A kind of active and passive automatic switching phase change liquid cooling device

Abstract

The present application relates to liquid cooling technical field, particularly to a kind of main passive automatic switching phase change liquid cooling device, comprising: case and main passive switcher, the case includes cooling cavity and drive cavity, cooling liquid is arranged in the cooling cavity, the main passive switcher includes working medium pump and temperature sensor, the working medium pump is arranged in drive cavity, and the working medium pump is communicated with the cooling cavity by pipeline by pipeline;Heating device is arranged in the cooling cavity, and the temperature sensor is arranged in the steam space above the heating device;The cooling liquid is used to absorb the heat generated by the heating device and generate steam;When the steam temperature value is less than or equal to the boiling point temperature of the cooling liquid, the phase change liquid cooling device works in passive phase change operating mode;When the steam temperature value is greater than the boiling point temperature of the cooling liquid, the phase change liquid cooling device works in active phase change operating mode.

Description

Technical Field

[0001] This invention relates to the field of liquid cooling technology, and in particular to a phase change liquid cooling device with automatic switching between active and passive operation. Background Technology

[0002] With the increasing integration of electronic equipment, the miniaturization of chips, and the localization of components, the thermal design power and heat flux density of chips are rapidly increasing. Conventional air cooling and non-contact liquid cooling technologies can no longer fully meet heat dissipation requirements. Immersion liquid cooling, a type of contact liquid cooling, has significant development potential due to its high heat transfer coefficient, low noise, low energy consumption, and small footprint. It has already been successfully applied in high-power, high-concentration electronic devices such as commercial data centers. Current immersion liquid cooling devices are designed based on the maximum thermal power consumption of the liquid cooling device, i.e., the liquid cooling device is in an active phase change operating mode. However, the liquid cooling device does not always operate at its maximum thermal power consumption state, and there is no effective monitoring and control mechanism for the liquid cooling device. Therefore, there is still room for further reduction in the energy consumption of liquid cooling devices.

[0003] Therefore, overcoming the shortcomings of the existing technology is an urgent problem to be solved in this technical field. Summary of the Invention

[0004] The technical problem to be solved by this invention is: how to switch between active phase change working mode and passive phase change working mode according to actual conditions in order to reduce the energy consumption of liquid cooling equipment.

[0005] The present invention adopts the following technical solution: In a first aspect, a phase change liquid cooling device with automatic switching between active and passive operation is provided, comprising: a chassis and an active / passive switcher, the chassis including a cooling chamber and a drive chamber, the cooling chamber containing coolant, the active / passive switcher including a working fluid pump and a temperature sensor, the working fluid pump being disposed in the drive chamber and connected to the cooling chamber via a pipe; a heating element being disposed in the cooling chamber, and the temperature sensor being disposed in the vapor space above the heating element; The coolant is used to absorb the heat generated by the heating device and produce steam; The temperature sensor is used to detect the steam temperature value in the steam space; The working fluid pump is used to drive the flow of the coolant; The phase change liquid cooling device has a passive phase change working mode and an active phase change working mode; When the steam temperature is less than or equal to the boiling point of the coolant, the working fluid pump is turned off, and the phase change liquid cooling device operates in passive phase change mode; when the steam temperature is greater than the boiling point of the coolant, the working fluid pump is turned on, and the phase change liquid cooling device operates in active phase change mode.

[0006] Preferably, the active-passive switch further includes a controller, the temperature sensor is connected to the controller, and the controller is connected to the working fluid pump; The temperature sensor is used to detect the steam temperature value in the steam space and transmit the steam temperature value to the controller; The controller is used to receive the steam temperature value and compare the steam temperature value with the boiling point temperature of the coolant. Based on different comparison results, it controls the opening and closing of the working fluid pump.

[0007] Preferably, the passive phase transition operating mode is as follows: When the steam temperature detected by the temperature sensor is less than or equal to the boiling point temperature of the coolant, the controller controls the working fluid pump to shut down, the coolant stops flowing, and the heating element and the coolant exchange heat to achieve heat transfer.

[0008] Preferably, the active phase transition operating mode is as follows: When the steam temperature detected by the temperature sensor is greater than the boiling point of the coolant, the controller controls the working fluid pump to start, and the working fluid pump drives the coolant to flow to achieve convective heat dissipation. The heating device and the coolant exchange heat to achieve heat transfer.

[0009] Preferably, the chassis further includes an interface cavity, the drive cavity is disposed on one side of the cooling cavity, and the interface cavity is disposed on the other side of the cooling cavity; The interface cavity is equipped with a connector, and external devices are connected to the connector. The heating element is connected to the connector for communication between the heating element and the external device.

[0010] Preferably, the cooling chamber is provided with at least one inlet end and at least one outlet end, the at least one outlet end being higher than the at least one inlet end; the at least one outlet end being disposed close to the liquid surface of the coolant; the at least one inlet end and the at least one outlet end being distributed on both sides of the cooling chamber; The working fluid pump is connected to at least one inflow end and at least one outflow end via pipelines.

[0011] Preferably, the active-passive automatic switching phase change liquid cooling device includes a condensation reflux module, which is disposed in the upper part of the cooling chamber; The condensation reflux module includes an annular heat pipe and an air-to-air heat exchanger. The air-to-air heat exchanger is disposed above the cooling chamber, and the vapor space is formed between the air-to-air heat exchanger and the liquid surface of the coolant. The annular heat pipe is located at the bottom of the air-to-air heat exchanger to absorb the heat of the steam in the steam space and transfer the heat to the air-to-air heat exchanger.

[0012] Preferably, the active-passive automatic switching phase change liquid cooling device further includes a forced air cooling module, which is disposed on the condensation reflux module; The forced air cooling module includes a fan and heat dissipation fins. The heat dissipation fins are fixed on the air-to-air heat exchanger and are used to receive heat from the air-to-air heat exchanger. The fan is located on top of the heat dissipation fins and is used to blow external cold air into the cooling chamber to remove the heat from the heat dissipation fins.

[0013] Preferably, the phase change liquid cooling device further includes a pressure detection module, which includes a pressure sensor and a pressure gauge, and the pressure sensor and the pressure gauge are connected. The pressure sensor is installed in the steam space and is used to detect the pressure in the steam space; The pressure gauge is mounted on the forced air cooling module to facilitate observation of the pressure in the steam space.

[0014] Secondly, a method for automatic switching between active and passive modes is provided, including: When the steam temperature is less than or equal to the boiling point of the coolant, the working fluid pump is turned off, and the phase change liquid cooling device operates in passive phase change mode. When the steam temperature is greater than the boiling point of the coolant, the working fluid pump is turned on, and the phase change liquid cooling device operates in active phase change mode.

[0015] Compared with the prior art, the beneficial effects of the present invention are as follows: This invention detects the steam temperature in the steam space using a temperature sensor and compares it with the boiling point of the coolant. When the steam temperature is less than or equal to the boiling point of the coolant, the working fluid pump is shut off, causing the phase change liquid cooling device to operate in passive phase change mode. When the steam temperature is greater than the boiling point of the coolant, the working fluid pump is turned on, causing the phase change liquid cooling device to operate in active phase change mode. This achieves the switching of the phase change liquid cooling device's operating mode based on the steam temperature and the coolant's boiling point, thereby reducing the energy consumption of the liquid cooling device. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of the structure of a phase change liquid cooling device with active-passive automatic switching provided in an embodiment of the present invention; Figure 2 This is a schematic diagram of the cooling chamber structure of a phase change liquid cooling device with active-passive automatic switching provided in an embodiment of the present invention; Figure 3 This is a schematic diagram of the chassis structure of a phase change liquid cooling device with active-passive automatic switching provided in an embodiment of the present invention; Figure 4 This is a schematic diagram of the active / passive switch of a phase change liquid cooling device with automatic active / passive switching provided in an embodiment of the present invention; Figure 5 This is a schematic diagram of the chassis of a phase change liquid cooling device with active-passive automatic switching provided in an embodiment of the present invention; Figure 6 This is a schematic diagram of the external structure of the cooling chamber of a phase change liquid cooling device with active-passive automatic switching provided in an embodiment of the present invention; Figure 7 This is a schematic diagram of the condensation reflux module and forced air cooling module of a phase change liquid cooling device with active-passive automatic switching provided in an embodiment of the present invention; Figure 8 This is a schematic diagram of the pressure detection module of a phase change liquid cooling device with active-passive automatic switching provided in an embodiment of the present invention; Figure 9 This is a flowchart illustrating a method for automatic switching between active and passive modes provided in an embodiment of the present invention. Figure 10 This is a schematic diagram of a multi-layer hole wave suppression device based on a piezoelectric beam structure provided in an embodiment of the present invention; Figure 11 This is a schematic diagram of the structure of the second wave-damping plate of a multi-layer perforated wave suppression device based on a piezoelectric beam structure provided in an embodiment of the present invention; Figure 12 This is a schematic diagram of the control principle of the second wave-damping plate of a multi-layer perforated wave suppression device based on a piezoelectric beam structure provided in an embodiment of the present invention; Figure 13 This is a schematic diagram of the first structure of a multi-layer hole wave suppression device based on a piezoelectric beam structure provided in an embodiment of the present invention; Figure 14This is a schematic diagram of the actual application of a multi-layer hole wave suppression device based on a piezoelectric beam structure provided in an embodiment of the present invention; Figure 15 This is a schematic diagram of the second structure of a multi-layer hole wave suppression device based on a piezoelectric beam structure provided in an embodiment of the present invention; Figure 16 This is a schematic diagram of the third structure of a multi-layer hole wave suppression device based on a piezoelectric beam structure provided in an embodiment of the present invention; Figure 17 This is a schematic diagram of the wave-damping plate of a multi-layer perforated wave suppression device based on a piezoelectric beam structure provided in an embodiment of the present invention. Detailed Implementation

[0018] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0019] In the description of this invention, the terms "inner", "outer", "upper", "lower", "bottom", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and do not require that this invention must be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting this invention.

[0020] In this invention, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0021] In this application, unless otherwise expressly specified and limited, the term "connection" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral part; it can be a direct connection or an indirect connection through an intermediate medium. Furthermore, the term "coupled" can refer to an electrical connection that enables signal transmission. Moreover, the technical features involved in the various embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other.

[0022] Example 1: Contact immersion liquid cooling offers advantages in heat dissipation efficiency and power consumption, but there is still room for optimization in current technology. Existing designs reference maximum heat dissipation, but actual operation may not always be at maximum power consumption. It is advisable to consider dynamically adjusting the liquid cooling system's operating mode based on real-time heat dissipation to avoid over-design. Current designs lack effective monitoring and control mechanisms, making it impossible to track and optimize the liquid cooling system's operating status in real time.

[0023] Based on existing technologies, sensors can be added to monitor real-time thermal power consumption and temperature, and integrated with the control system in a closed loop to achieve intelligent switching of operating modes.

[0024] To address the aforementioned problems, embodiments of the present invention provide a phase change liquid cooling device with automatic switching between active and passive operation, such as... Figure 1 , Figure 2 and Figure 3 As shown, the device includes: a chassis and an active / passive switch. The chassis includes a cooling chamber and a drive chamber. The cooling chamber contains coolant. The active / passive switch includes a working fluid pump and a temperature sensor. The working fluid pump is located in the drive chamber and is connected to the cooling chamber via a pipe. A heating element is located in the cooling chamber, and the temperature sensor is located in a steam space above the heating element. The coolant absorbs the heat generated by the heating element and produces steam. The temperature sensor detects the steam temperature in the steam space. The working fluid pump drives the flow of the coolant. The phase change liquid cooling device has a passive phase change operating mode and an active phase change operating mode. When the steam temperature is less than or equal to the boiling point of the coolant, the working fluid pump is turned off, and the phase change liquid cooling device operates in passive phase change mode. When the steam temperature is greater than the boiling point of the coolant, the working fluid pump is turned on, and the phase change liquid cooling device operates in active phase change mode.

[0025] The key functions of the working fluid pump include: driving the flow of coolant and achieving coolant circulation within the cooling chamber, which is more conducive to the removal of heat from the heat-generating components. In active phase change mode, activating the working fluid pump enhances the coolant's heat conduction and absorption capabilities, thereby removing heat generated by the heat-generating components more quickly. The on / off state of the working fluid pump directly determines whether the phase change liquid cooling device enters active or passive mode, and the working fluid pump is a crucial actuator for achieving automatic switching between active and passive modes. The performance of the working fluid pump directly affects the heat dissipation efficiency of the phase change liquid cooling device. Optimization of parameters such as pump flow rate and operating frequency will affect the overall performance of the phase change liquid cooling device. As an electromechanical component, the reliability and service life of the working fluid pump also affect the long-term operational reliability of the phase change liquid cooling device.

[0026] In addition, the temperature sensor is used to detect the steam temperature in the steam space in real time. The steam temperature is a key reference indicator for determining whether the phase change liquid cooling device needs to enter active mode. In a preferred embodiment, the real-time temperature data collected by the temperature sensor can also be fed back to its corresponding controller, enabling real-time monitoring and optimization of the phase change liquid cooling device's operating status. How the controller controls the working fluid pump based on the temperature sensor will be explained below. It is worth noting that, since it is located in a high-temperature area, the temperature sensor itself needs to have a certain high-temperature operating capability and service life, or multiple temperature sensors can be deployed in a cluster. This can also improve the detection accuracy and the reliability of the phase change liquid cooling device. In this embodiment, the specific model of the working fluid pump and the specific model of the temperature sensor are not specifically required.

[0027] This invention uses a temperature sensor to detect the steam temperature in the steam space and compares it with the boiling point of the coolant. When the steam temperature is less than or equal to the boiling point of the coolant, the working fluid pump is shut off, causing the phase change liquid cooling device to operate in passive phase change mode. When the steam temperature is greater than the boiling point of the coolant, the working fluid pump is turned on, causing the phase change liquid cooling device to operate in active phase change mode. This achieves switching of the operating mode of the phase change liquid cooling device based on the steam temperature and the boiling point of the coolant, thereby reducing the energy consumption of the liquid cooling device.

[0028] In a preferred embodiment, in order to control the opening and closing of the working fluid pump based on the steam temperature value fed back by the temperature sensor, such as... Figure 4 As shown, the active-passive switch also includes a controller, the temperature sensor is connected to the controller, and the controller is connected to the working fluid pump; the temperature sensor is used to detect the steam temperature value in the steam space and transmit the steam temperature value to the controller; the controller is used to receive the steam temperature value and compare the steam temperature value with the boiling point temperature of the coolant, and control the opening and closing of the working fluid pump according to different comparison results.

[0029] The controller is connected to the temperature sensor and can receive the steam temperature value collected by the sensor in real time. The controller is also connected to the working fluid pump and can control the on / off state of the working fluid pump, thereby controlling the phase change liquid cooling device to enter active or passive mode.

[0030] The controller is used to compare the received steam temperature value with the boiling point temperature of the coolant and make a judgment. The controller can compare the received steam temperature value with the boiling point temperature of the coolant by the following methods: (1) Digital comparison method: The boiling point temperature value of the coolant stored in the controller is used as the digital reference value Tref, and the received steam temperature value is used as the digital input value Tin. The digital comparator compares Tin with Tref to obtain the comparison result.

[0031] (2) Analog comparison method: Tref is preset in the reference circuit inside the controller in the form of voltage or current, and Tin is input to the controller in the same form of voltage or current. The two analog quantities are compared by an operational amplifier or comparator to obtain the comparison result.

[0032] (3) Microprocessor comparison method: Tref and Tin are stored in the microprocessor memory in the form of digital values. The microprocessor performs numerical comparison operation between Tin and Tref to obtain the comparison result.

[0033] In the above methods, the hardware implementation of the digital comparison method and the analog comparison method is simple; the program of the microprocessor comparison method is more flexible. In a preferred embodiment, the controller can be a microcontroller or a control chip. The overall selection should be determined according to the working mechanism and function of the controller, and no specific limitation is made in this embodiment.

[0034] The controller implements three key stages: temperature comparison, judgment, and control execution, giving the entire phase change liquid cooling device complete automatic control capabilities. In a preferred embodiment, learning capabilities can also be added to the controller to further optimize the active / passive switching strategy.

[0035] In a preferred embodiment, the passive phase change operating mode and the active phase change operating mode will be described in detail below.

[0036] The passive phase change working mode is as follows: when the steam temperature detected by the temperature sensor is less than or equal to the boiling point temperature of the coolant, the controller controls the working fluid pump to shut down, the coolant stops flowing, and the heating element and the coolant exchange heat to achieve heat transfer. The active phase change working mode is as follows: when the steam temperature detected by the temperature sensor is greater than the boiling point temperature of the coolant, the controller controls the working fluid pump to turn on, the working fluid pump drives the coolant to flow to achieve convective heat dissipation, and the heating element and the coolant exchange heat to achieve heat transfer.

[0037] In short, the passive phase change operating mode uses only natural convection for heat transfer. The heating element exchanges heat with the coolant through natural convection driven by the temperature difference. At this time, the coolant is basically still with very little fluidity. The heat dissipated by the heating element is conducted through the contact between the coolant molecules and the surface of the heating element. The heat transfer efficiency depends on the temperature difference and the physical properties of the coolant, and its heat dissipation capacity is limited.

[0038] The active phase change operating mode employs forced convection for heat transfer, with the working fluid pump circulating the coolant. The flowing coolant brings new coolant molecules into continuous contact with the surface of the heat-generating components, enhancing convective heat transfer. The convection generated by the working fluid pump also induces convection within the coolant, improving heat absorption and transfer efficiency. Heat is conducted from the heat-generating components to the coolant through both conduction at the contact interface and convection within the coolant fluid. Compared to the passive phase change operating mode, the active phase change operating mode offers significantly higher heat dissipation capabilities.

[0039] The difference between the two lies in the flow state of the coolant, the heat transfer mechanism, and the relative heat transfer efficiency. By automatically switching between the two modes based on the steam temperature, the controller ensures optimal heat dissipation for the heating components under different loads, thus preventing redundant energy consumption.

[0040] To facilitate communication between the heating device and external devices, in a preferred embodiment, such as... Figure 5 As shown, the chassis also includes an interface cavity, the drive cavity is located on one side of the cooling cavity, and the interface cavity is located on the other side of the cooling cavity; a connector is provided on the interface cavity, and an external device is connected to the connector; the heating element is connected to the connector for communication between the heating element and the external device.

[0041] When the external device communicates with the heating device, the external device can be located in the interface cavity and / or outside the chassis. When connecting the heating device to the external device, the connecting cable should have communication, waterproof, and data transmission functions, which will not be elaborated on in this embodiment. Secondly, the interface cavity can be arranged opposite to the driving cavity on both sides of the cooling cavity. At the same time, the interface cavity can also be arranged adjacent to the driving cavity on both sides of the cooling cavity, which will not be specifically limited in this embodiment.

[0042] The above design effectively isolates and integrates various functional modules of the system through the chassis, which facilitates assembly and maintenance, while ensuring efficient connection between heat-generating components and external devices, and better realizing automatic heat dissipation control.

[0043] In a preferred embodiment, under the active phase change operating mode, in order to improve the flow of the coolant, such as... Figure 6 As shown, the cooling chamber is provided with at least one inlet end and at least one outlet end, the at least one outlet end being higher than the at least one inlet end; the at least one outlet end being positioned close to the surface of the coolant; the at least one inlet end and the at least one outlet end being distributed on both sides of the cooling chamber; the working fluid pump being connected to the at least one inlet end and the at least one outlet end respectively via pipes.

[0044] The at least one inflow end and at least one outflow end are determined based on the actual size of the cooling cavity. In this embodiment, two inflow ends and two outflow ends are used as an example.

[0045] Because the heating element generates more heat at its upper part, the temperature of the upper part of the coolant may be higher than that of the lower part. Therefore, the outlet is positioned closer to the coolant surface to facilitate the pump drawing out the hotter coolant, while the inlet is positioned closer to the bottom to facilitate pumping the hotter coolant back to the cooler area near the bottom, thus achieving better heat exchange. Conversely, when the lower part of the heating element generates more heat... The positions of the inflow and outflow ends can be interchanged, depending on the actual situation. In this embodiment, two inflow ends and two outflow ends are selected to form a return pipe. This can ensure that the flow rate of coolant in the entire cooling chamber of the equipment is uniform and the cooling effect is better. No further explanation is given in this embodiment.

[0046] In a preferred embodiment, such as Figure 7 As shown, the active / passive automatic switching phase change liquid cooling device includes a condensation reflux module, which is located at the upper part of the cooling chamber. The condensation reflux module includes an annular heat pipe and an air-to-air heat exchanger. The air-to-air heat exchanger is located above the cooling chamber, and a vapor space is formed between the air-to-air heat exchanger and the liquid surface of the coolant. The annular heat pipe is located at the bottom of the air-to-air heat exchanger and is used to absorb the heat of the vapor in the vapor space and transfer the heat to the air-to-air heat exchanger.

[0047] The condensation reflux module recovers steam from the steam space, preventing it from dissipating along with heat and improving the device's heat dissipation efficiency. It also acts as a condenser, ensuring continuous and stable operation. The number of annular heat pipes is determined by actual heat dissipation requirements. These annular heat pipes, with their large surface area, exchange heat with the steam, condensing it into liquid and dripping it back into the cooling chamber for recovery. The annular heat pipes, using pipes or plates, are annular structures located at the bottom of the air-to-air heat exchanger, within the steam space. Their large surface area effectively absorbs and conducts heat from the steam. The air-to-air heat exchanger, with its large surface area, uses fins or cores and is positioned above the cooling chamber, forming a sealed steam space between itself and the coolant surface.

[0048] The working principle of the condensation reflux module is as follows: After the annular heat pipe absorbs heat from the steam, it conducts the heat to the air-to-air heat exchanger. The air-to-air heat exchanger transfers the heat from the annular heat pipe to the outside. The annular heat pipe, utilizing its large surface area, condenses the steam into a liquid state. The liquid coolant flows back to the cooling chamber, where the heat pipe absorbs a new round of steam heat. This cycle repeats, achieving effective steam recovery and condensation. The two work together to efficiently realize the functions of steam recovery and condensation.

[0049] In a preferred embodiment, the air-to-air heat exchanger transfers the heat from the annular heat pipe to the outside, such as... Figure 7 As shown, the "external" here refers to the active-passive automatic switching phase change liquid cooling device, which also includes a forced air cooling module. The forced air cooling module is disposed on the condensation reflux module. The forced air cooling module includes a fan and heat dissipation fins. The heat dissipation fins are fixed on the air-to-air heat exchanger and are used to receive heat from the air-to-air heat exchanger. The fan is disposed on the top of the heat dissipation fins and is used to blow external cold air into the cooling chamber to remove the heat from the heat dissipation fins.

[0050] The heat dissipation fins are fixed to the air-to-air heat exchanger. Therefore, based on the structure of the air-to-air heat exchanger, the air-to-air heat exchanger will transfer the heat from the annular heat pipe to the heat dissipation fins. A fan is provided above the heat dissipation fins to dissipate heat. Thus, the temperature of the steam is absorbed, and at the same time, it will not cause excessive loss of coolant.

[0051] In a preferred embodiment, to prevent excessively high steam pressure within the steam space, such as... Figure 8 As shown, the phase change liquid cooling device further includes a pressure detection module, which includes a pressure sensor and a pressure gauge. The pressure sensor and the pressure gauge are connected. The pressure sensor is installed in the steam space to detect the pressure in the steam space. The pressure gauge is installed on the forced air cooling module to facilitate observation of the pressure in the steam space.

[0052] In one embodiment, a pressure relief valve is installed on the wall above the coolant level in the cooling chamber within the steam space. The pressure relief valve is connected to a control module, and a pressure sensor is also connected to the control module. The pressure sensor transmits the pressure value of the steam space to the control module in real time. The control module has a preset safety pressure value. The control module receives the pressure value transmitted by the pressure sensor in real time and compares the pressure value with the preset safety pressure value. When the pressure value is greater than the preset safety pressure value, the control module promptly controls the pressure relief valve to open, thereby relieving pressure in the steam space to ensure safety.

[0053] Example 2 Example 1 presented a phase change liquid cooling device with automatic switching between active and passive modes. This example presents a method for automatic switching between active and passive modes, applicable to the phase change liquid cooling device with automatic switching between active and passive modes as described in Example 1. Figure 9 As shown, the method includes: Step 101: When the steam temperature is less than or equal to the boiling point of the coolant, the working fluid pump is turned off, and the phase change liquid cooling device operates in passive phase change mode.

[0054] The passive phase change operating mode utilizes only natural convection for heat transfer. The heating element exchanges heat with the coolant through natural convection driven by temperature difference. In this mode, the coolant is essentially still with very low fluidity. The heat dissipated by the heating element is conducted through contact between coolant molecules and the surface of the heating element. The heat transfer efficiency depends on the temperature difference and the physical properties of the coolant, and its heat dissipation capacity is limited.

[0055] Step 102: When the steam temperature is greater than the boiling point of the coolant, the working fluid pump is turned on, and the phase change liquid cooling device operates in active phase change mode.

[0056] The active phase change operating mode employs forced convection for heat transfer, with the working fluid pump circulating the coolant. The flowing coolant brings new coolant molecules into continuous contact with the surface of the heat-generating components, enhancing convective heat transfer. The convection generated by the working fluid pump also induces convection within the coolant, improving heat absorption and transfer efficiency. Heat is conducted from the heat-generating components to the coolant through both conduction at the contact interface and convection within the coolant fluid. Compared to the passive phase change operating mode, the active phase change operating mode offers significantly higher heat dissipation capabilities.

[0057] The difference between the two lies in the flow state of the coolant, the heat transfer mechanism, and the relative heat transfer efficiency.

[0058] By automatically switching between the two modes based on the steam temperature, the controller ensures optimal heat dissipation for the heating element under different loads, thus preventing redundant energy consumption. The specific structure of the active / passive automatic switching phase change liquid cooling device is described in Example 1, and will not be elaborated further in this embodiment.

[0059] Example 3 To further illustrate the active-passive automatic switching phase change liquid cooling device in Example 1, this example proposes a multi-layer hole wave suppression device based on a piezoelectric beam structure, wherein the multi-layer hole wave suppression device of the piezoelectric beam structure is disposed on the cooling liquid surface in the cooling chamber of the active-passive automatic switching phase change liquid cooling device.

[0060] The multi-layer perforated wave suppression device is used to suppress coolant fluctuations in the cooling chamber. Coolant fluctuations refer to the up-and-down movement of the coolant surface in the cooling chamber. Fluid fluctuations can be caused by various factors, including pipe layout, pressure fluctuations, and vibration tests on the equipment. Fluid surface fluctuations may lead to unstable cooling effects and damage to internal electronic components. Internal surging refers to the surging of the coolant surface in the cooling system. Internal surging may lead to uneven coolant mixing, unstable pressure, and increased fluid resistance.

[0061] like Figure 10 As shown, it includes: a first baffle plate and at least one second baffle plate, the second baffle plate being disposed below the first baffle plate, the first baffle plate being disposed on the surface of the coolant, and the second baffle plate being disposed below the surface of the coolant; both the first baffle plate and the second baffle plate are provided with baffle holes (e.g., Figure 13 As shown), the second anti-surge plate is provided with a piezoelectric sheet; the anti-surge holes on the first anti-surge plate are used to suppress fluctuations on the surface of the coolant; the anti-surge holes on the second anti-surge plate are used to suppress internal surges below the surface of the coolant; Among them, reference Figure 10 The first baffle plate is positioned on the coolant surface to suppress fluctuations. It has anti-surge holes to buffer these fluctuations. The second baffle plate is positioned below the first baffle plate and below the coolant surface. It also has anti-surge holes to suppress internal surging below the coolant surface. The specific method for setting the anti-surge holes will be described below.

[0062] The piezoelectric element is mounted on the second wave shield, such as... Figure 11 As shown, the piezoelectric sheet is disposed at the movable end of the second wave-damping plate. The piezoelectric sheet and the second wave-damping plate form a piezoelectric beam, which is a slender beam-like structure made of piezoelectric sheets, possessing both piezoelectric effect and mechanical properties of a beam. A piezoelectric beam deforms under stress and generates a potential difference when an electric field is applied. It is typically made of piezoelectric materials and possesses excellent piezoelectric properties and mechanical characteristics. It can convert an applied electric field into mechanical strain or deflection, or convert applied external force or strain into a potential difference, through the piezoelectric effect. The design and performance of the piezoelectric beam are affected by factors such as the selection of piezoelectric materials, beam geometry, and the application of electric field and mechanical loads. Therefore, in specific applications, these factors need to be considered, and appropriate piezoelectric sheet materials and the dimensional parameters of the second wave-damping plate need to be selected to meet practical application requirements.

[0063] The movable end of the second baffle plate allows the piezoelectric element to sense internal surging beneath the coolant surface via the piezoelectric effect and apply a corresponding force to mitigate this surging. In a preferred embodiment, the installation position of the piezoelectric element can vary depending on the specific design and application scenario. When the internal surging beneath the coolant surface is generally small, the piezoelectric element can also be fixed near the center of the second baffle plate. Simply ensure the piezoelectric element is positioned on the second baffle plate so that its vibration drives the vibration of the second baffle plate, generating a feedback force on the liquid surface under the influence of internal surging, thereby altering the movement state of the internal surging beneath the liquid surface. This helps increase the stability of the coolant and reduce the impact of internal surging.

[0064] The piezoelectric element operates as follows: it receives internal surging beneath the coolant surface to generate an electrical signal; it vibrates according to the vibration signal generated by the electrical signal; and it also drives the second anti-surge plate to vibrate to counteract the internal surging beneath the coolant surface.

[0065] Specifically: such as Figure 11 and Figure 12 As shown, a control module is provided on the second wave deflector, and the piezoelectric sheet is connected to the control module. The control module is used to receive the electrical signal transmitted by the piezoelectric sheet, thereby generating a vibration signal based on the electrical signal, and transmitting the vibration signal to the piezoelectric sheet to cause the piezoelectric sheet to vibrate accordingly. The piezoelectric sheet is used to generate a deformation with the same frequency but opposite phase as the internal surge based on the vibration signal, thereby driving the second wave deflector to vibrate to counteract the internal surge.

[0066] The control module may not be located on the second wave deflector; it can be located on the side wall of the cooling chamber or outside the cooling chamber to prevent interference with the placement of other modules within the cooling chamber. The control module is connected to the piezoelectric sheet. Since the entire piezoelectric beam structure is immersed in the coolant, there are certain requirements for the waterproof performance of the connecting wire and the control module. The specific types of the connecting wire and the control module are not specifically limited in this embodiment, as long as they have waterproof capabilities, signal transmission capabilities, and analysis and processing capabilities.

[0067] The control module receives electrical signals transmitted by the piezoelectric element and generates vibration signals based on these signals, then transmits the vibration signals back to the piezoelectric element. The piezoelectric element vibrates accordingly based on the received vibration signals, deforming with the same frequency but opposite phase to the internal surge. This vibration drives the second baffle plate to vibrate accordingly, counteracting the effect of the internal surge. In a preferred embodiment, the piezoelectric effect and feedback control system are utilized to counteract the internal surge through the cooperative vibration of the piezoelectric element and the second baffle plate. The electrical signals received by the piezoelectric element are processed by the control module to generate appropriate vibration signals, enabling the piezoelectric element to produce vibrations opposite to the internal surge. This vibration is transmitted to the second baffle plate, causing it to vibrate in the opposite manner. Through this coordinated vibration, the effects of the internal surge can be effectively counteracted, thereby maintaining the stability of the coolant surface.

[0068] It should be noted that the specific control module design, signal processing algorithm, and connection method between the piezoelectric element and the wave deflector will vary depending on the actual application. In practical scheme design, the impact of actual factors should be considered, and will not be elaborated upon in this embodiment.

[0069] A piezoelectric sheet is a thin sheet or plate-like component made of a piezoelectric material capable of producing the piezoelectric effect. It is typically made of piezoelectric crystal materials (such as quartz, lead zirconium titanate, etc.) and possesses excellent piezoelectric properties and mechanical characteristics. Piezoelectric sheets convert mechanical strain or vibration into electrical signals, or conversely, convert electrical signals into mechanical motion, through the piezoelectric effect.

[0070] The piezoelectric element functions to receive the mechanical vibrations generated by the internal surging beneath the coolant surface and convert these vibrations into electrical signals via the piezoelectric effect. The piezoelectric effect is a specific physical effect that refers to the mechanical deformation or strain that occurs when certain materials are excited by an external electric field or mechanical force. Specifically, when the piezoelectric element is subjected to external force or strain, a change in charge or potential is generated. This change in charge or potential is communicated to the control module, which then sends a vibration signal to the piezoelectric element to cause it to vibrate. This design utilizes the characteristics of the piezoelectric effect to convert the internal surging beneath the coolant surface into controllable mechanical vibrations, which are then counteracted by the vibration of the second anti-surge plate.

[0071] In a preferred embodiment, in order to combine the first wave-damping plate and the second wave-damping plate into a single unit, such as... Figure 13 As shown, the device further includes a first abutment plate and a second abutment plate, the first abutment plate and the second abutment plate being symmetrically arranged at both ends of the first wave-breaking plate; the fixed end of the second wave-breaking plate is connected to the first abutment plate, and / or the fixed end of the second wave-breaking plate is connected to the second abutment plate.

[0072] Among them, reference Figure 10 and Figure 14 Because the fluctuations on the coolant surface are greater than the internal surging below the coolant surface, the area of ​​the first baffle plate is larger than that of the second baffle plate. The internal surging below the coolant surface has a smaller amplitude than the fluctuations on the coolant surface and is mainly close to the equipment wall; therefore, the second baffle plate needs to be close to the wall. The number of second baffle plates is one or more, determined by the area of ​​the coolant surface. The second baffle plates are arranged as follows: the fixed end of the second baffle plate is fixed to the middle portion of the first abutment plate; and / or, the fixed end of the second baffle plate is fixed to the middle portion of the second abutment plate; and / or, the fixed ends of the second baffle plates are symmetrically fixed to the middle portions of the first and second abutment plates, respectively.

[0073] It is worth noting that, such as Figure 15 As shown, after the first and second anti-surge plates are installed, they will form a trapezoidal space below the coolant surface. This trapezoidal space is used to place other modules inside the liquid cooling chassis.

[0074] In a preferred embodiment, such as Figure 16 As shown, the first wave-breaking plate includes multiple wave-breaking strips, and slots are provided between adjacent wave-breaking strips. There are also multiple second wave-breaking plates, with a preset distance between adjacent second wave-breaking plates located on the same abutment plate; the slots are positioned directly opposite the openings corresponding to the preset distance.

[0075] The first wave deflector has slots that divide it into multiple wave-damping strips. This is to reduce the weight of the device without compromising its wave suppression effect. The number of wave-damping strips is determined by the area of ​​the coolant surface. To save materials and enhance the suppression effect, multiple second wave deflectors are used, with a predetermined spacing between adjacent second wave deflectors. This predetermined spacing is determined by the magnitude of internal surging below the actual coolant surface and the physical properties of the coolant; it is not specifically limited in this embodiment. On the device, the slots on the first wave deflector are positioned directly opposite the predetermined spacing to facilitate the vertical flow of coolant and enhance the suppression effect. For example, the predetermined spacing may be 10 cm or other values, depending on the actual situation, and is not specifically limited here.

[0076] Both the first and second wave-damping plates are provided with wave-damping holes. In a preferred embodiment, one design scheme for the wave-damping holes is as follows: A vibration test is conducted on the cooling chamber to obtain the test waveform of the test wave generated by the vibration. The actual waveforms generated by the fluctuations on the coolant surface and the internal surging below the coolant surface are compared with the test waveforms obtained from the vibration test. The frequency of the test waveforms is analyzed to obtain the wavelength and wave height of the test waves. Based on the physical parameters of the coolant itself, the aperture of the anti-surge holes is determined according to the wavelength, and the spacing between the anti-surge holes is determined according to the wave height. By adjusting the aperture and spacing, the anti-surge holes can absorb the fluctuations on the coolant surface and the internal surging below the coolant surface to the maximum extent.

[0077] Specifically, a vibration test is conducted on the cooling chamber, and the waveforms of the test waves generated by the vibration test are recorded. The waveforms generated by the fluctuations on the coolant surface and the internal surging below the coolant surface are compared with the waveforms obtained from the vibration test. The frequency of the test waveforms is analyzed to determine the wavelength and wave height of the test waves. Based on the physical parameters of the coolant, the aperture of the anti-surge holes is determined according to the wavelength, with a longer wavelength corresponding to a larger aperture. The spacing between the anti-surge holes is determined according to the wave height, with a larger wave height corresponding to a larger spacing. Finally, by adjusting the aperture and spacing of the anti-surge holes, they can effectively absorb the fluctuations on the coolant surface and the internal surging below the coolant surface.

[0078] The choice of orifice diameter is mainly related to the wavelength of the test waveform; a longer wavelength corresponds to a larger orifice diameter, allowing larger fluctuations to pass through the anti-wave orifice. The choice of spacing is mainly related to the wave height of the test waveform; a larger wave height requires a larger spacing to ensure sufficient distance between the anti-wave orifices to absorb and dissipate wave energy. Through reasonable orifice diameter and spacing design, the anti-wave orifices can absorb and dissipate fluctuations and internal surging on the coolant surface to the maximum extent, thereby maintaining the stability of the coolant surface.

[0079] The aperture setting based on wavelength and the spacing setting based on wave height can be estimated and optimized using the following methods: 1. Setting the aperture based on wavelength: Wavelength is the length of a wave and can be used to estimate the aperture of a wave-damping orifice. Longer wavelengths require larger apertures to accommodate the transmission of wave energy. The precise relationship depends on factors such as the properties of the liquid and the layout of the wave-damping orifice. A common method is to determine the relationship between aperture and wavelength based on empirical formulas or experimental results.

[0080] 2. Setting Spacing Based on Wave Height: Wave height refers to the amplitude or height of waves and can be used to estimate the spacing between breakwaters. Larger wave heights require larger spacing to ensure sufficient volume between the breakwaters to absorb and dissipate wave energy. Similar to orifice diameter settings, the specific relationship can be determined through empirical formulas or experimental data.

[0081] In practical applications, optimization is typically achieved by combining numerical simulation, experimental testing, and empirical design. By comparing and evaluating different combinations of aperture and spacing, the optimal design can be found to meet specific needs and conditions. It's important to note that the design of aperture and spacing is also constrained by other factors, such as the strength and stability of the material, and the overall structural layout. Therefore, specific settings must be made according to the actual situation to ensure the accuracy and effectiveness of the wave-damping hole design. The more detailed implementation process will not be elaborated upon in this embodiment.

[0082] After setting the aperture and spacing of the anti-surge holes according to the actual situation, in a preferred embodiment, the anti-surge holes on the first anti-surge plate and the second anti-surge plate are arranged alternately according to the interval between the anti-surge holes, so as to suppress the waves generated by the fluctuations on the surface of the coolant and the internal surges below the surface of the coolant, respectively.

[0083] The specific arrangement method of the staggered arrangement of the wave-damping holes will be described next. In one embodiment, such as... Figure 17 As shown, the wave-breaking holes on the first and second wave-breaking plates are configured as a first column of wave-breaking holes and a second column of wave-breaking holes. The first column of wave-breaking holes has mating holes A, and the second column of wave-breaking holes has mating holes B. Except for the mating holes A and / or mating holes B on the outermost sides, according to the arrangement order of mating holes A and mating holes B on the first and second wave-breaking plates, the Nth mating hole A is located at the middle position of the horizontal projection of the Nth mating hole B and the (N+1)th mating hole B; the Nth mating hole B is located at the middle position of the horizontal projection of the (N-1)th mating hole A and the Nth mating hole A.

[0084] like Figure 17 As shown in this embodiment, the mating holes A and / or B on the outermost sides of the first wave deflector do not have other mating holes on their adjacent sides. Therefore, apart from the outermost mating holes A and / or B, the remaining mating holes are numbered according to their arrangement order. The "Nth" can represent any mating hole other than the outermost mating holes. Due to the staggered arrangement of mating holes A and B, the first wave deflector can better suppress the fluctuations on the coolant surface. The wave deflector holes on the second wave deflector are arranged in the same way as those on the first wave deflector, also staggered, to further enhance the suppression of internal surging below the coolant surface.

[0085] In this embodiment of the invention, anti-wave holes provided on the first and second anti-wave plates respectively suppress fluctuations on the surface of the coolant and internal surges below the surface of the coolant. At the same time, the piezoelectric sheet receives the internal surges below the surface of the coolant, generates an electrical signal, and vibrates according to the vibration signal generated by the electrical signal, which drives the second anti-wave plate to vibrate, thereby suppressing the internal surges below the surface of the coolant.

[0086] The specific structure of the active-passive automatic switching phase change liquid cooling device is as described in Embodiment 1, and will not be further explained in this embodiment.

[0087] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A phase change liquid cooling device with automatic switching between active and passive operation, characterized in that, include: A chassis and an active / passive switch are provided. The chassis includes a cooling chamber and a drive chamber. The cooling chamber contains coolant. The active / passive switch includes a working fluid pump and a temperature sensor. The working fluid pump is located in the drive chamber and is connected to the cooling chamber via a pipe. A heating element is located in the cooling chamber, and the temperature sensor is located in the steam space above the heating element. The coolant is used to absorb the heat generated by the heating device and generate steam; the temperature sensor is used to detect the steam temperature value in the steam space; the working fluid pump is used to drive the flow of the coolant; the phase change liquid cooling device has a passive phase change working mode and an active phase change working mode. When the steam temperature is less than or equal to the boiling point of the coolant, the working fluid pump is turned off, and the phase change liquid cooling device operates in passive phase change mode; when the steam temperature is greater than the boiling point of the coolant, the working fluid pump is turned on, and the phase change liquid cooling device operates in active phase change mode. It also includes a multi-layer perforated wave suppression device based on a piezoelectric beam structure. The multi-layer perforated wave suppression device based on a piezoelectric beam structure is disposed on the coolant surface in the cooling chamber. The multi-layer perforated wave suppression device includes: a first anti-wave plate and at least one second anti-wave plate. The second anti-wave plate is disposed below the first anti-wave plate. The first anti-wave plate is disposed on the coolant surface, and the second anti-wave plate is disposed below the coolant surface. Both the first and second anti-wave plates are provided with anti-wave holes, and the second anti-wave plate is provided with piezoelectric sheets. The anti-surge holes on the first anti-surge plate are used to suppress fluctuations on the surface of the coolant; the anti-surge holes on the second anti-surge plate are used to suppress internal surging below the surface of the coolant; the piezoelectric sheet is used to receive the internal surging below the surface of the coolant, thereby generating an electrical signal; the piezoelectric sheet is used to vibrate according to the vibration signal generated by the electrical signal, and the piezoelectric sheet is also used to drive the second anti-surge plate to vibrate, so as to counteract the internal surging below the surface of the coolant.

2. The phase change liquid cooling device with active / passive automatic switching as described in claim 1, characterized in that, The active-passive switch also includes a controller, the temperature sensor is connected to the controller, and the controller is connected to the working fluid pump; The temperature sensor is used to detect the steam temperature value in the steam space and transmit the steam temperature value to the controller; The controller is used to receive the steam temperature value and compare the steam temperature value with the boiling point temperature of the coolant. Based on different comparison results, it controls the opening and closing of the working fluid pump.

3. The phase change liquid cooling device with active / passive automatic switching as described in claim 2, characterized in that, The passive phase transition working mode is specifically as follows: When the steam temperature detected by the temperature sensor is less than or equal to the boiling point temperature of the coolant, the controller controls the working fluid pump to shut down, the coolant stops flowing, and the heating element and the coolant exchange heat to achieve heat transfer.

4. The phase change liquid cooling device with active / passive automatic switching as described in claim 2, characterized in that, The active phase transition working mode is specifically as follows: When the steam temperature detected by the temperature sensor is greater than the boiling point of the coolant, the controller controls the working fluid pump to start, and the working fluid pump drives the coolant to flow to achieve convective heat dissipation. The heating device and the coolant exchange heat to achieve heat transfer.

5. The phase change liquid cooling device with active / passive automatic switching as described in claim 1, characterized in that, The chassis also includes an interface cavity, the drive cavity is located on one side of the cooling cavity, and the interface cavity is located on the other side of the cooling cavity; The interface cavity is equipped with a connector, and external devices are connected to the connector. The heating element is connected to the connector for communication between the heating element and the external device.

6. The phase change liquid cooling device with active / passive automatic switching as described in claim 1, characterized in that, The cooling chamber is provided with at least one inlet end and at least one outlet end, the at least one outlet end being higher than the at least one inlet end; the at least one outlet end being disposed close to the liquid surface of the coolant; the at least one inlet end and the at least one outlet end being distributed on both sides of the cooling chamber; The working fluid pump is connected to at least one inflow end and at least one outflow end via pipelines.

7. The phase change liquid cooling device with active / passive automatic switching as described in claim 1, characterized in that, The active-passive automatic switching phase change liquid cooling device includes a condensation reflux module, which is located in the upper part of the cooling chamber; The condensation reflux module includes an annular heat pipe and an air-to-air heat exchanger. The air-to-air heat exchanger is disposed above the cooling chamber, and the vapor space is formed between the air-to-air heat exchanger and the liquid surface of the coolant. The annular heat pipe is located at the bottom of the air-to-air heat exchanger to absorb the heat of the steam in the steam space and transfer the heat to the air-to-air heat exchanger.

8. The phase change liquid cooling device with active-passive automatic switching as described in claim 7, characterized in that, The active-passive automatic switching phase change liquid cooling device also includes a forced air cooling module, which is disposed on the condensation reflux module; The forced air cooling module includes a fan and heat dissipation fins. The heat dissipation fins are fixed on the air-to-air heat exchanger and are used to receive heat from the air-to-air heat exchanger. The fan is located on top of the heat dissipation fins and is used to blow external cold air into the cooling chamber to remove the heat from the heat dissipation fins.

9. The phase change liquid cooling device with active / passive automatic switching as described in claim 8, characterized in that, The phase change liquid cooling device also includes a pressure detection module, which includes a pressure sensor and a pressure gauge, and the pressure sensor and the pressure gauge are connected. The pressure sensor is installed in the steam space and is used to detect the pressure in the steam space; The pressure gauge is mounted on the forced air cooling module to facilitate observation of the pressure in the steam space.

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