Water chiller and cooling control method

Abstract

This application relates to a chiller and a cooling control method. The heat from the load equipment is carried by the coolant, which flows back to the expansion tank via a return pipe, forming a closed-loop coolant circulation. When it is necessary to lower the coolant temperature or maintain a low temperature, the refrigeration module starts, and the compressor drives the refrigerant to circulate between the evaporator, condenser, and throttling element. The refrigerant absorbs heat from the coolant in the evaporator, lowering the coolant temperature; the condenser dissipates the heat absorbed by the refrigerant, and the cooled refrigerant re-enters the evaporator, forming a closed-loop refrigeration cycle until the coolant temperature reaches the target value. This chiller overcomes the temperature range limitations of traditional chillers, solves the problem of insufficient high-temperature control capability, and achieves stable operation over a wide temperature range, covering various application scenarios such as low-temperature cooling, constant temperature operation, and high-temperature regulation, thus improving its flexibility of use.

Description

Technical Field

[0001] This application relates to the field of cooling technology, and in particular to chillers and cooling control methods. Background Technology

[0002] With the increasing demand for stable low-temperature cold sources in industries such as industrial manufacturing, precision electronics, data centers, chemical reactions, medical devices, and commercial HVAC, chillers have become the core equipment for achieving continuous cooling and precise temperature control.

[0003] In related technologies, the application scenarios for chillers are limited. Summary of the Invention

[0004] Therefore, it is necessary to provide a new type of chiller to address the limitation of existing chiller applications.

[0005] A chiller, the chiller comprising:

[0006] The coolant circulation unit includes an expansion tank, a circulation pump, circulation pipelines, an evaporator, an outlet pipeline, and a return pipeline. Driven by the circulation pump, the coolant in the expansion tank is transported to the evaporator through the circulation pipelines to exchange heat with the refrigerant in the evaporator. The coolant after heat exchange is transported to the load device through the outlet pipeline. The coolant after heat exchange with the load device is transported back to the expansion tank through the return pipeline.

[0007] The refrigeration module includes a compressor, a condenser, and a throttling element. In the first operating condition, the compressor is in the on state, and the compressor drives the refrigerant to circulate between the condenser, the throttling element, and the evaporator. After being cooled by the condenser, the refrigerant flows through the throttling element. The refrigerant that flows out of the throttling element exchanges heat with the coolant in the evaporator. The refrigerant after heat exchange flows through the compressor.

[0008] A heating module, used for heat exchange with the coolant, is installed in the circulation pipeline; in the second operating condition, the heating module is in the on state and the compressor is in the off state; or in the second operating condition, the heating module is in the on state and the cooling power of the compressor is reduced; wherein, the temperature of the coolant in the second operating condition is greater than the temperature of the coolant in the first operating condition.

[0009] In one embodiment, the temperature of the coolant under the first operating condition is 10°C to 30°C;

[0010] The temperature of the coolant under the second operating condition is 30°C to 60°C.

[0011] In one embodiment, the circulation pipeline is equipped with a circulation regulating valve to adjust the rotational speed of the circulation pump based on the target flow rate of the coolant;

[0012] The circulation pipeline is equipped with a flow detection device. Based on the actual flow value collected by the flow detection device, the opening of the circulation regulating valve is adjusted so that the difference between the actual flow value of the coolant entering the load equipment and the target flow value is less than 0.1 L / min.

[0013] In one embodiment, the coolant circulation unit further includes a bypass pipeline and a bypass regulating valve disposed on the bypass pipeline, one end of the bypass pipeline being connected to the outlet of the expansion tank and the other end being connected to the outlet pipeline.

[0014] And / or, the chiller further includes a replenishment tank and a replenishment pump; when the liquid level in the expansion tank is lower than a set liquid level value, the replenishment pump delivers the coolant in the replenishment tank to the expansion tank.

[0015] In one embodiment, the outlet pipe is provided with an outlet temperature detection device, which is used to detect the temperature of the coolant in the outlet pipe;

[0016] Under the first operating condition, when the coolant temperature in the outlet pipeline is less than or equal to the set low temperature value for outlet, the power of the compressor is reduced.

[0017] When the coolant temperature in the outlet pipe is higher than the set low temperature value for the outlet, the power of the compressor increases.

[0018] In one embodiment, under the second operating condition, when the coolant temperature of the outlet pipeline is greater than or equal to the set high temperature value for outlet, the power of the heating module is reduced or the heating module is turned off.

[0019] When the coolant temperature in the outlet pipe is lower than the set high temperature value for outlet, the power of the heating module increases.

[0020] In one embodiment, the return pipeline is provided with a return temperature detection device, which is used to detect the temperature of the coolant in the return pipeline;

[0021] Under the first operating condition, when the temperature of the return liquid pipeline is less than or equal to the set low temperature value for return liquid, the power of the compressor is reduced;

[0022] When the temperature of the return liquid pipeline is greater than the set low temperature value for return liquid, the power of the compressor increases.

[0023] In one embodiment, under the second operating condition, when the temperature of the return liquid pipeline is greater than or equal to the set high temperature value for return liquid, the power of the heating module is reduced or the heating module is turned off.

[0024] When the temperature of the return liquid pipeline is lower than the set high temperature value for return liquid, the power of the heating module increases.

[0025] A cooling control method, based on the chiller described above; the cooling control method includes:

[0026] Obtain the target temperature of the coolant;

[0027] When the target temperature is in the first operating condition, the compressor is controlled to be on; when the target temperature is in the second operating condition, the heating module is controlled to be on, and the compressor is controlled to be off or the compressor's cooling power is reduced.

[0028] The coolant temperature in the outlet pipe is obtained, and the power of the compressor and the power of the heating module are adjusted based on the coolant temperature in the outlet pipe.

[0029] The coolant temperature in the return line is obtained, and the power of the compressor and the power of the heating module are adjusted based on the coolant temperature in the return line.

[0030] In one embodiment, the cooling control method further includes:

[0031] Obtain the target flow rate of the coolant;

[0032] Adjust the speed of the circulating pump based on the target flow rate;

[0033] Obtain the actual flow rate of the liquid outlet pipeline;

[0034] The opening of the circulating control valve is adjusted based on the actual flow rate, so that the difference between the actual flow rate and the target flow rate is less than 0.1 L / min.

[0035] In the aforementioned chiller, the coolant stored in the expansion tank is pumped to the evaporator by a circulating pump. After heat exchange in the evaporator, the coolant is then transported to the external load equipment via a storage pipeline for refrigeration, constant temperature, or high temperature control. The heat from the load equipment is carried by the coolant and returns to the expansion tank via a return pipeline, forming a closed-loop coolant circulation. When it is necessary to lower the coolant temperature or maintain a low temperature, the refrigeration module starts, and the compressor drives the refrigerant to circulate between the evaporator, condenser, and throttling element. The refrigerant absorbs heat from the coolant in the evaporator, lowering the coolant temperature. The condenser dissipates the heat absorbed by the refrigerant, and the cooled refrigerant re-enters the evaporator, forming a closed-loop refrigeration cycle until the coolant temperature reaches the target value. When it is necessary to raise the water temperature or maintain a high temperature, the compressor shuts off or reduces its power, and the heating module starts. The heating module precisely heats the coolant in the circulation pipeline. When the target temperature is reached, the heating power of the heating module is reduced or shut off, achieving high temperature or constant temperature control. This chiller breaks through the temperature range limitations of traditional chillers and solves the problem of insufficient high-temperature control capability of traditional chillers. It achieves stable operation over a wide temperature range, covering various application scenarios such as low-temperature cooling, constant room temperature, and high-temperature regulation, thus improving its flexibility of use. Attached Figure Description

[0036] To more clearly illustrate the technical solutions in the embodiments or exemplary embodiments of this application, the drawings used in the description of the embodiments or exemplary embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0037] Figure 1 This is a schematic diagram of a chiller provided in one embodiment of this application.

[0038] Figure 2 for Figure 1 The diagram shows the coolant circulation unit and heating module in the chiller.

[0039] Figure 3 for Figure 1 The diagram shows a refrigeration module in a chiller.

[0040] Figure 4 A flowchart of a cooling control method provided in an embodiment of this application.

[0041] Reference numerals: 111, Make-up pump; 112, Expansion tank; 1121, Sight glass; 113, Heating module; 114, Circulation pump; 115, Circulation pipeline; 116, Evaporator; 117, Pressure detection module; 118, Outlet temperature detection element; 119, Outlet pipeline; 121, Circulation regulating valve; 122, Flow detection element; 123, Manual valve; 124, Pyramid connector; 125, Gas line check valve; 126, Gas source pipeline; 127, Load device; 1271, Drain port; 128, Return pipeline; 129, Return temperature detection element; 131, Compressor; 132, Condenser; 133, Receiver tank; 134, Needle valve; 135, Throttling element; 136, Bypass pipeline; 137, Bypass regulating valve; 138, Low-pressure detection element; 139, High-pressure detection element. Detailed Implementation

[0042] To make the above-mentioned objectives, features, and advantages of this application more apparent and understandable, the specific embodiments of this application are described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of this application. However, this application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of this application. Therefore, this application is not limited to the specific embodiments disclosed below.

[0043] In the description of this application, it should be understood that if terms such as "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" appear, these terms indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0044] Furthermore, where the terms "first" and "second" appear, these terms are for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, where the term "multiple" appears, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0045] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0046] In this application, unless otherwise expressly specified and limited, the use of descriptions such as "above" or "below" the second feature indicates that the first and second features are in direct contact or indirect contact via an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. Similarly, "below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0047] It should be noted that if an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. If an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. If so, the terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used in this application are for illustrative purposes only and do not represent the only possible implementation.

[0048] See Figures 1 to 3As shown, an embodiment of this application provides a chiller including a coolant circulation unit, a refrigeration module, and a heating module 113; the coolant circulation unit includes an expansion tank 112, a circulation pump 114, a circulation pipeline 115, an evaporator 116, an outlet pipeline 119, and a return pipeline 128; driven by the circulation pump 114, the coolant in the expansion tank 112 is transported to the evaporator 116 through the circulation pipeline 115 to exchange heat between the coolant and the refrigerant in the evaporator 116; the coolant after heat exchange is transported to the load device 127 through the outlet pipeline 119; the coolant after heat exchange with the load device 127 is transported to the expansion tank 112 through the return pipeline 128; the refrigeration module includes a compressor 131, a condenser 132, and a throttling element 135; the first working... In the first condition, compressor 131 is in the on state, driving refrigerant to circulate between condenser 132, throttling element 135, and evaporator 116. After being cooled by condenser 132, the refrigerant flows through throttling element 135. After exiting throttling element 135, the refrigerant exchanges heat with coolant in evaporator 116, and the refrigerant after heat exchange flows through compressor 131. Heating module 113 is used for heat exchange with coolant and is installed in circulation pipeline 115. In the second condition, heating module 113 is in the on state, and compressor 131 is in the off state; or in the second condition, heating module 113 is in the on state, and the cooling power of compressor 131 is reduced. In the second condition, the temperature of coolant is higher than that of coolant in the first condition.

[0049] The coolant stored in the expansion tank 112 is output to the evaporator 116 under the drive of the circulating pump 114. After heat exchange in the evaporator 116, it is transported to the external load device 127 through the liquid storage pipeline for cooling control, constant temperature control, or high temperature control of the load device 127. The heat of the load device 127 is carried by the coolant and flows back to the expansion tank 112 through the return liquid pipeline 128, forming a closed-loop circulation of coolant. When it is necessary to lower the coolant temperature or maintain a low temperature, the refrigeration module is started. The compressor 131 drives the refrigerant to circulate between the evaporator 116, the condenser 132, and the throttling element 135. The refrigerant absorbs heat from the coolant in the evaporator 116, causing the coolant temperature to drop. The condenser 132 dissipates the heat absorbed by the refrigerant, and the cooled refrigerant re-enters the evaporator 116, forming a closed-loop refrigeration cycle until the coolant temperature reaches the target temperature value. When it is necessary to increase the water temperature or maintain a high temperature, the compressor 131 shuts down or reduces its power, and the heating module 113 is activated. The heating module 113 precisely heats the coolant in the circulation pipe 115. When the target temperature value is reached, the heating power of the heating module 113 is reduced or turned off, achieving high-temperature control or constant-temperature control. This chiller breaks through the temperature range limitations of traditional chillers and solves the problem of insufficient high-temperature control capability of traditional chillers. It achieves stable operation over a wide temperature range, covering various application scenarios such as low-temperature cooling, constant temperature at room temperature, and high-temperature regulation, thus improving its flexibility of use.

[0050] In one embodiment, the coolant temperature under the first operating condition is 10°C to 30°C (excluding 30°C). The coolant temperature under the second operating condition is 30°C to 60°C. That is to say, the chiller can achieve wide temperature control from 10°C to 60°C, covering a variety of application scenarios such as low-temperature cooling, constant temperature, and high-temperature regulation, thus improving its flexibility of use.

[0051] In some embodiments, the cooling requirements of the load device 127 can be determined based on the temperature of the load device 127, thereby enabling the determination of parameters such as the target flow rate and target temperature of the coolant.

[0052] In some embodiments, the temperature of the load device 127 can be determined based on its operating status at different time periods, thereby determining the cooling requirements of the load device 127 during the corresponding time period, and establishing a mapping relationship between time periods and target coolant temperature values, as well as between time periods and target flow rates. The chiller controller can automatically obtain the target flow rate and target temperature values ​​of the coolant during the current time period.

[0053] See Figures 1 to 2As shown, in one embodiment, the circulation pipeline 115 is provided with a circulation regulating valve 121 to adjust the speed of the circulation pump 114 based on the target flow rate of the coolant; the circulation pipeline 115 is provided with a flow detection element 122 to adjust the opening of the circulation regulating valve 121 based on the actual flow rate value collected by the flow detection element 122, so that the difference between the actual flow rate value of the coolant entering the load device 127 and the target flow rate value is less than 0.1 L / min.

[0054] In some embodiments, the circulating pump 114 can be a variable frequency circulating pump 114, which allows for a wide range of adjustment of the coolant flow rate, i.e., coarse adjustment. The circulating regulating valve 121 can be an electronic expansion valve, which enables fine-tuning of the flow rate, ensuring that the difference between the actual flow rate and the target flow rate is less than 0.1 L / min. This reduces the flow control error to ±0.1 L / min, improving flow control accuracy and meeting the flow stability requirements of high-precision scenarios such as scientific research experiments and precision manufacturing. In some embodiments, the electronic expansion valve is model EBV03H001.

[0055] In other embodiments, the circulation pump 114 can be a constant-speed circulation pump 114, and the regulating valve can be a proportional regulating valve or an electronic regulating valve; the constant-speed circulation pump 114 provides a fixed base flow rate, and the flow rate can be finely adjusted through the proportional regulating valve or the electronic regulating valve. The constant-speed circulation pump 114 has a low failure rate and low maintenance cost, and is suitable for scenarios with relatively fixed flow requirements.

[0056] In other embodiments, a variable frequency circulating pump 114 and a constant speed circulating pump 114 can be operated in parallel. By controlling the start and stop of the variable frequency circulating pump 114 and the constant speed circulating pump 114, as well as the speed of the variable frequency circulating pump 114, flow rate regulation can be achieved. Moreover, when one circulating pump 114 fails, the other circulating pump 114 can continue to work, improving system reliability and making it suitable for application scenarios with high requirements for continuous operation of equipment, such as AI computing centers.

[0057] In some embodiments, the flow detection element 122 is selected from mass flow meters or high-frequency ultrasonic flow meters, which offer higher detection accuracy and faster response speed compared to traditional turbine flow meters. This enables real-time acquisition and feedback of flow data, providing precise detection data for closed-loop flow control. In some embodiments, the flow detection element 122 can be a flow meter of model RD-ME06-DN10. In other embodiments, the flow detection element 122 can also be a flow sensor or the like.

[0058] See Figures 1 to 2As shown, in one embodiment, the coolant circulation unit further includes a bypass pipe 136 and a bypass regulating valve 137 disposed on the bypass pipe 136. One end of the bypass pipe 136 is connected to the outlet port of the expansion tank 112, and the other end of the bypass pipe 136 is connected to the outlet pipe 119. The opening degree of the bypass regulating valve 137 can be controlled according to the cooling requirements of the load device 127, thereby adjusting the flow rate of the bypass pipe 136. Since the coolant in the bypass pipe 136 does not exchange heat with the evaporator 116, by adjusting the flow rate of the bypass pipe 136, the flow rate and temperature of the coolant flowing out of the bypass pipe 136 and the evaporator 116 can be adjusted, that is, the flow rate and temperature entering the load device 127 can be adjusted to meet the cooling requirements of the load device 127. In addition, when the flow rate of the circulation pump 114 is too high, the bypass regulating valve 137 is opened to short-circuit and return part of the liquid to ensure the stability of the flow rate and temperature of the coolant in the outlet pipe 119.

[0059] See Figures 1 to 2 As shown, in some embodiments, the chiller further includes a replenishing water tank and a replenishing pump 111. One end of the replenishing pump 111 is connected to the replenishing water tank, and the other end is connected to an expansion tank 112. When the liquid level in the expansion tank 112 is lower than a set liquid level, the replenishing pump 111 delivers the coolant from the replenishing water tank to the expansion tank 112. This enables automatic replenishment of the expansion tank 112, maintaining a stable liquid level and pressure, and improving the stability of the chiller's operation. The expansion tank 112 has a pressure stabilizing function; it automatically replenishes liquid when the system pressure is too low and partially returns liquid to the expansion tank 112 when the pressure is too high to maintain stable system pressure. In some embodiments, the volume of the expansion tank 112 can reach 3L. In some embodiments, a level gauge is installed inside the expansion tank 112. In some embodiments, the expansion tank 112 is equipped with a sight glass 1121 for visually observing the liquid level.

[0060] like Figure 1 As shown, in some embodiments, the coolant outlet pipe 119 is provided with a drain port 1271, through which coolant can be discharged, reducing the risk of corrosion. For example... Figure 1 As shown, in some embodiments, the liquid outlet pipe 119 is connected to a gas source pipe 126, which is used to connect to an external gas source. The gas source pipe 126 is equipped with a gas pipe check valve 125. During system maintenance, the residual liquid in the chiller pipe is purged by the external gas source to prevent corrosion.

[0061] like Figure 1 and Figure 2As shown, in some embodiments, a hand valve 123 is provided at the interface of the load device 127. When the load device 127 is not connected, the hand valve 123 is closed to prevent coolant leakage. When the load device 127 is connected, the interface of the load device 127 is connected to the outlet pipe 119 through the pagoda connector 124 and the hand valve 123 is opened. The pagoda connector 124 achieves a sealed connection of the pipe, reducing the risk of coolant leakage and ensuring cooling reliability.

[0062] See Figures 1 to 2 As shown, in one embodiment, the liquid outlet pipeline 119 is equipped with a pressure detection module 117 to detect the pressure inside the pipeline and ensure that the pressure inside the pipeline is stable.

[0063] See Figures 1 to 2 As shown, in one embodiment, the outlet pipe 119 is equipped with an outlet temperature detection element 118, which is used to detect the temperature of the coolant in the outlet pipe 119. Under the first operating condition, when the coolant temperature in the outlet pipe 119 is less than or equal to the set low outlet temperature value, the power of the compressor 131 can be appropriately reduced; when the coolant temperature in the outlet pipe 119 is greater than the set low outlet temperature value, the power of the compressor 131 can be appropriately increased. By collecting the coolant temperature in the pipe in real time through the outlet temperature detection element 118, a closed-loop control of temperature and compressor 131 power is formed, maintaining the outlet temperature of the coolant near the set low temperature value, reducing the risk of large temperature fluctuations, and also reducing unnecessary energy waste.

[0064] In one embodiment, under the second operating condition, when the coolant temperature in the outlet pipe 119 is greater than or equal to the set high temperature value for outlet cooling, the power of the heating module 113 is reduced or the heating module 113 is turned off; when the coolant temperature in the outlet pipe 119 is less than the set high temperature value for outlet cooling, the power of the heating module 113 is increased. In this way, the coolant temperature can be stabilized near the set high temperature value, avoiding temperature overshoot or large fluctuations; when the temperature reaches or exceeds the set high temperature value, the power of the heating module 113 is reduced or the heating module 113 is turned off, reducing energy waste and achieving on-demand heating and energy-saving operation. In some embodiments, the outlet temperature detection element 118 can be a thermometer or a temperature sensor, etc.

[0065] See Figures 1 to 2As shown, in one embodiment, the return liquid line 128 is equipped with a return liquid temperature detection element 129, which is used to detect the temperature of the coolant in the return liquid line 128. Under the first operating condition, when the temperature of the return liquid line 128 is less than or equal to the set low temperature value for return liquid, the power of the compressor 131 is reduced; when the temperature of the return liquid line 128 is greater than the set low temperature value for return liquid, the power of the compressor 131 is increased. If the return water temperature rises, it indicates that the load heat generation is increasing, so the power of the compressor 131 can be increased to enhance the cooling effect. When the return water temperature decreases, it indicates that the load heat generation is decreasing, so the power of the compressor 131 can be reduced to save energy. By detecting the outlet and return liquid temperatures of the coolant, the actual heat exchange effect of the load device 127 can be more accurately reflected, making the power adjustment of the compressor 131 more timely and closer to the actual heat load, thereby reducing coolant temperature fluctuations and improving overall temperature control accuracy. The return liquid temperature detection element 129 can be a thermometer or a temperature sensor, etc.

[0066] In one embodiment, under the second operating condition, when the temperature of the return liquid pipeline 128 is greater than or equal to the set high temperature value for return liquid, the power of the heating module 113 is reduced or the heating module 113 is turned off; when the temperature of the return liquid pipeline 128 is less than the set high temperature value for return liquid, the power of the heating module 113 is increased. When the return liquid temperature reaches or exceeds the set high temperature value for return liquid, the power of the heating module 113 is reduced or turned off in a timely manner to avoid ineffective heating and reduce power consumption; when the temperature is too low, the heating power is increased to achieve on-demand heating and improve energy saving. The outlet liquid temperature and the return liquid temperature jointly participate in temperature control, reducing coolant temperature fluctuations and improving overall temperature control accuracy.

[0067] In some embodiments, the heating module 113 can be an electric heating module 113 with a heating power of up to 1KW, such as a PTC self-regulating heater, which has self-regulating characteristics, no risk of overheating, high safety, and is suitable for scientific research experiments, small equipment and other scenarios with high safety requirements; or a tubular electric heater can be used, which has high heating efficiency and strong corrosion resistance, and is suitable for industrial scenarios where the coolant is a corrosive medium; of course, a plate electric heater can also be used, which has a large heat exchange area, uniform heating, and is suitable for high flow rate coolant heating scenarios.

[0068] In other embodiments, the heating module 113 can recover the heat released from the condenser side of the cooling module and use the recovered heat to heat the coolant. In this way, the electric heating module 113 can be eliminated, significantly reducing heating energy consumption and improving the overall energy efficiency of the system by more than 30%, making it suitable for high-flow, long-term operation scenarios that are sensitive to operating costs.

[0069] like Figure 1As shown, in some embodiments, the chiller is provided with an evaporator 116, and the number of load devices 127 can be multiple. Multiple load devices 127 share one evaporator 116. That is, the coolant circulation unit includes multiple outlet pipes 119 and multiple return pipes 128. Each outlet pipe 119 and each return pipe 128 corresponds to one load device 127.

[0070] In some embodiments, multiple evaporators 116 can be set up and connected to different external load circuits respectively to achieve independent control of multiple circuits, and the flow rate of each circuit can maintain an accuracy of ±0.1L / min, which is suitable for scenarios where multiple devices are liquid-cooled at the same time, such as multiple experimental devices in a laboratory.

[0071] In some embodiments, the evaporator 116 can be a conventional plate heat exchanger. In some embodiments, the evaporator 116 can be a shell-and-tube heat exchanger, where the coolant flows in the tube side and the refrigerant flows in the shell side, exchanging heat through the tube walls. Shell-and-tube heat exchangers have strong pressure resistance and good anti-fouling ability, making them suitable for industrial scenarios with high heat density and high impurity levels in the coolant. In other embodiments, the evaporator 116 can be a microchannel heat exchanger, employing a microchannel structure design. This results in a large heat exchange area, high heat exchange efficiency, and a smaller size and lighter weight, making it more suitable for scenarios with limited installation space, such as small laboratory equipment. It also improves the overall compactness of the system and facilitates mobile deployment.

[0072] In some embodiments, the compressor 131 is a single 1.5HP fixed-frequency compressor 131. In other embodiments, there are two compressors 131, which operate in parallel. One or both compressors 131 can be started or stopped according to the cooling demand, thereby increasing the range of cooling capacity adjustment and adapting to scenarios with large fluctuations in heat density.

[0073] In some embodiments, the compressor 131 is a variable frequency compressor 131. By adjusting the speed of the compressor 131, the cooling capacity can be continuously and precisely adjusted. Combined with closed-loop temperature control, the temperature control accuracy is further improved, making it suitable for scientific research experimental scenarios with extremely high requirements for the accuracy of coolant temperature.

[0074] In some embodiments, the condenser 132 can be an air-cooled heat dissipation component, such as a cooling fan, which is used to dissipate heat from the refrigeration module to the outside air to maintain a stable refrigeration cycle.

[0075] In some embodiments, the throttling element 135 can be an expansion valve, which functions as a throttling and pressure-reducing valve. It can convert the high-temperature, high-pressure refrigerant from the condenser 132 into a low-temperature, low-pressure refrigerant through a throttling orifice. Moreover, it can automatically adjust the refrigerant flow rate into the evaporator 116 according to load changes to ensure cooling effect. After the low-temperature, low-pressure refrigerant from the throttling element 135 enters the evaporator 116, it exchanges heat with the coolant to become a medium-temperature, low-pressure refrigerant. Then it enters the compressor 131, is compressed into a high-temperature, high-pressure refrigerant, and then returns to the condenser 132 for heat dissipation.

[0076] like Figure 1 and Figure 3 As shown, in some embodiments, the piping of the refrigeration module is also equipped with a needle valve 134 and a liquid receiver 133. The liquid receiver 133 is used to store refrigerant, and the needle valve 134 can replenish the refrigerant into the liquid receiver 133, thereby ensuring the pressure stability in the piping of the refrigeration module. Figure 3 As shown, the refrigeration module's piping is equipped with two needle valves 134. One needle valve 134 can be connected to a pressure gauge, and the other needle valve 134 is used to replenish refrigerant. When the pressure in the refrigeration module's piping reaches the target value, refrigerant replenishment stops. In some embodiments, the volume of the liquid receiver 133 can be 1L.

[0077] like Figure 1 As shown, in some embodiments, the piping in the refrigeration module can be selected using metric pipes with a diameter of DN8 or DN20. For example... Figure 1 As shown, in some embodiments, the piping of the refrigeration module is further equipped with a low-pressure detection element 138 and a high-pressure detection element 139 to monitor the pressure status of the refrigerant circulation. For example, the low-pressure threshold in the refrigeration module is 1 bar. When the pressure in the piping is lower than 1 bar, the system alarms or shuts down to prevent the circulation pump 114 from running dry. The high-pressure threshold in the refrigeration module can be 28 bar. When the high-pressure side exceeds 28 bar, an alarm or shutdown is triggered to protect the compressor 131 and condenser 132 from pipe bursting or damage. In some embodiments, the low-pressure detection element 138 and the high-pressure detection element 139 can be pressure sensors.

[0078] In some embodiments, a temperature sensing element is further provided in the piping of the refrigeration module for sensing the temperature of the refrigerant within the piping. In some embodiments, the temperature sensing element can be a patch-type temperature sensor. In other embodiments, the temperature sensing element can also be a thermometer.

[0079] In some embodiments, the chiller uses a standard 220V AC power plug as its power supply interface, enabling plug-and-play rapid deployment without requiring on-site power distribution modifications, thus optimizing the overall size and structural layout of the equipment. The chiller is suitable for scenarios with high mobility requirements, such as laboratories, small computing nodes, and production line verification, significantly improving deployment flexibility. Through coordinated control of coolant flow and temperature, the chiller reduces temperature overshoot by more than 60% and shortens lag time by more than 50% under flow fluctuation conditions, improving temperature control reliability under complex operating conditions.

[0080] Before the chiller starts operating, first check that all pipe connections are sealed and that the liquid level in the expansion tank 112 is within the specified range. After confirming everything is correct, insert the 220V AC power plug into the standard AC power interface to complete the power connection. Next, input the target flow rate and target water temperature into the chiller's controller, and the equipment will automatically complete self-tests for each detection module. After the self-tests pass, the circulation pump 114 starts at low speed, the coolant begins circulating at a small flow rate, and the flow rate sensor 122 and temperature sensor begin collecting data in real time. The chiller then enters initialization standby mode.

[0081] The controller determines the corresponding operating condition based on the target coolant temperature. For example, if the target coolant temperature is 25°C, it is in the first operating condition. Correspondingly, the compressor 131 is in the start-up state, the refrigerant begins to circulate, and the evaporator 116 is in the cooling state.

[0082] The speed of the circulating pump 114 is adjusted according to the target flow rate of the coolant, and the opening of the circulating regulating valve 121 is adjusted based on the real-time data of the flow detection element 122, so that the difference between the target flow rate and the actual flow rate is within 0.1 L / min.

[0083] The outlet temperature sensor 118 and return temperature sensor 129 collect data in real time. When the coolant temperature reaches the target temperature, the controller adjusts the power of the compressor 131 to a constant temperature maintenance power to ensure stable coolant temperature. If the return water temperature rises, it indicates increased heat generation from the load, so the power of the compressor 131 can be increased or the coolant flow rate can be increased. When the return water temperature decreases, it indicates decreased heat generation from the load, so the power of the compressor 131 and the coolant flow rate can be reduced to save energy.

[0084] Similarly, when the target temperature of the coolant is in the second operating condition, the compressor 131 can be shut off or operate at its lowest cooling power to offset heat loss from the piping; simultaneously, the heating module 113 is activated. The heating module 113 adjusts its heating power according to the target temperature, and the coolant, after being heated by the heating module 113, is delivered to the external load to achieve high-temperature control or constant-temperature control. When the return water temperature is higher than the target value, the heating power can be appropriately reduced; when the return water temperature is lower than the target value, the heating power can be increased to achieve precise constant temperature.

[0085] When rapidly switching the target coolant temperature, such as from 20°C to 50°C, the controller immediately shuts off the compressor 131 and simultaneously adjusts the heating power of the heating module 113 to its maximum power, achieving rapid cooling of the coolant. The controller can also adjust the flow parameters in advance based on the rate of water temperature change to avoid uneven temperature caused by flow fluctuations during the heating process. When the coolant temperature approaches the target temperature, the heating module 113 switches to precise fine-tuning power, achieving rapid and overshoot-free cooling temperature switching.

[0086] In some embodiments, when a shutdown command is manually input into the controller, the system first shuts down the cooling module and heating module 113, and the circulating pump 114 runs at low speed for 30 seconds to complete the return of coolant and cooling of the pipeline. After the circulating pump 114 stops running, the controller cuts off the power supply, completing the shutdown. Routine maintenance only requires checking the coolant level and pipeline sealing, without the need for professional power distribution or disassembly maintenance, reducing maintenance costs.

[0087] Furthermore, one embodiment of this application also provides a cooling control method based on the chiller described above; the cooling control method includes:

[0088] Step S100: Obtain the target temperature of the coolant.

[0089] Users can manually input and set the target temperature value of the coolant through the chiller's controller. The system receives and stores this temperature value as a control reference. Alternatively, the system can have multiple built-in preset operating modes, such as low-temperature cooling mode and high-temperature constant temperature mode. The controller will automatically call up the preset target temperature parameters for the corresponding mode based on the currently selected operating mode.

[0090] In step S200, when the target temperature is in the first operating condition, the compressor 131 is controlled to be turned on; when the target temperature is in the second operating condition, the heating module 113 is controlled to be turned on, and the compressor 131 is turned off or the cooling power of the compressor 131 is reduced.

[0091] When the target temperature of the coolant is between 10℃ and 30℃ (excluding 30℃), it corresponds to the first operating condition; when the target temperature of the coolant is between 30℃ and 60℃, it corresponds to the second operating condition. The system automatically distinguishes between cooling and heating conditions based on the target temperature. In cooling condition, only compressor 131 operates, while in heating condition, compressor 131 is shut down or its cooling power is significantly reduced to decrease energy waste and improve system energy efficiency.

[0092] In step S300, the coolant temperature of the outlet pipe 119 is obtained, and the power of the compressor 131 and the power of the heating module 113 are adjusted based on the coolant temperature of the outlet pipe 119.

[0093] The outlet pipe 119 may be equipped with an outlet temperature detection element 118, which can collect the temperature of the coolant in the outlet pipe 119. The controller acquires the coolant temperature of the outlet pipe 119 collected by the outlet temperature detection element 118 and compares this temperature with the target temperature. Taking the first operating condition as an example, when the coolant temperature of the outlet pipe 119 is higher than the target temperature, the controller increases the cooling power of the compressor 131 to enhance the cooling capacity and lower the coolant temperature. When the coolant temperature of the outlet pipe 119 is lower than the target temperature, the controller decreases the cooling power of the compressor 131. In the second operating condition, when the coolant temperature of the outlet pipe 119 is greater than or equal to the target temperature, the power of the heating module 113 is reduced or the heating module 113 is turned off; when the coolant temperature of the outlet pipe 119 is lower than the target temperature, the power of the heating module 113 is increased.

[0094] In step S400, the coolant temperature of the return pipe 128 is obtained, and the power of the compressor 131 and the power of the heating module 113 are adjusted based on the coolant temperature of the return pipe 128.

[0095] The return line 128 is equipped with a return temperature sensor 129, which can collect the coolant temperature in the outlet line 119. The controller acquires the coolant temperature in the outlet line 119 collected by the return temperature sensor 129 and compares it with the target temperature. In the first operating condition, when the temperature of the return line 128 is less than or equal to the set low temperature value, the power of the compressor 131 is reduced; when the temperature of the return line 128 is greater than the set low temperature value, the power of the compressor 131 is increased, achieving on-demand cooling and reducing energy waste. In the second operating condition, when the temperature of the return line 128 is greater than or equal to the set high temperature value, the power of the heating module 113 is reduced or the heating module 113 is turned off; when the temperature of the return line 128 is less than the set high temperature value, the power of the heating module 113 is increased, achieving on-demand heating and reducing ineffective heating.

[0096] In one embodiment, the cooling control method further includes: obtaining a target flow rate of coolant; adjusting the rotational speed of the circulation pump 114 based on the target flow rate; obtaining the actual flow rate of the outlet pipe 119; and adjusting the opening of the circulation regulating valve 121 based on the actual flow rate, so that the difference between the actual flow rate and the target flow rate is less than 0.1 L / min.

[0097] Users can manually input and set the target flow rate of the coolant through the chiller's controller. The system receives and stores this value as a control reference. Alternatively, the system can have multiple built-in preset operating modes, such as low-temperature cooling mode and high-temperature constant-temperature mode. The controller automatically calls the preset target flow rate parameters for the corresponding mode based on the currently selected operating mode. Based on the target flow rate of the coolant, the speed of the circulating pump 114 is adjusted to achieve a wide range of coolant flow rate regulation. The circulating pipeline 115 is equipped with a flow detection element 122. Based on the actual flow rate value collected by the flow detection element 122, the opening of the circulating regulating valve 121 is adjusted to complete the fine-tuning of the flow rate, reducing the flow control error to 0.1L / min and improving the flow control accuracy.

[0098] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0099] The above embodiments merely illustrate several implementation methods of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent application. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the protection scope of this application. Therefore, the protection scope of this patent application should be determined by the appended claims.

Claims

1. A water chiller characterized by, The chiller includes: The coolant circulation unit includes an expansion tank, a circulation pump, circulation pipelines, an evaporator, an outlet pipeline, and a return pipeline. Driven by the circulation pump, the coolant in the expansion tank is transported to the evaporator through the circulation pipelines to exchange heat with the refrigerant in the evaporator. The coolant after heat exchange is transported to the load device through the outlet pipeline. The coolant after heat exchange with the load device is transported back to the expansion tank through the return pipeline. The refrigeration module includes a compressor, a condenser, and a throttling element. In the first operating condition, the compressor is in the on state, and the compressor drives the refrigerant to circulate between the condenser, the throttling element, and the evaporator. After being cooled by the condenser, the refrigerant flows through the throttling element. The refrigerant that flows out of the throttling element exchanges heat with the coolant in the evaporator. The refrigerant after heat exchange flows through the compressor. A heating module, used for heat exchange with the coolant, is installed in the circulation pipeline; in the second operating condition, the heating module is in the on state and the compressor is in the off state; or in the second operating condition, the heating module is in the on state and the cooling power of the compressor is reduced; wherein, the temperature of the coolant in the second operating condition is greater than the temperature of the coolant in the first operating condition.

2. The water chiller according to claim 1, characterized in that, The temperature of the coolant under the first operating condition is 10°C to 30°C; The temperature of the coolant under the second operating condition is 30°C to 60°C.

3. The water chiller of claim 1, wherein The circulation pipeline is equipped with a circulation regulating valve to adjust the speed of the circulation pump based on the target flow rate of the coolant. The circulation pipeline is equipped with a flow detection device. Based on the actual flow value collected by the flow detection device, the opening of the circulation regulating valve is adjusted so that the difference between the actual flow value of the coolant entering the load equipment and the target flow value is less than 0.1 L / min.

4. The water chiller of claim 1, wherein The coolant circulation unit also includes a bypass pipeline and a bypass regulating valve disposed on the bypass pipeline. One end of the bypass pipeline is connected to the outlet of the expansion tank, and the other end is connected to the outlet pipeline. And / or, the chiller further includes a replenishment tank and a replenishment pump; when the liquid level in the expansion tank is lower than a set liquid level value, the replenishment pump delivers the coolant in the replenishment tank to the expansion tank.

5. The water chiller of claim 1, wherein The outlet pipe is equipped with an outlet temperature detection device, which is used to detect the temperature of the coolant in the outlet pipe. Under the first operating condition, when the coolant temperature in the outlet pipeline is less than or equal to the set low temperature value for outlet, the power of the compressor is reduced. When the coolant temperature in the outlet pipe is higher than the set low temperature value for the outlet, the power of the compressor increases.

6. The chiller according to claim 5, characterized in that, In the second operating condition, when the coolant temperature in the outlet pipe is greater than or equal to the set high temperature value for outlet, the power of the heating module is reduced or the heating module is turned off; when the coolant temperature in the outlet pipe is less than the set high temperature value for outlet, the power of the heating module is increased.

7. The chiller according to claim 5, characterized in that, The return liquid pipeline is equipped with a return liquid temperature detection device, which is used to detect the temperature of the coolant in the return liquid pipeline; Under the first operating condition, when the temperature of the return liquid pipeline is less than or equal to the set low temperature value for return liquid, the power of the compressor decreases; when the temperature of the return liquid pipeline is greater than the set low temperature value for return liquid, the power of the compressor increases.

8. The chiller according to claim 7, characterized in that, In the second operating condition, when the temperature of the return liquid pipeline is greater than or equal to the set high temperature value for return liquid, the power of the heating module is reduced or the heating module is turned off. When the temperature of the return liquid pipeline is lower than the set high temperature value for return liquid, the power of the heating module increases.

9. A cooling control method, characterized in that, Based on the chiller as described in any one of claims 1 to 8; The cooling control method includes: Obtain the target temperature of the coolant; When the target temperature is in the first operating condition, the compressor is controlled to be on; when the target temperature is in the second operating condition, the heating module is controlled to be on, and the compressor is controlled to be off or the compressor's cooling power is reduced. The coolant temperature in the outlet pipe is obtained, and the power of the compressor and the power of the heating module are adjusted based on the coolant temperature in the outlet pipe. The coolant temperature in the return line is obtained, and the power of the compressor and the power of the heating module are adjusted based on the coolant temperature in the return line.

10. The cooling control method according to claim 9, characterized in that, The cooling control method further includes: Obtain the target flow rate of the coolant; Adjust the speed of the circulating pump based on the target flow rate; Obtain the actual flow rate of the liquid outlet pipeline; The opening of the circulating control valve is adjusted based on the actual flow rate, so that the difference between the actual flow rate and the target flow rate is less than 0.1 L / min.

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