field to control fluid injection. They have good pressure control accuracy, especially the plunger pump, which can achieve precise fluid injection under high pressure environment and can withstand large back pressure. It is very suitable for injecting coolant into the circulation channel when pressurization is required. These pumps have good flow control capabilities, can adjust the amount of liquid injected, and maintain the pressure required by the system. Some equipment is also equipped with a feedback control device connected to the controller 600, which can automatically adjust the injection amount.

[0058] In some embodiments, after the heat dissipation device has been running for a period of time, as the gas of the coolant is precipitated, it is necessary to timely inject coolant into the circulation flow channel through the injection device, and cooperate with the exhaust valve to discharge the precipitated gas from the circulation flow channel. Based on this, it is necessary to design a heat dissipation device control method for controlling the replenishment of coolant and the discharge of precipitated gas. The specific steps are as follows: Step 1: Determine the initial injection volume of the coolant based on the total volume of the circulation channel and the liquid replenishment channel.

[0059] Step 2: deriving the cumulative amount of gas evolution of the coolant according to the detection data of the second temperature sensor, the detection data of the third temperature sensor and the detection data of the pressure monitoring component.

[0060] Step three: derive the amount of coolant to be added based on the amount of gas released from the coolant, the detection data of the second temperature sensor, the detection data of the third temperature sensor, and the detection data of the pressure monitoring component.

[0061] Step 4: Control the injection device to inject the coolant equal to the supplementary injection amount into the liquid replenisher 700.

[0062] Among them, step 1: determining the initial injection amount of the coolant according to the total volume of the circulation channel and the liquid replenishment channel, which can be obtained specifically through the following steps: When determining the amount of coolant to be injected, the initial amount of coolant to be injected needs to be determined based on the total volume of the circulation channel and the refill channel. In addition, because the operating temperature range of the automotive drive motor is between 60°C and 100°C, the thermal expansion change of the pipes and other components of the heat sink within this temperature range is small, so there is no need to consider the effect of the thermal expansion of the heat sink on the injection amount. Therefore, the calculation of the initial amount of coolant to be injected is mainly based on the geometry and volume of the channel. The steps for calculating the total volume of these two parts are as follows: The volume of the circulation channel: The circulation channel includes the internal space of the first pipe 300, the internal space of the second pipe 400, the first heat exchange space in the first heat exchanger 110, and the second heat exchange space in the second heat exchanger 200. The size of these spaces can be obtained by geometric calculation or determined according to the manufacturer's rated capacity, or the amount of fluid injection required to fill the circulation channel and the infusion channel can be determined by cooperating with the pressure detection component. Take the circulation channel volume obtained by geometric calculation and according to the manufacturer's rated capacity as an example: The volume of the internal space of the first pipe 300 and the volume of the internal space of the second pipe 400 can be obtained by the following formula: .

[0063] in: : The volume of the pipeline.

[0064] : The inner diameter of the pipe.

[0065] : The length of the pipeline.

[0066] The inner diameter of the above pipe and length All of these can be obtained by measuring or consulting the design drawings. When there is a bend in the pipe fitting, just adjust the pipe length. It can be replaced with the centerline arc length of the curved part of the pipe, which can usually be obtained from the design drawings.

[0067] The volume of the first heat exchange space in the first heat exchanger 110 and the volume of the second heat exchange space in the second heat exchanger 200 can usually be obtained through parameters calibrated by the manufacturer.

[0068] The total volume of the circulation channel is the sum of the volume of the internal space of the first pipe 300, the volume of the internal space of the second pipe 400, the volume of the first heat exchange space in the first heat exchanger 110, and the volume of the second heat exchange space in the second heat exchanger 200: .

[0069] The infusion channel mainly includes the volume of the infusion space in the infusion device 700, the volume of the internal space of the third tube 800, and the volume of the internal space of the fourth tube 900. The calculation method of the volume of the internal space of the third tube 800 and the volume of the internal space of the fourth tube 900 is the same as the calculation method of the volume of the internal space of the first tube 300. The volume of the infusion space in the infusion device 700 can be obtained through the parameters calibrated by the manufacturer. The volume of the infusion device 700 can be obtained through the parameters calibrated by the manufacturer. Therefore, the total volume of the infusion channel is .

[0070] Therefore, the total volume of the circulation channel and the fluid replenishment channel is , and because , therefore, the initial charge (full fill) of coolant can be determined from the total volume.

[0071] Step 2: The cumulative amount of gas precipitation of the coolant is obtained based on the detection data of the second temperature sensor, the detection data of the third temperature sensor and the detection data of the pressure monitoring component. The amount of gas precipitation of the coolant is related to the type of coolant and the real-time changes of the temperature and pressure in the circulation channel. It can be specifically obtained by the following gas precipitation calculation formula: .

[0072] in: : Cumulative amount of gas precipitation in the coolant (unit: cubic meter).

[0073] : The initial volume of the coolant (in cubic meters). This volume can be obtained through previous calculations.

[0074] : Coolant in initial condition (temperature ,pressure ) in gas solubility under the condition of , the unit is gas volume / liquid volume, this value can be found in the coolant database.

[0075] : Coolant temperature in real time and pressure The gas solubility under , the unit is the same as above, this value is obtained through the coolant solubility database.

[0076] : Initial temperature and pressure values, detected values ​​when the system is not running.

[0077] : Real-time temperature and pressure are obtained through the second temperature sensor, the third temperature sensor and the pressure monitoring component respectively, and updated in real time.

[0078] : Time interval, refers to the time cumulative effect of gas evolution.

[0079] Henry's law states that the solubility of a gas is proportional to pressure and temperature. By comparing the change in gas solubility between the initial state and the current state of the coolant, the amount of gas precipitated in the coolant can be determined.

[0080] The solubility database is obtained through a large number of experiments on the gas solubility of various types of coolants under various temperature and pressure conditions. Users can check the corresponding gas solubility of various types of coolants under specific temperature and pressure from the database.

[0081] Furthermore, the formula is added , which means that the system can collect data regularly and calculate the cumulative gas precipitation amount, and then perform exhaust operation after the gas precipitation reaches a certain value.

[0082] It should be noted that the use of real-time temperature and pressure data is due to the different amounts of gas precipitation of the coolant at different temperatures, and the temperature of the coolant in the first pipe 300 and the temperature of the coolant in the second pipe 400 are significantly different during the operation of the heat dissipation device. Therefore, the temperature change process of the coolant in the first pipe 300 and the second pipe 400 needs to be considered during the calculation, which can be calculated in the following way: Temperature calculation: Assuming that the second temperature sensor The temperature of the coolant after passing through the heat exchange component 100 (cooling) is read. The third temperature sensor The reading is the temperature of the coolant after passing through the second heat exchanger 200 (heating), the average temperature of the coolant It can be obtained by weighted average calculation: .

[0083] Then, As real-time temperature input to the solubility calculation: .

[0084] Pressure calculation: pressure data is acquired in real time through the pressure monitoring component (ie, obtained through pressure sensors installed at the first pipe 300 and the second pipe 400, etc., and the detection data of multiple pressure sensors can be obtained through weighted average calculation).

[0085] Also, the initial pressure With current pressure The difference can be used to verify the rationality of the amount of gas precipitation. When the heat dissipation device is running, if a pressure drop is detected, it can be inferred that there is gas precipitation. The amount of gas precipitation can be verified by the following methods: .

[0086] By comparing the pressure change with the amount of gas released from the coolant, if the calculated release amount and the pressure change are within a preset range, it can be confirmed that the calculation of the gas release amount is reasonable.

[0087] In summary, the complete calculation process of the gas precipitation amount of the coolant is as follows: Initial condition acquisition: When the system is not running, record the initial temperature of the coolant , initial pressure and initial volume .

[0088] Real-time data acquisition: via a second temperature sensor and the third temperature sensor And the pressure monitoring component obtains temperature and pressure data in real time.

[0089] Call database: through the coolant database, according to the real-time temperature and pressure Check the current solubility of the coolant .

[0090] Calculate the amount of gas released: Use the formula to calculate the amount of gas released , and the cumulative amount of gas released is calculated by combining the time cumulative effect.

[0091] Furthermore, the calculation of the amount of gas released can be verified by the pressure difference: the calculated amount of gas released is compared with the pressure difference recorded by the pressure sensor to ensure the accuracy of the calculation.

[0092] The above-mentioned coolant gas precipitation method dynamically calculates the coolant gas precipitation through real-time monitoring of temperature and pressure data and calling the coolant database. The time accumulation effect in the formula ensures that the gas precipitation amount gradually accumulates until enough gas is discharged, and the system can proceed to the next step of exhaust and refilling operations.

[0093] The establishment of a solubility database is a complex process that involves experimental measurements of the gas solubility of different types of coolants under different temperature and pressure conditions. This process usually includes the following steps: experimental design, data collection, model building, and database creation. The following is the process of establishing a solubility database, as well as the specific methods of each step.

[0094] First, you need to define the coolant types to be covered in the database. Common coolant types include: ethylene glycol-water mixtures (e.g. 70% ethylene glycol + 30% water), propylene glycol-water mixtures, deionized water, special coolants (some industrial or automotive special coolants, which may contain special additives), etc.

[0095] Next, once these coolant types are determined, their gas solubility under different temperature and pressure conditions is experimentally measured.

[0096] The core of solubility measurement is based on Henry's law, which states that the solubility of a gas in a liquid is proportional to the partial pressure of the gas in the liquid. The formula is as follows: .

[0097] in: C is the solubility of the gas (unit: mol / L or g / L), which indicates the volume of gas that can be dissolved per liter of coolant at a specific temperature and pressure.

[0098] is the Henry's constant, which is a temperature-dependent coefficient. Different coolants have different Henry's constants.

[0099] is the partial pressure of the gas.

[0100] By experimentally measuring the solubility at different temperatures and pressures, the Henry constant of the coolant can be obtained , and use this constant to calculate the solubility of the gas.

[0101] The experimental process can be carried out through the following steps: Prepare coolant sample: Select the type of coolant to be tested and prepare a sufficient volume of coolant sample in the experimental environment.

[0102] The experimental equipment includes: An autoclave or solubility tester is used to control the temperature and pressure of the environment in which the coolant is located.

[0103] Gas volume measuring devices, such as gas flow meters or micro bubble detectors, are used to measure the amount of gas that can be dissolved in the coolant at different temperatures and pressures.

[0104] Temperature sensors and pressure sensors are used to accurately monitor environmental conditions during experiments.

[0105] Experimental steps: First, place a sample of the coolant in a high-pressure reactor. Next, set specific temperature and pressure conditions, and change the partial pressure of the gas above the coolant by adjusting the pressure in the reactor. Then, start gradually adding gas (usually air or a specific gas, such as nitrogen or oxygen) to the coolant until the coolant reaches a saturated dissolved state, and record the volume of gas at this time. Finally, repeat the experiment, changing the temperature (for example, different temperature points from -20°C to 120°C) and pressure (for example, from 1 atmosphere to 10 atmospheres) conditions, and record the amount of dissolved gas under each condition.

[0106] At each temperature and pressure condition, record the volume or mass of gas dissolved in the coolant. Perform multiple experiments to obtain solubility at different pressures and repeat this operation at different temperatures.

[0107] Among them, the above experimental results can be used to solve the Henry constant of the coolant , using the data obtained from multiple experiments, plot the gas solubility With pressure The slope is the Henry constant . And, it can be found in experiments that Henry's constant changes with temperature. According to the empirical formula: .

[0108] in: It is the temperature Henry's constant under .

[0109] is the Henry's constant at base temperature.

[0110] It is the enthalpy change when a gas dissolves, which indicates the energy released or absorbed during the gas dissolution process.

[0111] is the gas constant.

[0112] Through the above formula, the experimentally measured solubility data can be fitted to the Henry constant at different temperatures, and then the gas solubility at different temperatures and pressures can be calculated through the model.

[0113] In summary, by designing experiments, measuring the gas solubility of different coolants under various temperature and pressure conditions, and fitting the experimental data into the Henry constant model, a coolant solubility database can be constructed. This database can be used as a core tool in the coolant system to help calculate the amount of gas precipitation in actual operation, thereby ensuring that the coolant replenishment and exhaust operations can be carried out accurately.

[0114] Step 3: According to the amount of gas released from the coolant, the detection data of the temperature sensor, and the detection data of the pressure monitoring component, the amount of coolant to be added can be obtained through the following steps: First, the total volume of the circulation channel and the fluid replenishment channel is a known fixed value and can be obtained according to step 1.

[0115] Secondly, calculate the expansion volume of the coolant, based on the real-time temperature and initial temperature, using the thermal expansion coefficient of the coolant , calculate the volume of the coolant after expansion. The formula is as follows: .

[0116] in: is the initial coolant volume (i.e. the total volume in the circulation channel and the replenishment channel).

[0117] is the coefficient of thermal expansion of the coolant.

[0118] and They are real-time temperature and initial temperature respectively.

[0119] Then, the amount of gas released from the coolant is the cumulative amount of released gas within a preset time period, which can be obtained through step two.

[0120] Finally, calculate the amount of coolant to be added, combining the volume after expansion and the amount of gas precipitation to calculate the amount of coolant to be added , the formula is as follows: .

[0121] in: is the total volume of the system.

[0122] It is the expansion volume of the coolant at the actual temperature and pressure.

[0123] It is the amount of gas precipitation calculated based on real-time temperature and pressure conditions.

[0124] In the actual replenishment process, the pressure changes detected by the gas flow sensor and pressure monitoring component on the exhaust valve are also required to ensure sufficient exhaust. Based on the real-time monitoring of pressure and temperature data, the speed and pressure of coolant injection are dynamically adjusted to ensure stable operation of the system.

[0125] The above step ensures that the expansion and gas precipitation of the coolant under real-time temperature and pressure conditions are taken into account. The amount of coolant added must not only make up for the loss caused by gas precipitation, but also make up for the volume change of the coolant due to temperature changes. During the replenishment process, it is necessary to cooperate with real-time monitoring of temperature and pressure changes and adjust the injection rate to avoid too much gas remaining in the system. Through the complete process of this step, it can be ensured that the system is always maintained in an ideal cooling state, and the amount of coolant added can be dynamically adjusted according to the current environmental conditions.

[0126] The above steps involve the expansion coefficient of the coolant under different temperature and pressure conditions. The expansion coefficient of each type of cooling at a specific temperature and a specific pressure needs to be obtained through experimental measurement or using known data. The following are the general method steps for obtaining the expansion coefficient of the coolant: The expansion coefficient of the coolant usually refers to its volume expansion coefficient , which represents the rate at which the liquid volume changes with temperature. The specific calculation formula is as follows: .

[0127] in: : Volume expansion coefficient, unit: 1 / °C.

[0128] :Coolant at initial temperature The volume below.

[0129] : The rate at which the coolant volume changes with temperature.

[0130] The most direct way to obtain the expansion coefficient is to experimentally measure the volume change of the coolant at different temperatures and pressures. The following are the experimental steps: The experimental equipment includes: high-precision volume measuring devices (such as volume expansion meters, volumetric measuring devices); constant temperature devices (such as constant temperature boxes) for controlling the temperature of liquid samples; pressure regulating equipment for simulating different pressure conditions; temperature sensors for accurately measuring the state of liquids at different temperatures.

[0131] First, prepare the sample, select the coolant sample to be tested, and measure its initial temperature. The volume below .

[0132] Secondly, change the temperature, gradually adjust the temperature of the thermostat, and record each temperature. Coolant volume under , and record data at each temperature point , record the volume change of the coolant, and get .

[0133] Next, calculate the coefficient of expansion using the coefficient of expansion formula , calculate the expansion coefficient for each temperature interval.

[0134] Then, repeat the experiment, repeat the above process under different pressure conditions, and record the different situations in which the volume changes with temperature.

[0135] Finally, the experimentally measured data can be fitted into a coolant expansion coefficient curve, which represents the expansion coefficient under different temperature and pressure conditions.

[0136] Of course, if there is already mature data on the expansion coefficient of coolant, you can refer to relevant literature, standards and databases, such as the fluid physical property database, chemical handbook, "CRC Handbook of Chemistry and Physics" and engineering thermal property database, etc., to directly obtain the expansion coefficient of coolant under different conditions. In addition, coolant manufacturers usually provide the expansion coefficient of their products at various temperatures, and these data can be directly used in the database.

[0137] It should be noted that before adding coolant, you first need to control the exhaust valve to exhaust the gas, and judge whether the gas exhaust volume reaches the set threshold based on the real-time data of the sensor (the sensor here is a gas flow sensor, which is installed on the exhaust valve to monitor the gas flow). If it does not reach the threshold, you need to assist the exhaust by injecting coolant under pressure.

[0138] Step 4: Control the injection device to inject the coolant equal to the supplementary injection amount into the liquid replenisher 700.

[0139] To avoid bubble formation, the coolant should be injected at a slower rate, and the injection pressure should be greater than the exhaust pressure. Through the real-time data of each temperature sensor and pressure monitoring component, the controller 600 can dynamically adjust the injection speed and pressure during the coolant injection process. The system can set a slow injection strategy to gradually increase the injection pressure to prevent bubble formation, and, based on the feedback from the gas flow sensor in the exhaust valve, determine whether the gas has been exhausted to reach the set threshold.

[0140] Furthermore, if the pressure values ​​detected by some pressure sensors arranged at the corners of the pressure monitoring component still differ from the pressure values ​​of pressure sensors at other positions beyond the preset range, the power of the pressure generator 500 can be increased by the controller 600 to accelerate the flow rate of the coolant in the circulation channel to assist in the discharge of retained precipitated gas.

[0141] The above contents described in this specification are merely examples of the present invention. Those skilled in the art may make various modifications or additions to the specific embodiments described or replace them in similar ways, as long as they do not deviate from the contents of the present specification or exceed the scope defined by the claims, they shall all fall within the protection scope of the present invention.

Claims

1. A control method for a heat dissipation device of a drive system, characterized in that: The heat dissipation device comprises: The heat exchange component includes a first heat exchange space, so that when the coolant flows through the first heat exchange space, heat is exchanged with the heat exchange component to cool the coolant; A second heat exchanger is arranged on the drive system, and the second heat exchanger includes a second heat exchange space, so that when the coolant flows through the second heat exchange space, heat is exchanged with the drive system to increase the temperature of the coolant; a first pipe fitting, wherein both ends of the first pipe fitting are respectively connected to the first heat exchange space and the second heat exchange space, so that the first heat exchange space is connected to the second heat exchange space through the first pipe fitting; a second pipe fitting, wherein two ends of the second pipe fitting are respectively connected to the first heat exchange space and the second heat exchange space, so that the first heat exchange space is connected to the second heat exchange space through the second pipe fitting; a pressure generator connected to the first pipe member to allow the coolant in the first pipe member to flow; a controller connected to the pressure generator and the heat exchange component to control the operation of the pressure generator and the heat exchange component; The first heat exchange space in the heat exchange assembly, the second heat exchange space in the second heat exchanger, the inner space of the first pipe and the inner space of the second pipe form a circulation channel for the coolant to flow; A fluid infusion device, comprising a fluid infusion space, wherein the fluid infusion device is provided with a fluid infusion port connected to the fluid infusion space; An injection valve, arranged at the fluid infusion port of the fluid infusion device, to control the opening and closing of the fluid infusion port; a third pipe, one end of which is connected to the fluid replenisher so that the interior of the third pipe is in communication with the fluid replenishing space, and the other end of the third pipe is in communication with the circulation channel; a fourth pipe, one end of which is connected to the fluid replenisher so that the interior of the fourth pipe is in communication with the fluid replenishing space, and the other end of the fourth pipe is in communication with the circulation channel; Wherein, the liquid replenishing space of the liquid replenisher, the inner space of the third pipe and the inner space of the fourth pipe constitute a liquid replenishing channel; a second temperature sensor, disposed on the first pipe to detect the temperature of the coolant flowing through the first pipe, the second temperature sensor being connected to the controller; a third temperature sensor, disposed on the second pipe to detect the temperature of the coolant flowing through the second pipe, the third temperature sensor being connected to the controller; A pressure monitoring component is arranged on the heat dissipation device to detect the liquid pressure in the circulation channel, and the pressure monitoring component is connected to the controller; an exhaust valve, connected to the circulation flow channel; an injection device, the injection device being connected to the fluid replenisher through the injection valve to inject external coolant into the fluid replenisher; The control method comprises: Determining an initial injection amount of the coolant according to the total volume of the circulation channel and the liquid replenishment channel; Determining the cumulative amount of gas precipitation of the coolant according to the detection data of the second temperature sensor, the detection data of the third temperature sensor and the detection data of the pressure monitoring component; Determining the amount of coolant to be replenished based on the accumulated amount of gas released from the coolant, the detection data of the second temperature sensor, the detection data of the third temperature sensor, and the detection data of the pressure monitoring component; The injection device is controlled to inject cooling liquid equal to the supplementary injection amount into the liquid replenisher.

2. The control method according to claim 1, characterized in that: The heat exchange component comprises: a first heat exchanger, wherein the first heat exchange space is arranged inside the first heat exchanger; The radiator is arranged outside the first heat exchanger.

3. The control method according to claim 1, characterized in that: include: A first temperature sensor is disposed at the driving system to monitor the temperature of the driving system, and the first temperature sensor is connected to the controller.

4. The control method according to claim 1, characterized in that: The driving system is arranged in the second heat exchange space.

5. The control method according to claim 1, characterized in that: The fluid replenisher is provided with an observation port communicated with the fluid replenishing space, and a transparent sealing member is arranged at the observation port.

6. The control method according to claim 1, characterized in that: The cumulative amount of gas precipitation of the coolant is obtained according to the detection data of the second temperature sensor, the detection data of the third temperature sensor and the detection data of the pressure monitoring component, wherein the steps of obtaining the cumulative amount of gas precipitation are as follows: Recording the initial temperature and initial pressure of the coolant, and determining the initial gas solubility of the coolant at the initial temperature and the initial pressure; Obtaining the real-time temperature through the detection data of the second temperature sensor and the detection data of the third temperature sensor, and obtaining the real-time pressure through the pressure monitoring component; determining a real-time gas solubility of the coolant according to the real-time temperature and the real-time pressure; Obtaining the volume of the real-time coolant precipitated gas according to the real-time gas solubility, the initial gas solubility and the initial injection amount of the coolant; The accumulated amount of gas evolution is obtained according to the running time of the coolant.

7. The control method according to claim 6, characterized in that: The amount of coolant to be replenished is obtained based on the amount of gas precipitated from the coolant, the detection data of the second temperature sensor, the detection data of the third temperature sensor, and the detection data of the pressure monitoring component, wherein the steps of obtaining the amount of replenishment are as follows: Calculating the expansion volume of the coolant according to the real-time temperature, the initial temperature and the thermal expansion coefficient of the coolant; The replenishment injection amount of the coolant is obtained according to the accumulated amount of gas precipitation, the expansion volume of the coolant, and the total volume of the circulation channel and the liquid replenishment channel.

8. The control method according to claim 6, characterized in that: The real-time volume of the gas precipitated from the coolant is obtained according to the real-time gas solubility, the initial gas solubility and the initial injection amount of the coolant, and the cumulative amount of the gas precipitation is obtained according to the running time of the coolant, wherein the cumulative amount of the gas precipitation is obtained by the following steps: ； in: : Cumulative amount of gas precipitation in the coolant; : initial volume of coolant; : The gas solubility of the coolant under initial conditions, obtained from the coolant database; : Coolant temperature in real time and pressure The gas solubility under is obtained from the coolant solubility database; : The initial temperature value and the initial pressure value are obtained by the second temperature sensor, the third temperature sensor and the pressure monitoring component respectively; : The real-time temperature value and the real-time pressure value are obtained through the second temperature sensor, the third temperature sensor and the pressure monitoring component respectively; : Time interval, representing the time cumulative effect of gas evolution; in: ； ； Indicates the temperature of the coolant after passing through the heat exchange component; Indicates the temperature of the coolant after passing through the second heat exchanger.

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