Control method, thermo-acoustic heat pump refrigerator and storage medium

Abstract

The application discloses a control method, a thermoacoustic heat pump refrigerator and a storage medium. The thermoacoustic heat pump refrigerator comprises a box body and a thermoacoustic heat pump system arranged in the box body. The thermoacoustic heat pump system comprises a thermoacoustic driver. The control method comprises the following steps: acquiring operation parameter information of the thermoacoustic heat pump refrigerator, wherein the operation parameter information comprises at least one of a box body temperature, an ambient temperature, a hot end temperature, a door opening frequency and a running time length; and adjusting working parameters of the thermoacoustic heat pump system according to the operation parameter information, wherein the working parameters comprise at least one of a working pressure, a resonance frequency of the thermoacoustic driver and an output power. According to the control method, the working parameters of the thermoacoustic heat pump system are dynamically adjusted according to the actual operation state of the refrigerator, so that the system can maintain a high-efficiency operation state under different working conditions. Compared with a fixed parameter operation mode, the control method can greatly reduce energy consumption and improve temperature control precision.

Description

Technical Field

[0001] This application relates to the field of refrigerator technology, specifically to a control method, a thermoacoustic heat pump refrigerator, and a storage medium. Background Technology

[0002] Thermoacoustic refrigeration technology is a novel refrigeration technology that utilizes sound energy to transfer heat. Its basic principle is that, under the influence of the sound field within a resonant tube, the working gas undergoes periodic compression and expansion processes in the regenerator, thereby pumping heat from the low-temperature end to the high-temperature end. Compared to traditional vapor compression refrigeration technology, thermoacoustic refrigeration technology has significant advantages such as no moving parts, no use of environmentally friendly refrigerants like Freon, high reliability, and long lifespan, and is considered an important development direction for next-generation green and environmentally friendly refrigeration technologies.

[0003] Thermoacoustic refrigeration technology is increasingly being used in the refrigerator industry. However, existing thermoacoustic heat pump refrigerators suffer from insufficient self-adaptation capabilities, making it difficult to maintain efficient operation and resulting in energy waste.

[0004] Therefore, the technology still needs to be improved and enhanced. Summary of the Invention

[0005] This application provides a control method, a thermoacoustic heat pump refrigerator, and a storage medium, which can improve the adaptive adjustment capability of the thermoacoustic heat pump refrigerator and enhance the refrigerator's operating efficiency.

[0006] This application provides a control method applied to a thermoacoustic heat pump refrigerator, the thermoacoustic heat pump refrigerator including a cabinet and a thermoacoustic heat pump system disposed within the cabinet, the thermoacoustic heat pump system including a thermoacoustic driver, the control method including: Obtain the operating parameter information of the thermoacoustic heat pump refrigerator, the operating parameter information including at least one of the following: cabinet temperature, ambient temperature, hot end temperature, number of times the door is opened, and running time; The operating parameters of the thermoacoustic heat pump system are adjusted according to the operating parameter information. The operating parameters include at least one of the operating pressure, the resonant frequency of the thermoacoustic driver, and the output power.

[0007] In some embodiments, the housing is provided with multiple compartments, and the thermoacoustic heat pump system further includes a cold-end heat exchanger, which is connected to each of the compartments respectively; the control method further includes: delivering the cooling capacity generated by the cold-end heat exchanger to the multiple compartments in turn according to a preset time sequence.

[0008] In some embodiments, the thermoacoustic heat pump system further includes a time-sharing switching channel, which includes multiple parallel branches. One end of each branch is connected to the cold-end heat exchanger, and the other end is connected to the heat exchange mechanism of the corresponding compartment. Each branch is provided with an acoustic impedance adjustment unit, which is used to adjust the acoustic impedance of the corresponding branch to adjust the distribution ratio of the acoustic power output by the cold-end heat exchanger among the multiple branches. The step of sequentially delivering the cooling capacity generated by the cold-end heat exchanger to the multiple compartments according to a preset time sequence includes: Each of the acoustic impedance adjustment units is controlled to adjust the acoustic impedance of the corresponding branch in a time sequence so that the cooling capacity generated by the cold end heat exchanger is delivered to the multiple compartments in turn.

[0009] This application also provides a thermoacoustic heat pump refrigerator, including: Box; A thermoacoustic heat pump system, installed in the enclosure, includes a thermoacoustic driver; A controller, connected to the thermoacoustic heat pump system, is used to adjust the operating parameters of the thermoacoustic heat pump system according to the operating parameter information of the refrigerator; the operating parameter information includes at least one of the following: cabinet temperature, ambient temperature, hot end temperature, number of door openings, and running time; the operating parameters include at least one of the following: operating pressure, resonant frequency of the thermoacoustic driver, and output power.

[0010] In some embodiments, the thermoacoustic heat pump system further includes a regenerator comprising multiple layers of perforated plates stacked sequentially; the aperture of the through holes on the perforated plates gradually increases from the cold end to the hot end of the regenerator; and / or From the cold end to the hot end of the regenerator, the porosity of the through holes on the porous plate gradually increases.

[0011] In some embodiments, the regenerator includes a first plate, a second plate, and a third plate stacked sequentially from the cold end to the hot end; The diameter of the through hole on the first plate is 0.35 mm and the porosity is 65%, the diameter of the through hole on the second plate is 0.4 mm and the porosity is 68%, and the diameter of the through hole on the third plate is 0.5 mm and the porosity is 70%.

[0012] In some embodiments, the working gas in the thermoacoustic heat pump system is pure argon.

[0013] In some embodiments, the thermoacoustic driver is a standing waveform thermoacoustic compressor.

[0014] In some embodiments, the resonant tube is a quarter-wavelength resonator.

[0015] This application also provides a storage medium on which a computer program is stored, wherein the computer executes the above-described control method when it runs.

[0016] The control method, thermoacoustic heat pump refrigerator and storage medium provided in this application dynamically adjust the operating parameters of the thermoacoustic heat pump system according to the actual operating status of the refrigerator, so that the system can maintain a high-efficiency operating state under different operating conditions. Compared with the fixed parameter operation mode, it can significantly reduce energy consumption and improve temperature control accuracy. Attached Figure Description

[0017] The technical solution and other beneficial effects of this application will become apparent from the following detailed description of specific embodiments in conjunction with the accompanying drawings.

[0018] Figure 1 This is a schematic diagram of the structure of a thermoacoustic heat pump system provided in an embodiment of this application.

[0019] Figure 2 This is a schematic diagram of the structure of a thermoacoustic heat pump refrigerator provided in an embodiment of this application.

[0020] Figure 3 This is a schematic diagram of the structure of the regenerator provided in an embodiment of this application.

[0021] Figure 4 for Figure 3 The cross-sectional view of the regenerator shown.

[0022] Figure 5 A flowchart of the control method provided in the embodiments of this application.

[0023] Figure label: 10. Thermoacoustic heat pump refrigerator; 100. Thermoacoustic heat pump system; 200. Controller; 110. Thermoacoustic actuator; 120. Resonant tube; 130. Cold end heat exchanger; 140. Regenerator; 150. Hot end heat exchanger; 141. First plate; 142. Second plate; 143. Third plate. Detailed Implementation

[0024] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the scope of protection of this application.

[0025] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Features thus defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0026] This application provides a thermoacoustic heat pump refrigerator; for example, please refer to [link to example]. Figures 1-2 , Figure 1 This is a schematic diagram of the structure of a thermoacoustic heat pump system provided in an embodiment of this application. Figure 2 This is a schematic diagram of the structure of a thermoacoustic heat pump refrigerator provided in an embodiment of this application. The thermoacoustic heat pump refrigerator 10 includes a cabinet (not shown in the figure) and a thermoacoustic heat pump system 100 and a controller 200 disposed in the cabinet.

[0027] The thermoacoustic heat pump system 100 includes a thermoacoustic actuator 110, a resonant tube 120, a regenerator 140, a cold-end heat exchanger 130, and a hot-end heat exchanger 150. The resonant tube 120 is connected to the output end of the thermoacoustic actuator 110. The thermoacoustic actuator 110 is the system's acoustic energy generating device, used to generate sound waves propagating axially along the resonant tube 120, which can conduct and amplify the sound waves. Along the circumference of the resonant tube 120, the regenerator 140, cold-end heat exchanger 130, and hot-end heat exchanger 150 are sequentially arranged within the resonant tube 120. The regenerator 140, located within the acoustic field of the resonant tube 120, is the core component for thermoacoustic energy conversion. Under the excitation of sound waves, the working gas is periodically compressed and expanded within the porous structure of the regenerator 140, efficiently exchanging heat with the surface of the porous solid skeleton, thereby forming a temperature gradient within the regenerator 140, creating the hot and cold ends of the regenerator 140. The cold-end heat exchanger 130 is connected to the cold-end side of the regenerator 140 and is used to exchange heat with the refrigerator compartment to achieve a cooling effect on the compartment. The hot-end heat exchanger 150 is connected to the hot end of the regenerator 140 and is used to release heat to the external environment of the refrigerator.

[0028] The controller 200 is electrically connected to the thermoacoustic heat pump system 100 and is used to adjust the operating parameters of the thermoacoustic heat pump system 100 according to the refrigerator's operating parameter information. The operating parameter information includes at least one of the following: cabinet temperature, ambient temperature, hot end temperature, number of door openings, and operating time. The operating parameters include at least one of the following: operating pressure, resonant frequency of the thermoacoustic driver 110, and output power. The controller 200 is electrically connected to temperature sensors installed in each compartment of the cabinet, an ambient temperature sensor installed outside the cabinet, a hot end temperature sensor installed on the hot end heat exchanger 150, and a door open / close sensor used to detect the number of door openings, etc., to collect the refrigerator's operating status information in real time.

[0029] The thermoacoustic heat pump refrigerator 10 provided in this application embodiment dynamically adjusts the operating parameters of the thermoacoustic heat pump system 100 according to the actual operating status of the refrigerator, so that the system can maintain a high-efficiency operating state under different operating conditions. Compared with the fixed parameter operating mode, it can save 20% to 30% of energy and improve the temperature control accuracy.

[0030] Preferably, the thermoacoustic actuator 110 is a standing wave thermoacoustic compressor, which includes a cylinder, a piston, and a linear motor. The linear motor drives the piston to reciprocate within the cylinder, generating high-power, low-frequency longitudinal sound waves. The linear motor can be a moving-coil or moving-magnet type, or it can be a piezoelectric ceramic actuator. The piston material can be aluminum alloy or engineering plastic, and the inner wall of the cylinder is precision ground to ensure good sealing and low friction loss.

[0031] The resonant tube 120 can be made of stainless steel, copper, aluminum alloy, titanium alloy, or carbon fiber composite, with a smooth inner wall to reduce viscous losses during sound wave propagation. Preferably, the resonant tube 120 is a quarter-wavelength resonator. One end of the quarter-wavelength resonator is closed, and the other end is open or connected to subsequent components. This standing wave distribution is beneficial for establishing a stable temperature gradient in the regenerator 140 region. The length of the resonant tube 120 can be 0.8m to 1.0m. The resonant tube 120 can also be a ring resonant tube.

[0032] The cold-end heat exchanger 130 and the hot-end heat exchanger 150 can adopt finned tube, plate, or microchannel heat exchange structures, and the preferred material is copper or aluminum alloy with good thermal conductivity. The heat exchange area of ​​the cold-end heat exchanger 130 is designed according to the cooling capacity requirements of the refrigerator.

[0033] For preferred options, please refer to [link / reference]. Figures 3-4 , Figure 3 This is a schematic diagram of the structure of the regenerator provided in the embodiment of this application. Figure 4 for Figure 3 The diagram shows a cross-sectional view of the regenerator 140. The regenerator 140 comprises multiple layers of perforated plates stacked sequentially. The multiple layers of perforated plates are arranged along the axial direction of the regenerator 140, and the pore diameter and porosity of the through holes on each layer of the perforated plate change in a gradient along this direction. Specifically, from the cold end to the hot end of the regenerator 140, the pore diameter of the through holes on the perforated plates gradually increases, and / or, from the cold end to the hot end of the regenerator 140, the porosity of the through holes on the perforated plates gradually increases.

[0034] It should be noted that when the regenerator 140 is working, there is a significant temperature gradient along the axial direction from the cold end to the hot end inside. The working gas in different temperature regions has different thermophysical properties: the gas density is higher and the dynamic viscosity is lower in the cold end region, while the gas density is lower and the dynamic viscosity is higher in the hot end region.

[0035] In the cold end region, the use of a porous plate structure with smaller pore size and lower porosity has the following technical effects: First, the small pore size channel helps to thin the thermal boundary layer of the working gas, improves the convective heat transfer coefficient, and enhances the heat transfer effect in the cold end region; second, the lower porosity increases the volume ratio of the solid skeleton, enhances the axial heat conduction capacity, and helps to maintain the temperature gradient within the regenerator 140, preventing heat from flowing back from the hot end to the cold end; third, the gas density in the cold end region is relatively high, and although the smaller pore size channel increases the flow resistance to a certain extent, the high gas density and strong inertial force still ensure sufficient thermo-acoustic energy conversion.

[0036] In the hot-end region, the use of a porous plate structure with larger pore size and higher porosity has the following technical effects: First, the large-diameter channels significantly reduce gas flow resistance, allowing the working gas with lower density to pass through smoothly and reducing viscous dissipation losses; second, the higher porosity provides more effective flow area, increasing volumetric flow rate and heat transfer power density, compensating for insufficient heat transfer capacity caused by the lower gas density at the hot end; third, under the hot-end temperature conditions, the larger pore size is matched with the smaller heat penetration depth, still maintaining good thermoacoustic heat transfer effect.

[0037] Thus, through gradient matching design along the temperature direction, each section of the regenerator 140 can approach the optimal thermoacoustic heat transfer state. Compared with the uniform structure regenerator 140, the gradient regenerator 140 can improve the thermoacoustic conversion efficiency by 15% to 25% and the cooling COP by 10% to 20%.

[0038] In some embodiments, the regenerator 140 includes a first plate 141, a second plate 142, and a third plate 143 stacked sequentially from the cold end to the hot end. The first plate 141 has through holes with a diameter of 0.35 mm and a porosity of 65%, the second plate 142 has through holes with a diameter of 0.4 mm and a porosity of 68%, and the third plate 143 has through holes with a diameter of 0.5 mm and a porosity of 70%. Thus, the pore diameter of the three porous plates gradually changes from 0.35 mm to 0.4 mm and to 0.5 mm, and the porosity gradually changes from 65% to 68% and to 70%, forming a smooth gradient transition. The difference in pore diameter between each plate layer is 0.05 mm, and the difference in porosity is 2% to 3%. This gradual change avoids eddies and sound energy scattering losses caused by abrupt changes in the interlayer flow channels.

[0039] The material for the perforated plate can be selected from stainless steel, titanium alloy, copper alloy, or high-temperature resistant polymer. The thickness of the perforated plate is 0.05mm to 0.2mm, preferably 0.08mm to 0.15mm. The through holes can be round, elliptical, or polygonal, preferably round. Multiple layers of perforated plates can be positioned using precision locating pins and fixed together using diffusion welding or brazing.

[0040] It should be noted that the above three-layer structure is a preferred embodiment. In other embodiments, the number of layers in the multi-layer perforated plate can also be four, five, or more, as long as the gradient change trend from the cold end to the hot end is met, similar technical effects can be achieved. Increasing the number of layers can make the gradient transition smoother and further optimize the thermoacoustic matching performance. In addition, the specific values ​​of pore size and porosity can be optimized and adjusted according to the actual operating temperature range, the type of working gas, and the operating frequency. For example, when the operating frequency is high, the thermal penetration depth is small, and the pore size of each layer can be reduced proportionally; when using different working gases, the optimal pore size gradient can be recalculated based on the thermophysical properties of the gas.

[0041] The working gas in the thermoacoustic heat pump system 100 is preferably pure argon. The purity of the pure argon is preferably above 99.99% to avoid the adverse effects of impurities on the acoustic field characteristics and heat transfer performance. As a monatomic gas, argon has a specific heat ratio γ = 5 / 3 ≈ 1.67 and a Prandtl number Pr ≈ 0.67, close to the optimal value of the thermoacoustic regenerator 140, exhibiting good thermal penetration depth matching characteristics. At standard atmospheric pressure and 300K temperature, the speed of sound in argon is approximately 323 m / s, significantly lower than the speed of sound in helium. Therefore, at the same operating frequency, the length of the resonant tube 120 using pure argon as the working gas can be shortened by approximately 60%–70%, greatly benefiting the compact design of the system. The operating pressure range of the system is preferably 1.2 MPa–1.8 MPa, more preferably 1.2 MPa–1.4 MPa. Within this pressure range, the density of the working gas is moderate, ensuring sufficient heat transfer capacity while controlling the system's pressure resistance requirements at a reasonable level. In other embodiments, the working gas in the thermoacoustic heat pump system 100 may also be helium as the working gas, a mixture of argon and nitrogen as the working gas, or neon as the working gas.

[0042] In a specific embodiment, a 400L thermoacoustic heat pump refrigerator 10 uses pure argon as the working fluid, a 0.9m resonant tube 120, and a gradient porosity regenerator 140. Under standard operating conditions, its charging pressure is 1.3MPa, its resonant frequency is 80Hz, its steady-state power consumption is 80W, its operating noise is less than or equal to 32dB, and its COP can reach 2.1. A small 200L thermoacoustic heat pump refrigerator 10 uses pure argon as the working fluid, a 0.8m resonant tube 120, and a gradient porosity regenerator 140. Under standard operating conditions, its charging pressure is 1.15~1.25MPa, its resonant frequency is 72~78Hz, its steady-state power consumption is 55W, its operating noise is less than or equal to 30dB, and its COP can reach 2.1. A large thermoacoustic heat pump refrigerator 10 with a volume of 600L uses pure argon gas as the working fluid, a 1m resonant tube 120 and a gradient porosity regenerator 140. Under standard operating conditions, its charging pressure is 1.3~1.5MPa, the resonant frequency is 82~88HZ, the steady-state power consumption is 95W, the operating noise is less than or equal to 33dB, and the COP can reach 2.3.

[0043] Optionally, the thermoacoustic heat pump refrigerator 10 also includes a heat dissipation module (not shown in the figure). The heat dissipation module can use a fan to force-cool the heat exchanger at the hot end to dissipate heat to the outside of the cabinet and ensure stable operation of the system.

[0044] In some embodiments, the thermoacoustic heat pump system 100 further includes a time-sharing switching channel (not shown in the figure), which includes multiple parallel branches. One end of each branch is connected to the cold-end heat exchanger 130, and the other end is connected to the heat exchange mechanism of the corresponding compartment. Each branch is equipped with an acoustic impedance adjustment unit to adjust the acoustic impedance of the corresponding branch, thereby controlling the distribution ratio of the acoustic power output by the cold-end heat exchanger 130 among the branches, and realizing the directional delivery of cooling capacity to different compartments. The controller 200 is used to control each acoustic impedance adjustment unit to adjust the acoustic impedance of the corresponding branch in a time sequence, so that the cooling capacity generated by the cold-end heat exchanger 130 is delivered to multiple compartments in turn. In each cooling cycle, the system first determines the target compartment that needs cooling, and then adjusts the acoustic impedance adjustment unit corresponding to the target compartment to make the corresponding branch in an acoustic impedance matching state, while setting the other branches in an acoustic impedance mismatch state, thereby realizing the directional distribution of cooling capacity.

[0045] Specifically, the controller 200 is electrically connected to each acoustic impedance adjustment unit and is used to control the operating state of each acoustic impedance adjustment unit in a time sequence. Thus, by adjusting the operating state of the acoustic impedance adjustment units on each branch, the acoustic impedance of each branch can be changed, thereby adjusting the distribution ratio of the acoustic power output from the cold-end heat exchanger 130 among the multiple branches. When the acoustic impedance of a branch is adjusted by the acoustic impedance adjustment unit to match the main acoustic path, the acoustic power is mainly distributed to that branch, and the corresponding room receives sufficient cooling output, operating in an effective cooling state. When the acoustic impedance of a branch is adjusted to a state of severe mismatch with the main acoustic path, very little acoustic power enters that branch, and the corresponding room receives almost no cooling, operating in a state of stopped or minimal cooling.

[0046] The acoustic impedance adjustment unit can be implemented in at least one of the following ways: A movable acoustic reflector allows adjustment of the equivalent acoustic impedance of the corresponding branch by changing the position of the reflector. The variable cross-section acoustic impedance transformation section achieves acoustic impedance matching or mismatch by changing the channel cross-sectional area; A side resonant cavity utilizes the acoustic resonance characteristics of the side cavity to generate a specific acoustic impedance effect in the branch circuit.

[0047] Compared to traditional mechanical valve switching methods, the time-sharing switching channel in this embodiment has the following advantages: the acoustic impedance adjustment unit has no macroscopic mechanical moving parts, does not generate valve action noise, and the system noise can be reduced by 15dB to 20dB; there are no valve wear and aging problems, and the service life can be increased by more than 3 times; the switching process does not generate transient sound field disturbances, the sound field stability is good, which is conducive to maintaining the efficient operation of the thermoacoustic system; through continuous adjustment of the sound power distribution ratio, the cooling capacity can be finely distributed, and the temperature control accuracy is higher.

[0048] The thermoacoustic heat pump refrigerator 10 provided in this application embodiment dynamically adjusts the operating parameters of the thermoacoustic heat pump system 100 according to the actual operating status of the refrigerator, so that the system can maintain a high-efficiency operating state under different operating conditions. Compared with the fixed parameter operating mode, it can save 20% to 30% of energy and improve the temperature control accuracy.

[0049] This application also provides a control method applied to the aforementioned thermoacoustic heat pump refrigerator 10. This control method can be executed by its controller. For an example, please refer to [link to example]. Figure 5 , Figure 5 A flowchart of a control method provided in an embodiment of this application is included. The control method includes the following steps S101-S102: Step S101: Obtain the operating parameter information of the thermoacoustic heat pump refrigerator; The operating parameters include at least one of the following: cabinet temperature, ambient temperature, hot-end temperature, number of door openings, and operating time. The hot-end temperature can be the temperature of the hot-end heat exchanger or the hot-end temperature of the regenerator. The number of door openings indicates the number of times the thermoacoustic heat pump refrigerator is opened during the current cooling cycle. The operating time indicates the operating duration of the thermoacoustic heat pump refrigerator during the current cooling cycle.

[0050] The enclosure temperature can be monitored in real time by temperature sensors installed in each compartment. These sensors can be NTC thermistors, PT100 platinum resistance thermometers, or thermocouples. Ambient temperature can be monitored by temperature sensors located externally to the enclosure, or by obtaining local weather data through a user terminal such as a mobile app. The hot-end temperature can be monitored by a temperature sensor installed on the hot-end heat exchanger. The number of door openings can be cumulatively monitored by door switch sensors on the door, such as Hall effect sensors or microswitches. Running time can be recorded by a timer inside the controller.

[0051] Operating parameters can be collected in real time or periodically monitored at preset intervals, such as every 5 to 30 seconds. Furthermore, historical data can be used to predict temperature trends over a future period, providing a forward-looking basis for control decisions.

[0052] Step S102: Adjust the operating parameters of the thermoacoustic heat pump system according to the operating parameter information; The operating parameters include at least one of the operating pressure, the resonant frequency of the thermoacoustic driver, and the output power.

[0053] The working pressure can be adjusted by controlling the pressure regulating valve installed on the working gas pipeline to change the charging pressure of the working gas in the system. Increasing the working pressure increases the gas density and enhances the heat exchange effect, making it suitable for high cooling demand conditions; decreasing the working pressure reduces the gas density and lowers power consumption, making it suitable for low cooling demand conditions. The preferred adjustment range for the working pressure is 1.2 MPa to 1.8 MPa, and more preferably 1.2 MPa to 1.4 MPa.

[0054] The resonant frequency can be adjusted by changing the driving signal frequency of the thermoacoustic actuator, thereby altering the acoustic field resonance state of the system. Adjusting the resonant frequency changes the distribution of the nodes and antinodes of the standing wave, affecting the temperature gradient distribution and acoustic energy utilization within the regenerator. When the ambient temperature is high or the heat load is large, the resonant frequency can be appropriately increased to enhance cooling power; conversely, when the ambient temperature is low or the heat load is small, the resonant frequency can be appropriately decreased to reduce power consumption. The preferred adjustment range for the resonant frequency is 70Hz to 90Hz.

[0055] The output power can be adjusted by changing the piston stroke amplitude by adjusting the driving voltage or driving current of the thermoacoustic driver, thereby adjusting the sound pressure level and cooling capacity of the sound field. The preferred adjustment range for the output power is 60W to 100W. The output power can be continuously adjusted within a wide range, achieving precise control of the cooling capacity.

[0056] The above three operating parameters can be adjusted individually or in combination. When adjusting multiple parameters together, a weighted optimization algorithm can be used to determine the optimal adjustment amount of each parameter based on the weight of each parameter's influence on the cooling effect and the control sensitivity. For example, with maximizing the cooling COP as the objective function and minimizing the temperature deviation of each compartment as the constraint, the optimal value of each operating parameter can be solved using optimization methods such as gradient descent or genetic algorithms.

[0057] The control method for a thermoacoustic heat pump refrigerator provided in this application dynamically adjusts the operating parameters of the thermoacoustic heat pump system according to the actual operating status of the refrigerator, so that the system can maintain a high-efficiency operating state under different operating conditions. Compared with the fixed parameter operating mode, it can save 20% to 30% of energy and improve the temperature control accuracy.

[0058] This embodiment takes the temperature feedback control of a single compartment as an example. The specific execution flow of the control method includes: The current temperature and target temperature of the target room are acquired in real time, and the temperature deviation ΔT is calculated. If the temperature deviation is greater than the preset temperature, it is determined that the chamber is in a high temperature state. Then, the working pressure is increased to the first pressure value, such as 1.4MPa, the output power of the thermoacoustic driver is increased to the first power value, such as 100W, and the resonant frequency is adjusted to the first frequency value, such as 90Hz. If the temperature deviation is less than or equal to the preset temperature and greater than 0, it is determined that the room temperature is close to the target temperature. Then, the working pressure is controlled to be maintained at the second pressure value, such as 1.3MPa, the output power is controlled to be reduced to the second power value, such as 80W, and the resonant frequency is controlled to be maintained at the second frequency value, such as 80Hz.

[0059] If the temperature deviation is less than or equal to 0, it is determined that the chamber has reached the target temperature. The working pressure is reduced to the third pressure value, such as 1.2MPa, the output power is reduced to the third power value, such as 60W, and the resonant frequency is reduced to the third frequency value, such as 70Hz, in order to maintain the chamber temperature with minimal power consumption.

[0060] In some embodiments, the refrigerator body is provided with multiple compartments, and the thermoacoustic heat pump system further includes a cold-end heat exchanger, which is connected to each compartment. The control method further includes: sequentially delivering the cooling capacity generated by the cold-end heat exchanger to the multiple compartments according to a preset time sequence. For example, the refrigerator body is provided with a refrigerator compartment, a freezer compartment, and a deep-freeze compartment. The thermoacoustic heat pump refrigerator sequentially delivers the cooling capacity generated by the cold-end heat exchanger to the refrigerator compartment, freezer compartment, and deep-freeze compartment according to a preset time sequence. This enables independent temperature control for multiple temperature zones.

[0061] In some embodiments, the thermoacoustic heat pump system further includes a time-switching flow channel. The hot-end heat exchanger includes multiple parallel branches, one end of each branch is connected to the cold-end heat exchanger, and the other end is connected to the heat exchange mechanism of the corresponding compartment. Each branch is provided with an acoustic impedance adjustment unit, which is used to adjust the acoustic impedance of the corresponding branch to adjust the distribution ratio of the acoustic power output by the cold-end heat exchanger among the multiple branches. The step of sequentially delivering the cooling capacity generated by the cold-end heat exchanger to the multiple compartments according to a preset time sequence includes: controlling each acoustic impedance adjustment unit to adjust the acoustic impedance of the corresponding branch according to the time sequence so that the cooling capacity generated by the cold-end heat exchanger is sequentially delivered to the multiple compartments.

[0062] For example, the control method includes: In the first timing phase, the acoustic impedance adjustment unit on the corresponding branch of the refrigerator compartment is controlled to match the acoustic impedance of the refrigerator compartment branch with that of the main acoustic path. The cooling capacity generated by the cold-end heat exchanger is then directionally delivered to the refrigerator compartment through a time-sharing switching flow channel. Simultaneously, the branches corresponding to the freezer and deep-freeze compartments are set to an acoustic impedance mismatch state. During this process, the refrigerator compartment temperature is monitored in real time. When the refrigerator compartment temperature reaches the target range, such as 2℃~8℃, the refrigerator compartment cooling phase ends.

[0063] In the second timing phase, the operating mode of the acoustic impedance adjustment unit is switched to match the acoustic impedance of the freezer compartment branch with that of the main acoustic path, and the cooling capacity generated by the cold-end heat exchanger is directionally delivered to the freezer compartment. Simultaneously, the branches corresponding to the refrigerator compartment and the deep-freeze compartment are set to an acoustic impedance mismatch state. During this process, the freezer compartment temperature is monitored in real time, and the freezer compartment cooling phase ends when the freezer compartment temperature reaches the target range, such as -18℃ to -24℃.

[0064] In the third phase, the acoustic impedance adjustment unit is switched again to match the acoustic impedance of the cryogenic chamber branch with the main acoustic path, and the cooling capacity generated by the cold-end heat exchanger is directionally delivered to the cryogenic chamber. Simultaneously, the branches corresponding to the refrigerator and freezer compartments are set to an acoustic impedance mismatch state. During this process, the cryogenic chamber temperature is monitored in real time. When the cryogenic chamber temperature reaches the target range, such as -38℃ to 40℃, the cryogenic chamber cooling phase ends.

[0065] The cooling sequence of each of the above-mentioned compartments can be executed cyclically. A complete cooling cycle can last from 30 minutes to 120 minutes, with the cooling time of each compartment dynamically allocated according to the actual heat load. For example, the cooling time of the refrigerator compartment accounts for 40% to 50% of a cycle, the cooling time of the freezer compartment accounts for 20% to 30%, and the cooling time of the deep-freeze compartment accounts for 20% to 30%.

[0066] It should be noted that the cooling sequence of each room in the above-described sequential cooling process is not fixed, but can be dynamically adjusted according to actual needs. For example, during periods when users frequently open the refrigerator door, the cooling frequency and duration of the refrigerator can be appropriately increased; during low-load periods at night, the cooling interval between each room can be extended to reduce system operating power and achieve quiet and energy-saving operation.

[0067] The control method for a thermoacoustic heat pump refrigerator provided in this application dynamically adjusts the operating parameters of the thermoacoustic heat pump system according to the actual operating status of the refrigerator, so that the system can maintain a high-efficiency operating state under different operating conditions. Compared with the fixed parameter operating mode, it can save 20% to 30% of energy and improve the temperature control accuracy.

[0068] This application also provides a storage medium storing a computer program that executes the control method described above when running. Integrated modules / units, if implemented as software functional units and sold or used as independent products, can be stored in a computer-readable storage medium. Based on this understanding, all or part of the processes in the methods of the above embodiments can also be implemented by a computer program instructing related hardware. The computer program can be stored in a computer-readable storage medium, and when executed by a processor, it can implement the steps of the various control method embodiments described above.

[0069] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0070] The antenna device provided in the embodiments of this application has been described in detail above. Specific examples have been used to illustrate the principles and implementation methods of this application. The description of the above embodiments is only for the purpose of helping to understand the technical solutions and core ideas of this application. Those skilled in the art should understand that they can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. These modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application.

Claims

1. A control method, characterized in that, An application is made in a thermoacoustic heat pump refrigerator, the refrigerator comprising a cabinet and a thermoacoustic heat pump system disposed within the cabinet, the thermoacoustic heat pump system comprising a thermoacoustic driver, and the control method comprising: Obtain the operating parameter information of the thermoacoustic heat pump refrigerator, the operating parameter information including at least one of the following: cabinet temperature, ambient temperature, hot end temperature, number of times the door is opened, and running time; The operating parameters of the thermoacoustic heat pump system are adjusted according to the operating parameter information. The operating parameters include at least one of the operating pressure, the resonant frequency of the thermoacoustic driver, and the output power.

2. The control method according to claim 1, characterized in that, The housing is provided with multiple compartments, and the thermoacoustic heat pump system also includes a cold-end heat exchanger, which is connected to each of the compartments respectively; the control method further includes: delivering the cooling capacity generated by the cold-end heat exchanger to the multiple compartments in turn according to a preset time sequence.

3. The control method according to claim 2, characterized in that, The thermoacoustic heat pump system further includes a time-switching flow channel, which includes multiple parallel branches. One end of each branch is connected to the cold-end heat exchanger, and the other end is connected to the heat exchange mechanism of the corresponding compartment. Each branch is equipped with an acoustic impedance adjustment unit, which is used to adjust the acoustic impedance of the corresponding branch to adjust the distribution ratio of the acoustic power output by the cold-end heat exchanger among the multiple branches. The step of sequentially delivering the cooling capacity generated by the cold-end heat exchanger to the multiple compartments according to a preset time sequence includes: Each acoustic impedance adjustment unit is controlled to adjust the acoustic impedance of the corresponding branch in a time sequence so that the cooling capacity generated by the cold end heat exchanger is delivered to the multiple compartments in turn.

4. A thermoacoustic heat pump refrigerator, characterized in that, include: Box; A thermoacoustic heat pump system, installed in the enclosure, includes a thermoacoustic driver; A controller, connected to the thermoacoustic heat pump system, is used to adjust the operating parameters of the thermoacoustic heat pump system according to the operating parameter information of the refrigerator; the operating parameter information includes at least one of the following: cabinet temperature, ambient temperature, hot end temperature, number of door openings, and running time; the operating parameters include at least one of the following: operating pressure, resonant frequency of the thermoacoustic driver, and output power.

5. The thermoacoustic heat pump refrigerator according to claim 4, characterized in that, The thermoacoustic heat pump system further includes a regenerator, which comprises multiple layers of perforated plates stacked sequentially; from the cold end to the hot end of the regenerator, the diameter of the through holes on the perforated plates gradually increases; and / or From the cold end to the hot end of the regenerator, the porosity of the through holes on the porous plate gradually increases.

6. The thermoacoustic heat pump refrigerator according to claim 5, characterized in that, The regenerator includes a first plate, a second plate, and a third plate stacked sequentially from the cold end to the hot end; The diameter of the through hole on the first plate is 0.35 mm and the porosity is 65%, the diameter of the through hole on the second plate is 0.4 mm and the porosity is 68%, and the diameter of the through hole on the third plate is 0.5 mm and the porosity is 70%.

7. The thermoacoustic heat pump refrigerator according to any one of claims 4-6, characterized in that, The working gas in the thermoacoustic heat pump system is pure argon.

8. The thermoacoustic heat pump refrigerator according to any one of claims 4-6, characterized in that, The thermoacoustic actuator is a standing wave thermoacoustic compressor.

9. The thermoacoustic heat pump refrigerator according to any one of claims 4-6, characterized in that, The thermoacoustic heat pump system also includes a resonant tube, which is a 1 / 4 wavelength resonator.

10. A storage medium, characterized in that, It stores a computer program, and the computer executes the control method as described in any one of claims 1-3 when it is running.

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