Low-power long-keeping refrigeration method and system for refrigeration system

Abstract

The application relates to a low-power-consumption long-temperature-maintenance refrigeration method and system of a refrigeration system, and relates to the field of intelligent control, which comprises the following steps: matching a working mode based on a power supply state; when the working mode is a chargeable mode, calling a user arrival place based on vehicle navigation information, and matching an expected engine-off duration based on the user arrival place and user historical parking information; generating a forward-looking cold charging instruction according to the expected engine-off duration, the temperature in the box and the temperature of a cold storage material unit, so as to control the refrigeration assembly to run before the vehicle is turned off, and improve the cold storage of the cold storage material unit; when the working mode is switched to a non-chargeable mode, the refrigeration assembly is prohibited from running, and the required released cold is determined according to the temperature in the box; the required released cold is used to determine the number of window openings, and a corresponding number of release windows are opened. The application has the effect that the vehicle-mounted refrigerator can realize long-time stable maintenance of temperature in a low zero-power-consumption mode when the battery is powered.

Description

Technical Field

[0001] This invention relates to the field of intelligent control, and in particular to a low-power, long-lasting heat preservation cooling method and system for a refrigeration system. Background Technology

[0002] Low-power, long-term heat preservation cooling refers to a technical means that, in specific scenarios where a system switches from a high-power power source (such as mains power or a vehicle alternator) to a limited-capacity battery (such as a vehicle battery), intelligent energy management is used to maintain the temperature of the cooled space within a set range for a long time while strictly limiting power consumption.

[0003] Currently, in the typical application scenario of in-vehicle refrigerators, most commonly used in-vehicle refrigerators employ semiconductor refrigeration or compressor refrigeration technology. While the vehicle is in motion, the refrigerator can be stably powered and operate normally by the vehicle's alternator. However, when the vehicle is turned off, the refrigerator needs to be powered by the car's battery.

[0004] For existing vehicle refrigerators, their cooling control methods usually rely solely on simple feedback of the internal temperature to start and stop the compressor, which makes it impossible to maintain a stable temperature for a long time with low power consumption when powered by a battery, and this needs to be improved. Summary of the Invention

[0005] In order to enable vehicle refrigerators to maintain stable temperature for a long time with low power consumption when powered by battery, the present invention provides a low power consumption long-term heat preservation refrigeration method and system.

[0006] In a first aspect, the present invention provides a low-power, long-heat-insulation refrigeration method for a refrigeration system, which adopts the following technical solution: A low-power, long-term heat preservation cooling method for a refrigeration system includes: Collect data on the power supply status, internal temperature, and temperature of the cold storage material unit of the vehicle-mounted refrigerator; The corresponding working mode is matched based on the power supply status. When the matched working mode is rechargeable mode, vehicle navigation information and user historical parking information are collected, and the user's arrival location is retrieved based on the vehicle navigation information. The estimated engine shutdown time is matched based on the user's arrival location and user historical parking information. Based on the expected shutdown time, the internal temperature of the chamber, and the temperature of the cold storage material unit, a forward-looking charging command for the cold storage material unit is generated. In response to a forward-looking charge command, the operation of the refrigeration components is controlled before the vehicle is turned off to increase the cold storage capacity of the cold storage material unit. When the working mode is switched to non-rechargeable mode, the cooling components are prohibited from operating, and the required cooling capacity is determined based on the internal temperature of the chamber. The number of windows to be opened is determined based on the demand for cold energy release, and the opening of the corresponding number of release windows is controlled to adjust the cold energy release rate and maintain the temperature inside the chamber.

[0007] By adopting the above technical solution, when the vehicle is powered while driving, the system stores sufficient cold energy in advance for the passive cold storage system based on the prediction of the user's parking time. When the vehicle is turned off and switched to battery power, the system actively shuts down the high-energy-consuming refrigeration components and instead maintains the temperature inside the refrigerator by precisely controlling the cold release rate of the passive cold storage system. This significantly reduces the energy consumption of the vehicle refrigerator during battery power from both the perspectives of increasing energy supply and reducing energy consumption, thereby enabling the vehicle refrigerator to maintain a stable temperature for a long time with low to zero power consumption when powered by the battery.

[0008] Optionally, a method for adjusting the number of open windows may also be included: The rate of temperature change inside the acquisition chamber and the historical average temperature of the cold storage material unit were collected. Compare the rate of temperature change with a rate of change threshold, and compare the material’s historical average temperature with an average temperature threshold. When the rate of temperature change exceeds the rate of change threshold, it is determined that the temperature is rising rapidly, and a compensation instruction to increase the number of release windows is generated. When the historical average temperature of the material is lower than the average temperature threshold, it is determined that the overall cold storage material has sufficient cold capacity reserves, and a restriction instruction to reduce the number of release windows is generated. The number of basic windows to be opened is calculated based on the demand for releasing cooling capacity. Then, by combining compensation instructions and restriction instructions, the number of basic windows to be opened is dynamically added and reduced to obtain the final number of windows to be opened.

[0009] Optional, heat load handling methods are also included: The pressure change value of the storage support structure inside the collection box and the contact temperature of the items in direct contact with it were collected. When the pressure change value reaches the pressure characteristic threshold within the preset pressure detection time, it is preliminarily determined that an item has been placed. In response to the initial assessment, the contact temperature is compared with the temperature inside the chamber. When the contact temperature is consistently higher than the temperature inside the chamber and exceeds the contact temperature threshold, the placed item is determined to be a heat-loaded item. In response to the secondary determination, the rate and magnitude of pressure change values ​​are collected during the period when the pressure characteristic threshold is reached; Pressure characteristic factors are calculated based on the rate and magnitude of change. The temperature difference is calculated based on the difference between the contact temperature and the temperature inside the chamber. Based on the pressure characteristic factor and temperature difference, the quantitative thermal shock value of the heat load is obtained through weighted fusion calculation; The thermal load compensation strategy is determined based on the quantified thermal shock value and the operating mode, and the corresponding thermal load compensation strategy is executed.

[0010] Optionally, the heat load compensation strategy includes: If the current matched operating mode is rechargeable mode, the enhanced operating power increment and enhanced operating time of the cooling component are calculated based on the quantified thermal shock value. The location of the heat-loaded item to be placed is recorded; The target surface curvature of the deformable air duct required to deflect and guide the cold airflow is calculated based on the relative orientation of the placement area and the main air duct inside the box. The target inflation pressure value of each independent air chamber inside the deformable air bladder is determined based on the target surface curvature. The cooling components are controlled to enhance operating power and operating time. At the same time, based on the target inflation pressure value of each air chamber, the corresponding micro air pump is controlled to inflate the deformable guide airbag, causing it to deform into a shape with the target surface curvature, thereby guiding the cold airflow to the placement area.

[0011] Optionally, the heat load compensation strategy further includes: If the current matching working mode is non-rechargeable mode, the compensation value for the number of additional windows that need to be opened is calculated based on the quantified thermal shock value and the internal temperature of the chamber. Collect the zone temperature of each independent zone within the cold storage material unit, and sort them according to the zone temperature to obtain a temperature sorting list. The window number to be opened is determined based on the temperature sorting list and the window quantity compensation value. Control the opening of the heat insulation covers of all release windows corresponding to the window numbers to be opened, so as to promote heat exchange between the cold storage material unit and the air inside the box.

[0012] Optionally, a door-opening transient thermal management method may also be included: Collect the opening and closing status signal of the refrigerator door; When the open / closed status signal indicates that the door is open, the door opening amplitude, door opening speed, and ambient temperature value are collected. The dynamic thermal intrusion coefficient corresponding to the current door opening action is calculated based on the door opening range, door opening speed, and ambient temperature. The initial start-up wind speed and continuous operating wind pressure of the air curtain device are determined based on the dynamic thermal intrusion coefficient. The control air curtain device starts operating at the initial start-up wind speed and the continuous operating wind pressure, forming an active isolation air curtain inside the door frame.

[0013] Optional, also includes: The door opening heat load compensation value is obtained based on the dynamic heat intrusion coefficient; The total number of dynamically opened windows is determined by combining the door opening heat load compensation value with the number of windows opened. The control panel opens a corresponding number of release windows according to the total number of dynamic windows opened. When the open / closed status signal indicates that the door is closed, the closing aftereffect timer is started, and the total number of windows open is maintained dynamically based on the current door opening heat load compensation value during the timer period; When the after-effect timer ends after the door is closed, the door opening heat load compensation value is reset to zero, and the control logic is restored to determine the required cooling capacity and the number of windows to be opened based solely on the internal temperature of the box.

[0014] Optional methods include condensate recovery and heat dissipation enhancement: Collect the condenser temperature of the condenser; When the condenser temperature exceeds the preset high temperature alarm threshold and the ambient temperature exceeds the high temperature ambient threshold, the control water collection container will transport the collected evaporator condensate to the ultrasonic atomizing device. The ultrasonic atomizing device is activated to atomize the evaporator condensate into micron-sized water mist and spray it onto the surface of the condenser's heat dissipation fins, thereby updating the condenser temperature. The ultrasonic atomizing device will stop when the temperature of the updated condenser drops below the high-temperature alarm threshold.

[0015] Optional methods for storing cold energy include: Collect ambient temperature values ​​and the expected engine shutdown time setting value input by the user through the interactive interface; The estimated shutdown time setting value is compared with the estimated shutdown time, and the larger of the two values ​​is taken as the final estimated shutdown time. The target cold energy reserve value is calculated based on the final estimated shutdown time, the temperature inside the chamber, the temperature of the cold storage material unit, and the ambient temperature. The current cold storage reserve value is determined based on the temperature of the cold storage material unit; The required additional cooling capacity is calculated based on the current and target cooling capacity reserves. Generate forward-looking cooling charge instructions based on the required additional cooling capacity.

[0016] Secondly, this application provides a low-power, long-insulation refrigeration system, which adopts the following technical solution: A low-power, long-insulation refrigeration system, comprising: The data acquisition module is used to collect information such as power supply status, internal temperature, temperature of cold storage material unit, vehicle navigation information, and user's historical parking information. The memory is used to store the program that implements a low-power, long-heat-preservation refrigeration method for a refrigeration system; The processor is used to load and execute programs stored in memory.

[0017] In summary, this application includes at least one of the following beneficial technical effects: 1. When the vehicle is running and powered, sufficient cold energy is stored based on the prediction of the user's parking time; when the vehicle is turned off and switched to battery power, the temperature inside the refrigerator is maintained by controlling the cold energy release rate of the passive cold storage system, so that the vehicle refrigerator can achieve long-term stable temperature maintenance in a low-power and zero-power manner when powered by the battery. 2. When a user places a new high-temperature item, the system dynamically increases the output power and operating time of the cooling components to cope with the increased heat load. On the other hand, by precisely controlling the deformation of the deformable air-guiding bag, the system directly and centrally directs the cold airflow to the area where the item is located, thereby maintaining a uniform and stable temperature while avoiding a significant increase in energy consumption caused by enhanced cooling across the entire area. 3. By dynamically calculating the compensation value and adjusting the number of cold release windows, the cold release capacity of the passive cold storage system can be actively enhanced after the door is closed, thereby accelerating the offsetting of intruding heat and allowing the temperature inside the chamber to quickly return to stability. Attached Figure Description

[0018] Figure 1 This is a flowchart of a low-power, long-insulation refrigeration method for a refrigeration system. Figure 2 This is a schematic diagram of the internal structure of a car refrigerator.

[0019] The parts referred to by the numbers in the above attached diagrams are as follows: 1. Vehicle refrigerator; 2. Cold storage material unit; 3. Release window; 4. Deformable airbag; 5. Miniature air pump. Detailed Implementation

[0020] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments.

[0021] Reference Figure 1 and Figure 2 This application discloses a low-power, long-term heat preservation refrigeration method for a refrigeration system, comprising the following steps: S10: Collect the power supply status, internal temperature, and temperature of the cold storage material unit of the vehicle refrigerator 1.

[0022] The power supply status refers to the type and characteristics of the power source currently connected to the vehicle refrigerator 1. Specifically, it includes: High-power external power supply status: refers to the state when the vehicle engine is running (driving power generation), or when the refrigerator is connected to a stable high-power power source such as mains power or a large-capacity auxiliary battery.

[0023] Vehicle battery status: This refers to the state where, after the vehicle is turned off, the refrigerator is powered solely by the vehicle's main starter battery or auxiliary battery. In this state, the power output is limited and continuously consumed.

[0024] Extremely low battery state: This refers to the state where the voltage of the vehicle battery is lower than a preset safety threshold (such as 11.8V), and the vehicle must enter an extremely power-saving mode to protect its starting ability.

[0025] The power supply status can be obtained by detecting the voltage and current at the input terminals or by communicating with the vehicle bus (CAN).

[0026] The internal temperature refers to the air temperature value measured in real time by a temperature sensor installed in the inner liner of the refrigerator's storage compartment.

[0027] The unit temperature of a cold storage material (PCM) refers to the real-time temperature of the material measured by a temperature sensor embedded within the PCM. This temperature directly reflects the physical state (solid, liquid, or solid-liquid mixture) of the PCM and the level of its inherent "cold energy". When the temperature is close to or below its phase change point, it indicates that the cold energy reserve is sufficient; when the temperature is above the phase change point and continues to rise, it indicates that the cold energy is approaching depletion.

[0028] S11: Matching the corresponding working mode based on the power supply status.

[0029] A working mode refers to a set of preset operating strategies and control parameters invoked by the controller based on the power supply status. The core mode includes at least: Rechargeable mode: Matched with "High-power external power supply state". In this mode, the system prioritizes optimal performance, allowing the cooling components to operate at full power to rapidly cool down and efficiently "charge" the cold storage material unit 2.

[0030] Non-rechargeable mode: Matched with "on-board battery status" or "extremely low battery status". In this mode, the system prioritizes "maintaining range" and the core strategy is to strictly limit or prohibit the operation of high-power cooling components. It mainly relies on the cold storage material unit 2 to release the stored cold energy to maintain the box temperature and achieve long-term heat preservation.

[0031] The controller determines the current power supply status by monitoring the voltage of the power supply. A mapping table between power supply status and operating mode is pre-stored in the controller. When a high-power external power supply is detected, the controller matches and enters a rechargeable mode; when the onboard battery status or extremely low battery status is detected, the controller matches and enters a non-rechargeable mode. This mapping table is pre-recorded by those skilled in the art and will not be elaborated upon here.

[0032] S12: When the matched working mode is rechargeable mode, collect vehicle navigation information and user historical parking information, retrieve the user's arrival location based on the vehicle navigation information, and match the expected shutdown time based on the user's arrival location and user historical parking information.

[0033] Vehicle navigation information refers to trip planning data obtained from the vehicle's central control system or a vehicle-connected terminal (such as a mobile phone). It includes at least the destination, estimated arrival time, and remaining travel time.

[0034] User historical parking information refers to the set of historical parking duration data recorded and stored by the system for users in different locations. Its data structure is associated with at least two fields: "location identifier" and "historical parking duration". User historical parking information is retrieved from the system.

[0035] The user's destination refers to the location information of the trip's final destination, which is parsed from the vehicle navigation information. The specific parsing methods are common knowledge in this field and will not be elaborated here.

[0036] The estimated engine shutdown time refers to the duration from the next time the vehicle is turned off until it is expected to be restarted.

[0037] The estimated shutdown time is determined by matching the user's arrival location with the user's historical parking information to obtain historical parking duration data associated with that location. This historical parking duration is then used as the estimated shutdown time. The specific query methods for matching and obtaining the data are common knowledge in the field and will not be elaborated upon here.

[0038] If no historical parking duration data is found in the user's historical parking information when the user arrives at the location, the preset default parking duration is used as the estimated engine shutdown duration. The default parking duration can be set by those skilled in the art based on experience (e.g., 4 hours), or it can be pre-configured by the user in the system.

[0039] When the matched working mode is rechargeable mode, the vehicle navigation information and the user's historical parking information need to be collected first, and the estimated shutdown time is calculated based on the collected information for subsequent steps.

[0040] S13: Generate a forward-looking charging command for the cold storage material unit 2 based on the expected shutdown duration, the internal temperature of the chamber, and the temperature of the cold storage material unit.

[0041] A forward-looking charge command refers to a set of control parameters used to instruct the refrigeration components to operate during the remaining time before the vehicle is turned off. The specific method for determining the forward-looking charge command will be explained in detail in S90 to S95, and will not be repeated here.

[0042] S14: In response to the forward-looking charging command, control the operation of the refrigeration components before the vehicle is turned off to increase the cold storage material unit 2.

[0043] The refrigeration component refers to the core component system in the vehicle-mounted refrigerator 1 that enables active refrigeration. In this step, the controller precisely controls the start-up, shutdown, and power of the refrigeration component (mainly the compressor) according to the forward-looking charging command, transferring the heat inside the refrigerator and the cold storage material to the outside, thereby reducing the temperature of the cold storage material unit 2, causing more of the phase change material in it to solidify, and realizing the storage of cold energy.

[0044] S15: When the working mode is switched to non-rechargeable mode, the cooling components are prohibited from operating, and the required cooling capacity is determined based on the internal temperature.

[0045] The determination of the non-rechargeable mode is as described in S11. Once this mode is entered, the system first enforces a hard constraint to prohibit the operation of the cooling components, in order to eliminate the largest source of power consumption and ensure the safety of the vehicle battery. Demand-released cooling capacity refers to the amount of cooling capacity that needs to be released instantaneously from the cooling material unit 2 in order to maintain the internal temperature within the target temperature range set by the user.

[0046] The system compares the internal temperature with a preset target temperature setting, calculates the difference between the current temperature and the target temperature setting, and uses this temperature difference to query a preset temperature difference cooling capacity mapping table to determine the required cooling capacity. This temperature difference cooling capacity mapping table records the correspondence between different temperature difference ranges and the required cooling capacity values. This table is pre-set and stored in the controller by those skilled in the art based on the thermodynamic characteristics of the cold storage material unit 2, the chamber's heat load model, and temperature control accuracy requirements. Once the temperature difference value is obtained, the system queries this table to obtain the corresponding cooling capacity requirement value, i.e., the required cooling capacity to be released. The construction method and specific values ​​of the temperature difference cooling capacity mapping table are conventional techniques determined by those skilled in the art based on system parameters and will not be elaborated upon here.

[0047] When the operating mode is switched to non-rechargeable mode, the cooling components must be disabled, and the required cooling capacity must be determined based on the internal temperature of the chamber for subsequent steps.

[0048] S16: Determine the number of windows to open based on the demand for releasing cold energy, and control the opening of the corresponding number of release windows 3 to adjust the cold energy release rate and maintain the temperature inside the chamber.

[0049] The number of open windows refers to the number of independently electrically controlled heat insulation covers (i.e., "release windows 3") located on the surface of the cold storage material unit 2 enclosure that are commanded to open at the same time. The cold storage material unit 2 is divided into multiple independent partitions or modules, and each partition has multiple such release windows 3.

[0050] The number of windows to be opened is calculated based on the demand for cold release and a preset standard release capacity parameter for a single window. Specifically, the demand for cold release is divided by a preset baseline value representing the amount of cold release that a single release window 3 can release per unit time, resulting in an initial calculation. This initial calculation result is then rounded up to obtain an integer value, which is the number of windows to be opened. The standard release capacity parameter for a single window is determined in advance by those skilled in the art based on the thermal properties of the cold storage material and the heat exchange area of ​​the window. The method for determining this parameter is a conventional technique in the field and will not be elaborated here.

[0051] Once the number of open windows is obtained, the corresponding number of release windows 3 need to be opened to adjust the cold energy release rate and maintain the temperature inside the chamber.

[0052] It also includes methods for adjusting the number of open windows: S20: Collect the temperature change rate inside the chamber and the historical average temperature of the cold storage material unit 2.

[0053] The rate of temperature change refers to the amount of temperature change within the chamber per unit time, obtained by calculating the derivative of continuously collected chamber temperature data over a preset time interval. The historical average temperature of the material refers to the arithmetic mean of the temperatures of the cold storage material units over a preset statistical period in the past.

[0054] S21: Compare the rate of temperature change with the rate of change threshold, and compare the material's historical average temperature with the average temperature threshold.

[0055] The calculated rate of temperature change is compared with a preset rate of change threshold. This threshold is used to determine whether the temperature change in the chamber falls within the range requiring intervention. The specific value is set in advance by those skilled in the art and will not be elaborated here.

[0056] The calculated historical average temperature of the material is compared with a preset average temperature threshold. This threshold is set near the phase transition point of the cold storage material to determine whether its overall cold energy reserve is in a "sufficient" state. The specific value is set in advance by those skilled in the art and will not be elaborated here.

[0057] S22: When the rate of temperature change exceeds the rate of change threshold, it is determined that the temperature is rising rapidly, and a compensation instruction to increase the number of release windows is generated.

[0058] A compensation command is a control signal used to temporarily increase the number of release windows on top of the base control value. It contains a positive increment (such as "+1" or "+2"), indicating the additional number of windows that need to be added in subsequent calculations to cope with the rapid rise in chamber temperature and accelerate the release of cooling capacity.

[0059] The compensation command is calculated by multiplying the difference between the rate of temperature change and a threshold value by a preset proportional coefficient. This proportional coefficient is predetermined by those skilled in the art based on the system's temperature control response characteristics; its determination method is conventional and will not be elaborated upon here. The calculated value is rounded to obtain a positive increment. When the rate of temperature change exceeds the threshold value, it is determined that the temperature is rising rapidly, and a compensation command needs to be generated for subsequent steps.

[0060] S23: When the historical average temperature of the material is lower than the average temperature threshold, it is determined that the overall cold storage material has sufficient cold capacity reserves, and a restriction instruction to reduce the number of release windows is generated.

[0061] A limit instruction is a control signal used to temporarily limit or reduce the number of release windows based on a basic control variable. It contains a negative decrement (such as "-1"), indicating the number of windows to be reduced in subsequent calculations.

[0062] The limiting instruction is calculated by multiplying the difference between the average temperature threshold and the material's historical average temperature by a preset reduction ratio. This reduction ratio is predetermined by those skilled in the art based on the cold release characteristics of the cold storage material and the target insulation duration optimization requirements; its determination method is conventional in the field and will not be elaborated upon here. The calculated value, after being rounded, constitutes a negative reduction.

[0063] When the historical average temperature is low, it indicates that the cold storage material has been in a phase transition period with sufficient cold energy for most of the recent period. In order to extend the overall insulation duration, its cold energy release rate should be strategically slowed down. When the historical average temperature of the material is below the average temperature threshold, it indicates that the cold storage material has been in a phase transition period with sufficient cold energy for most of the recent period. In order to extend the overall insulation duration, its cold energy release rate should be strategically slowed down. Therefore, at this time, it should be determined that the overall cold energy reserve of the cold storage material is sufficient, and a limiting instruction should be generated for subsequent steps.

[0064] S24: Calculate the basic number of windows to be opened based on the demand for releasing cooling capacity, and dynamically add or reduce the basic number of windows to be opened by combining compensation instructions and restriction instructions to obtain the final number of windows to be opened.

[0065] The basic window opening quantity refers to the initial window opening quantity calculated without correction, based solely on the cooling capacity released according to the demand determined in S15, using the S16 method (such as dividing by the standard release capacity of a single window and rounding down).

[0066] By algebraically adding the calculated base number of open windows to the compensation and limitation instructions, a corrected intermediate value for the number of windows is obtained. This intermediate value is then compared and limited with the system's preset minimum and maximum allowed number of open windows: if the intermediate value is less than the minimum number of open windows, the final number of open windows is the minimum number; if the intermediate value is greater than the maximum number of open windows, the final number of open windows is the maximum number; if the intermediate value is between the two, it is directly rounded down to the nearest integer and used as the final number of open windows. The minimum and maximum number of open windows are determined by those skilled in the art based on the system design, and the determination method is a conventional technique in the field, which will not be elaborated here.

[0067] It also includes methods for dealing with heat load: S30: Collect the pressure change value of the storage support structure inside the box and the contact temperature of the items in direct contact with it.

[0068] The internal storage support structure refers to the components inside the refrigerator used to support stored items, such as the bottom of a drawer or the support surface of a movable shelf. In this design, this structure integrates a pressure sensor array and a contact temperature sensor.

[0069] The pressure change value refers to the change in total or local pressure on the support surface caused by the insertion or removal of an object, as measured by an array of pressure sensors. It is a continuously or periodically sampled signal used to detect whether an object has been placed inside.

[0070] Contact temperature refers to the temperature of the area in contact with the bottom of a newly placed item, measured directly by a temperature sensor integrated into the surface of the storage support structure.

[0071] S31: When the pressure change value reaches the pressure characteristic threshold within the preset pressure detection time, it is preliminarily determined that an item has been placed.

[0072] Pressure detection time refers to a short time window (e.g., 2 seconds) during which the system continuously monitors and judges the pressure from the moment it begins to change. It is used to distinguish between slow object movement and rapid placement, and to prevent false triggering.

[0073] The pressure characteristic threshold refers to a preset minimum pressure increment. Only when the pressure change exceeds this threshold within the pressure detection time is it considered a valid "item placement" event, rather than a minor disturbance or adjustment. The pressure characteristic threshold is preset by those skilled in the art and will not be elaborated upon here.

[0074] When the pressure change value reaches the pressure characteristic threshold within the pressure detection time, it is preliminarily determined that an item has been placed.

[0075] S32: In response to the initial determination, the contact temperature is compared with the temperature inside the chamber. When the contact temperature is consistently higher than the temperature inside the chamber and exceeds the contact temperature threshold, the placed item is determined to be a heat-loaded item.

[0076] The contact temperature threshold refers to a preset minimum temperature difference. It is used to determine whether the placed item is "hot" enough and requires special system handling. The contact temperature threshold is preset by those skilled in the art and will not be elaborated here.

[0077] Heat-loaded items are those placed inside the enclosure at a temperature significantly higher than the current internal temperature. Their placement introduces additional heat into the enclosure (i.e., a "heat load"), causing the enclosure temperature to rise rapidly and disrupting temperature stability.

[0078] When the contact temperature is consistently higher than the internal temperature, and the temperature difference between the two exceeds the contact temperature threshold, it is necessary to determine a second time that the placed item is a heat-loaded item for subsequent steps.

[0079] S33: In response to the secondary determination, the rate and magnitude of pressure change value during the period when the pressure characteristic threshold is reached are collected.

[0080] The rate of change refers to how quickly the pressure increases over time as it reaches a pressure characteristic threshold.

[0081] The rate of change is calculated by dividing the difference between the pressure from its initial value and the pressure characteristic threshold by the time taken for the pressure to increase.

[0082] The magnitude of change refers to the total amount of pressure change from the initial value to the final stable value (or peak value) within the pressure testing period. A larger magnitude usually indicates a larger total weight of the placed item.

[0083] The magnitude of change is obtained by calculating the absolute difference between the pressure sensor reading and the new stable value (or peak value) reached after the event, within the pressure detection time window. If the pressure drops slightly and stabilizes after reaching the peak, this stable value is usually used as the final value for calculation.

[0084] S34: Calculate the pressure characteristic factor based on the rate and magnitude of change.

[0085] The pressure characteristic factor is a numerical index used to comprehensively quantify the dynamic characteristics of implantation movements.

[0086] The formula can be obtained through calculation: Pressure characteristic factor = rate of change × amplitude of change.

[0087] S35: Calculate the temperature difference based on the difference between the contact temperature and the chamber temperature.

[0088] The temperature difference refers to the arithmetic difference between the contact temperature and the current temperature inside the box. This value directly reflects the initial temperature difference caused by the placed items.

[0089] S36: Based on the pressure characteristic factor and temperature difference, the quantitative thermal shock value of the heat load is obtained through weighted fusion calculation.

[0090] The quantified thermal shock value is a numerical value used to comprehensively and quantitatively assess the total impact intensity of this thermal load introduction event on the temperature system inside the chamber.

[0091] The quantified thermal shock value is calculated by weighting and summing the pressure characteristic factor and the temperature difference according to preset weighting coefficients. Specifically, the calculation formula is: Quantified thermal shock value = α × pressure characteristic factor + β × temperature difference, where α and β are preset weighting coefficients corresponding to the pressure characteristic factor and the temperature difference, respectively, and both α and β are positive numbers and dimensionless.

[0092] This weighted fusion calculation aims to integrate information from two dimensions—the pressure characteristic factor reflecting the dynamic impact of the insertion action and the temperature difference reflecting the initial thermal difference—into a single value characterizing the total thermal shock intensity. The specific values ​​of the weighting coefficients α and β are determined by those skilled in the art through system calibration experiments to balance the contribution of both to the final temperature rise. The method for determining these values ​​is a conventional technique in the field and will not be elaborated here.

[0093] S37: Determine the thermal load compensation strategy based on the quantified thermal shock value and operating mode, and execute the corresponding thermal load compensation strategy.

[0094] Heat load compensation strategy refers to the specific control action plan taken to offset the heat introduced by heat-loaded items, quickly restore and maintain the stable temperature inside the chamber.

[0095] The heat load compensation strategy is determined by querying a pre-defined heat load compensation strategy table. This table takes the quantified thermal shock value and operating mode as input conditions and outputs the corresponding heat load compensation strategy. The heat load compensation strategy table is prepared in advance by those skilled in the art based on the system thermodynamic model and experimental data, and will not be described in detail here.

[0096] The specific heat load compensation strategies will be explained in detail in subsequent sections S40 to S44 and S50 to S53, and will not be repeated here.

[0097] Thermal load compensation strategies include: S40: If the current matched operating mode is rechargeable mode, the enhanced operating power increment and enhanced operating time of the cooling component are calculated based on the quantified thermal shock value.

[0098] Enhanced operating power increment refers to the temporary increase in power required on top of the current operating power to enable the refrigeration components to output more cooling capacity to quickly offset the heat load. This increment is positively correlated with the quantified thermal shock value; the larger the shock value, the larger the increment.

[0099] The enhanced operating power increment is obtained by multiplying the quantified thermal shock value by a preset power ratio coefficient. This power ratio coefficient is preset by those skilled in the art based on the power regulation characteristics of the refrigeration components and the system's heat capacity; the method for determining this coefficient is a conventional technique in the field and will not be elaborated upon here.

[0100] Enhanced runtime refers to the length of time that the cooling components need to operate continuously at enhanced power. This duration is also positively correlated with the quantified thermal shock value to ensure sufficient time to deliver the required cooling capacity.

[0101] The enhanced runtime is obtained by multiplying the quantified thermal shock value by a preset time scaling factor. The time scaling factor is preset by those skilled in the art based on the system's thermal inertia and temperature control response speed requirements. The method for determining this factor is a conventional technique in the field and will not be elaborated here.

[0102] If the current matching working mode is rechargeable mode, the enhanced operating power increment and enhanced operating time need to be calculated first for subsequent steps.

[0103] S41: Collect the location of the placement area for the heat-loaded item.

[0104] The placement area location refers to the specific spatial coordinates of the heat-loaded items inside the refrigerator compartment.

[0105] By analyzing the triggering state and signal strength of each sensor in the pressure sensor array integrated on the storage support structure inside the box, the specific area where the pressure change occurs is determined, and this area is mapped to predefined spatial coordinates inside the box, thereby obtaining the placement area position.

[0106] S42: Calculate the target surface curvature of the deformable air bladder 4 required to deflect and guide the cold airflow based on the relative orientation of the placement area and the main air duct inside the box.

[0107] The main air duct inside the refrigerator refers to the main airflow channel located inside the refrigerator body, used to transport and distribute the cold air generated by the refrigeration components (evaporator side) to various areas inside the refrigerator.

[0108] The deformable airbag 4 is a flexible pneumatic device installed at the end of the air duct inside the box. It consists of multiple independent air chambers that can be inflated and deflated independently. By controlling the pressure of each air chamber, the airbag as a whole can undergo controllable deformation, thereby changing its surface shape to guide and redirect the cold airflow blown out of the air duct.

[0109] The target surface curvature refers to the mathematical description of the specific three-dimensional curved surface shape that the deformable air guide airbag 4 needs to deform to accurately guide the cold airflow from the main air duct outlet direction to the placement area.

[0110] By performing geometric analysis based on the spatial coordinates of the placement area and the spatial vector of the airflow direction of the main air duct inside the box, the ideal airflow deflection amount required to deflect the airflow from the main air duct outlet and point it toward the placement area is calculated.

[0111] Subsequently, based on the deformation capability model of the deformable airbag 4, the model describes the correspondence between the surface curvature of the airbag and the achievement of a specific airflow deflection angle, mapping the ideal airflow deflection magnitude to the curvature parameter that the airbag surface needs to achieve, i.e., the target surface curvature.

[0112] The specific geometric calculations, vector analysis, and model mapping methods are routine applications of fluid mechanics and mechanism kinematics in this field, and are technical means that can be implemented by those skilled in the art, so they will not be elaborated here.

[0113] S43: Determine the target inflation pressure value of each independent air chamber inside the deformable air bladder 4 based on the target surface curvature.

[0114] The target inflation pressure value refers to the gas pressure setting value that each independent air chamber needs to achieve in order to make the individual air chambers of the deformable air guiding airbag 4 deform in a coordinated manner, so that the entire airbag surface reaches the target surface curvature.

[0115] By inputting the target surface curvature into the preset airbag deformation control model, the target inflation pressure value corresponding to each independent air chamber inside the deformable airbag 4 is calculated.

[0116] This airbag deformation control model describes the mapping relationship between the overall surface morphology of the airbag (characterized by curvature parameters) and the internal pressure of each individual air chamber constituting its surface. This model was pre-established and stored in the controller by those skilled in the art based on the airbag's physical structure, material mechanical properties, and hydrodynamic characteristics, through theoretical modeling and experimental calibration.

[0117] Based on this model, the controller can calculate the precise pressure values ​​required to be applied to each air chamber to achieve a specific target surface curvature. The model construction and solution process is a conventional technique in this field for achieving precision aerodynamic shape control, and will not be elaborated here.

[0118] S44: Control the cooling components to enhance operating power and operating time, and at the same time, according to the target inflation pressure value of each air chamber, control the corresponding micro air pump 5 to inflate the deformable guide air bag 4, so that it is deformed into a shape with the target surface curvature, thereby guiding the cold airflow to the placement area position.

[0119] The cooling components are controlled to enhance the operating power and extend the operating time. At the same time, according to the target inflation pressure value of each air chamber, the corresponding micro air pump 5 is controlled to inflate the deformable guide air bag 4 until the pressure sensor readings in each air chamber reach their respective target inflation pressure values.

[0120] As the airbag deforms to the target shape, the enhanced cold airflow blown out from the air duct will be redirected and concentrated on the placement area where the heat-loaded items are located, achieving rapid and precise counter-heating of the area, thereby effectively suppressing the rise in chamber temperature and quickly restoring temperature stability.

[0121] Thermal load compensation strategies also include: S50: If the current matched working mode is non-rechargeable mode, the compensation value for the number of additional windows that need to be opened is calculated based on the quantified thermal shock value and the internal temperature of the chamber.

[0122] The window quantity compensation value refers to the number of release windows 3 that need to be temporarily added to the base number of windows opened in non-rechargeable mode in order to cope with thermal load shocks, in addition to the base number of windows opened based on the temperature inside the chamber.

[0123] The window quantity compensation value can be obtained by querying the preset compensation value mapping table.

[0124] This mapping table uses the quantized thermal shock value and the current chamber temperature as joint input conditions. Specifically, the quantized thermal shock value is divided into several intervals, and the chamber temperature is also divided into several intervals. The table records a specific window number compensation value corresponding to each pair of "quantized thermal shock value interval" and "chamber temperature interval".

[0125] Once the system obtains the current quantified thermal shock value and the chamber temperature, it first determines the respective intervals to which they belong, and then directly obtains the corresponding window quantity compensation value by looking up a table. This mapping relationship is pre-set by those skilled in the art based on the test data of the cold storage unit's cold release characteristics and thermal load simulation experiment data in the non-rechargeable mode. Its construction method is a conventional technique in this field and will not be elaborated here.

[0126] S51: Collect the zone temperature of each independent zone within the cold storage material unit 2, and sort them according to the zone temperature to obtain a temperature sorting list.

[0127] Zone temperature refers to the real-time temperature of each physically independent sub-region (i.e., "zone") within the cold storage material unit 2. Each zone integrates an independent temperature sensor. Due to uneven temperature distribution within the chamber or different usage conditions, the phase change process and remaining cold capacity vary among the zones.

[0128] A temperature sorting list is an ordered sequence obtained by sorting each zone according to its temperature value from highest to lowest. This list reflects the order of the degree of "cold energy scarcity" of the cold storage material in different zones. The higher the temperature of the zone, the deeper the phase transition of its cold storage material, and the less remaining usable cold energy.

[0129] S52: Determine the number of windows to be opened based on the temperature sorting list and the window quantity compensation value.

[0130] The window number to be opened refers to the unique identifier of the specific window 3 that has been selected as the target for this additional opening.

[0131] Based on the temperature sorting list, starting with the partition with the highest temperature, each partition is traversed sequentially. During the traversal, the available release window 3 numbers are selected sequentially from the currently traversed partitions, and the number of selected window numbers is accumulated. This process is repeated until the accumulated number of selected window numbers reaches the window number compensation value, or all partitions have been traversed. Finally, all the accumulated selected release window 3 numbers are determined as the additional window numbers to be opened this time.

[0132] S53: Control the opening of the heat insulation cover of all release windows 3 corresponding to the window number to be opened, so as to promote heat exchange between the cold storage material unit 2 and the air inside the box.

[0133] The controller sends a command to the corresponding window drive mechanism based on the determined window number to be opened, and controls it to open the heat insulation cover of the release window 3 with the specified number.

[0134] Once the heat-insulating cover is opened, the surface of the previously insulated cold storage material is exposed to the air inside the chamber. This increases the heat exchange area between the cold storage material unit 2 and the air inside the chamber, thereby releasing the stored cold energy at a higher rate. This concentrated release of additional cold energy is used to quickly offset the heat introduced by the heat-loaded items, helping to stabilize the temperature inside the chamber within the set range.

[0135] It also includes transient thermal management methods for door opening: S60: Collects the opening and closing status signal of the refrigerator door.

[0136] The open / closed status signal is an electrical signal used to characterize whether the refrigerator door is in the "open" or "closed" position. This signal is generated by a magnetic induction sensor installed on the door frame. When the door leaves the closed position, the sensor state changes, and the controller obtains real-time status information of the door's open / closed position.

[0137] S61: When the open / closed status signal indicates that the door is open, collect the door opening amplitude, door opening speed, and ambient temperature value.

[0138] The door opening radius refers to the angle through which the door has rotated relative to its fully closed position, which is measured by an angle sensor installed at the door hinge.

[0139] The door opening speed refers to the instantaneous speed of the door during the opening process, which is measured by a speed sensor.

[0140] The ambient temperature value refers to the air temperature of the external space where the refrigerator is located, which is measured by an ambient temperature sensor installed on the refrigerator's outer shell.

[0141] When the open / closed status signal indicates that the door is open, it means that the refrigerator door has been opened. It is necessary to collect the door opening range, door opening speed, and ambient temperature value for subsequent steps.

[0142] S62: Calculate the dynamic thermal intrusion coefficient corresponding to the current door opening action based on the door opening range, door opening speed, and ambient temperature.

[0143] The dynamic thermal intrusion coefficient is a numerical indicator used to comprehensively quantify the potential severity of thermal intrusion caused by a single door opening event.

[0144] After normalizing the door opening width, door opening speed, and ambient temperature, the dynamic thermal intrusion coefficient is obtained by weighting and fusion calculation according to preset weighting coefficients.

[0145] Specifically, the calculation formula can be expressed as: Dynamic thermal intrusion coefficient = k1*F (amplitude) + k2*G (speed) + k3*H (temperature). Wherein, F (amplitude), G (speed), and H (temperature) are functions that normalize the original door opening amplitude, door opening speed, and ambient temperature values, respectively; k1, k2, and k3 are preset weighting coefficients for the corresponding terms, all of which are positive numbers and satisfy k1+k2+k3=1.

[0146] This calculation formula reflects the physical relationship that the greater the door opening range, the slower the speed, and the higher the ambient temperature, the greater the risk of heat intrusion. The specific values ​​of the weighting coefficients k1, k2, and k3 are determined in advance by those skilled in the art through a combination of thermodynamic simulation and experimental calibration. The determination method is a conventional technique in this field and will not be elaborated here.

[0147] S63: Determine the initial start-up wind speed and continuous operating wind pressure of the air curtain device based on the dynamic thermal intrusion coefficient.

[0148] An air curtain device is a device integrated inside the refrigerator door frame, consisting of a row of miniature air outlets and a fan and duct connected to them. Its function is to create a top-down airflow barrier (i.e., an air curtain) with a certain speed and pressure to block or reduce the mixing and exchange of air inside and outside the refrigerator when the door is opened.

[0149] Initial start-up wind speed refers to the set value of the airflow speed at the air outlet when the air curtain device starts instantly after detecting the door opening signal.

[0150] Continuous operating air pressure refers to the airflow pressure setting value required for the air curtain device to maintain an effective air curtain while the door is continuously open.

[0151] The initial start-up wind speed and the continuous operating wind pressure are calculated by multiplying the dynamic thermal intrusion coefficient by a preset wind speed ratio coefficient and a preset wind pressure ratio coefficient, respectively.

[0152] Specifically, the initial start-up wind speed = dynamic thermal intrusion coefficient × Kv; the continuous operation wind pressure = dynamic thermal intrusion coefficient × Kp. Wherein, Kv is a preset wind speed proportional coefficient, and Kp is a preset wind pressure proportional coefficient. Both are determined in advance by those skilled in the art through experimental calibration based on the physical characteristics of the air curtain device, the opening size of the box, and the target blocking efficiency. The determination method is a conventional technical means in this field and will not be elaborated here.

[0153] This calculation method ensures that the wind speed and wind pressure settings are proportional to the dynamic thermal intrusion coefficient, thereby achieving a dynamic and linear response to different levels of thermal intrusion risk.

[0154] S64: Control the air curtain device to start operation with the initial start-up wind speed and the wind pressure during continuous operation, forming an active isolation air curtain inside the door frame.

[0155] The controller generates control commands to drive the fan of the air curtain device based on the calculated initial start-up wind speed and continuous operating wind pressure. After the device starts, an active isolation air curtain is formed from top to bottom inside the door frame. This air curtain is designed to form an isolation layer at the opening of the box during door opening through airflow dynamics, effectively reducing the inflow of external hot air and the escape of internal cold air, thereby significantly reducing the transient heat load and cooling loss caused by door opening operation.

[0156] Also includes: S70: Obtain the door opening heat load compensation value based on the dynamic heat intrusion coefficient.

[0157] The door opening heat load compensation value refers to the number of additional release windows (3) that need to be opened temporarily, beyond the baseline number of windows determined based on the internal temperature, to offset the extra heat intrusion caused by the door opening event during the opening period and for a period after the door is closed. This value is a non-negative integer, and its magnitude is positively correlated with the dynamic heat intrusion coefficient. The larger the coefficient, the more severe the expected heat intrusion, and the greater the required compensation value.

[0158] The door opening heat load compensation value is obtained by querying a preset heat intrusion compensation table. This table records the mapping relationship between dynamic heat intrusion coefficients of different ranges and the corresponding door opening heat load compensation values. It is preset by those skilled in the art after calibration based on thermodynamic simulation and experimental data of the enclosure. Its construction method is a conventional technical means in this field and will not be described in detail here.

[0159] S71: Combine the door opening heat load compensation value with the number of windows opened to determine the total number of dynamic windows opened.

[0160] The total number of dynamic open windows refers to the total number of release windows 3 that actually need to be opened during the entire period affected by the door opening event (including the door opening period and the timer period of the post-closing effect). It consists of two parts: one part is the baseline number of open windows determined based on the current internal temperature of the chamber to maintain the base temperature; the other part is the additional door opening heat load compensation value to cope with the door opening heat load.

[0161] The number of reference windows opened according to method S16 is directly added to the door opening heat load compensation value obtained in S70, and the sum is the total number of dynamic windows opened.

[0162] S72: Control the heat insulation cover to open the corresponding number of release windows 3 according to the total number of dynamic windows opened.

[0163] Based on the calculated total number of dynamic windows to be opened, the controller selects from the cold storage material zones with higher temperatures according to the established window selection rules, determines the specific window number to be opened, and sends a command to control the opening of the insulation cover of the corresponding release window 3, thereby increasing the cold release rate of the cold storage material to actively offset the heat load brought by opening the door.

[0164] S73: When the open / closed status signal indicates that the door is closed, start the closing aftereffect timing and maintain the total number of dynamic open windows based on the current door opening heat load compensation value during the timing period.

[0165] The door-closing effect timing refers to a countdown period that begins when the door closing signal is detected. Its preset duration is determined in advance by those skilled in the art based on factors such as the thermal inertia of the enclosure and the mixing process of residual hot air after the air curtain closes.

[0166] The timing period refers to the time from the start of the after-effect timing when the door closes until its end.

[0167] When the open / closed status signal indicates that the door is closed, the after-effect timer needs to be started, and the total number of windows open should be maintained dynamically based on the current door opening heat load compensation value during the timer period.

[0168] S74: When the after-effect timer ends after the door is closed, the door opening heat load compensation value is reset to zero, and the control logic is restored to determine the required cooling capacity and the number of windows to be opened based solely on the temperature inside the box.

[0169] When the aftereffect timer for the door closing ends, the system considers the additional heat impact of the door opening event to have been largely eliminated. At this point, the controller resets the door opening heat load compensation value to zero. Subsequently, the system exits the "door opening transient management mode," and its control logic fully reverts to the normal state, as shown in S15 and S16: that is, it determines the required cooling capacity based solely on the real-time collected internal temperature, and then calculates and controls the number of windows to be opened, without adding any additional compensation caused by the door opening event.

[0170] It also includes methods for condensate recovery and enhanced heat dissipation: S80: Collects the condenser temperature of the condenser.

[0171] The condenser temperature refers to the temperature value measured in real time by a temperature sensor located near the heat dissipation fins of the refrigerator condenser.

[0172] S81: When the condenser temperature exceeds the preset high temperature alarm threshold and the ambient temperature exceeds the high temperature ambient threshold, the control water collection container will transport the collected evaporator condensate to the ultrasonic atomizing device.

[0173] The high temperature alarm threshold is a critical temperature value used to determine whether the condenser is not dissipating heat well or the operating temperature is too high. The specific value is set in advance by those skilled in the art and will not be elaborated here.

[0174] The high-temperature environment threshold refers to the critical ambient temperature value used to determine whether the external environment temperature is too high, causing a serious decrease in the efficiency of air cooling. The specific value is set in advance by those skilled in the art and will not be elaborated here.

[0175] A condensate collection container is a water storage device used to collect the condensate produced by the refrigerator evaporator during the refrigeration process. It is located below the evaporator and connected by pipes.

[0176] An ultrasonic atomizing device is a device that uses high-frequency ultrasonic vibrations to break liquid water into extremely fine micron-sized water mist.

[0177] This enhanced cooling mode is only triggered when the condenser temperature is too high, exceeding the high-temperature alarm threshold, and the ambient temperature is also high, exceeding the high-temperature ambient threshold. This dual condition check ensures that the system only activates when it truly faces a cooling bottleneck, the condenser itself is overheating, and the ambient temperature is too high for conventional air cooling, thus avoiding unnecessary energy consumption and operation.

[0178] S82: Activate the ultrasonic atomizing device to atomize the evaporator condensate into micron-level water mist and spray it onto the surface of the condenser's heat dissipation fins, thereby updating the condenser temperature.

[0179] The controller activates the ultrasonic atomizing device to atomize the condensate from the water collection container and spray the micron-sized water mist evenly onto the surface of the condenser's heat dissipation fins through the nozzle. After the spraying begins, the condenser temperature is continuously collected to monitor the actual effect of the enhanced heat dissipation measures and provide a basis for further judgment.

[0180] S83: Stop the ultrasonic atomizing device when the temperature of the updated condenser drops below the high temperature alarm threshold.

[0181] When the condenser temperature has dropped below the high-temperature alarm threshold, it indicates that the enhanced heat dissipation has achieved the expected effect and the heat dissipation bottleneck has been resolved. At this point, the controller stops the ultrasonic atomizing device, and the system switches back to the conventional air-cooling mode.

[0182] It also includes methods for storing cold energy: S90: Collects ambient temperature values ​​and the estimated engine shutdown time setting value input by the user through the interactive interface.

[0183] The ambient temperature value is the same parameter as the ambient temperature value mentioned in the aforementioned steps (such as S61 and S81), both referring to the air temperature of the external space where the refrigerator is located, and are measured by the same ambient temperature sensor.

[0184] The estimated engine shutdown time setting refers to the estimated time the vehicle will be shut off, which is manually entered by the user through the interactive interface of the mobile application linked to the in-vehicle refrigerator 1.

[0185] S91: Compare the estimated shutdown duration setting value with the estimated shutdown duration, and take the larger of the two values ​​as the final estimated shutdown duration.

[0186] The estimated shutdown duration setting is compared with the estimated shutdown duration. The larger of the two values ​​is taken as the final estimated shutdown duration. This prioritizes preparation for potentially longer periods without external power, thereby ensuring sufficient cooling capacity reserves and avoiding insulation failure due to insufficient prediction or setting.

[0187] S92: The target cold storage capacity is calculated based on the final expected shutdown time, the temperature inside the chamber, the temperature of the cold storage material unit, and the ambient temperature.

[0188] The target cold energy reserve value refers to the ideal cold energy reserve that the cold storage material unit 2 needs to achieve before the vehicle is turned off in order to maintain the temperature inside the chamber within the target range during the expected shutdown time.

[0189] The target cooling capacity reserve value is calculated by querying the preset cooling capacity demand model.

[0190] The cooling capacity demand model is a multidimensional data model that takes the final expected shutdown time, internal temperature, cold storage material unit temperature, and ambient temperature as inputs, and outputs the target cooling capacity reserve value. A typical implementation of this model is a pre-defined multidimensional lookup table, which specifies a corresponding target cooling capacity reserve value for different combinations of expected shutdown time, internal temperature, cold storage material unit temperature, and ambient temperature.

[0191] Once the system obtains the four input parameters mentioned above, it can directly obtain the required target cooling capacity reserve value by performing a matching query in the table. The cooling capacity demand model was pre-established and stored by those skilled in the art based on thermodynamic simulation of the vehicle-mounted refrigerator system and calibration using a large amount of experimental data. The construction and calibration methods are conventional technical means in this field for determining system parameters through modeling and experimentation, and will not be elaborated here.

[0192] S93: Determine the current cold storage reserve value based on the temperature of the cold storage material unit.

[0193] The current cold energy reserve value refers to the actual usable cold energy stored in cold energy storage material unit 2. The current cold energy reserve value is determined by querying a preset temperature-cold energy mapping table. This mapping table defines the quantitative relationship between different temperature ranges of cold energy storage material units and their corresponding current cold energy reserve values. Its establishment principle is based on the thermophysical properties of the phase change material used: when the temperature is below the phase change point, the cold energy reserve increases as the temperature decreases; near the phase change point, the cold energy reserve undergoes a step change; above the phase change point, the cold energy reserve tends to zero.

[0194] By matching the real-time collected temperature of the cold storage material unit with the temperature range in the mapping table, the corresponding current cold storage reserve value can be obtained by looking up the table. The specific data in this mapping table is determined in advance by those skilled in the art through experimental calibration based on the thermophysical parameters of the phase change material used. Its construction and usage methods are conventional techniques in this field and will not be elaborated here.

[0195] S94: Calculate the required additional cooling capacity based on the current and target cooling capacity reserves.

[0196] The required additional cooling capacity refers to the amount of cooling capacity that needs to be added to the cold storage material unit 2 to meet future insulation needs. Its value is the difference between the target cooling capacity reserve and the current cooling capacity reserve, i.e., Required additional cooling capacity = Target cooling capacity reserve - Current cooling capacity reserve. If the difference is positive, it indicates that additional cooling capacity is needed; if the difference is zero or negative, it indicates that the current reserve is sufficient or excessive, and no additional cooling is required.

[0197] S95: Generate a forward-looking cooling charge command based on the required additional cooling capacity.

[0198] This step connects with S13 and is a specific implementation of "generating forward-looking cooling commands" in S13.

[0199] The system generates a forward-looking charging command by querying a preset mapping relationship of cooling capacity parameters. Specifically, based on the calculated required cooling capacity value, the system searches the mapping relationship for the target power and target duration that the refrigeration component needs to operate to achieve the required cooling capacity. The mapping relationship defines a quantitative relationship between different levels of required cooling capacity values ​​and the corresponding combination of refrigeration component operating power and duration. Its construction principle is based on the performance curve of the refrigeration system (i.e., the amount of cooling capacity that can be replenished to the cold storage material per unit time at different power levels). This mapping relationship is in the form of a data table, predetermined and stored in advance by those skilled in the art based on the performance calibration experimental data of a specific refrigeration system. Ultimately, the generated forward-looking charging command contains a set of defined (target power, target duration) control parameters to guide the refrigeration component to perform precise charging operations before the vehicle is turned off. The specific construction and usage methods of the mapping relationship are conventional techniques in this field and will not be elaborated here.

[0200] Based on the same inventive concept, embodiments of the present invention provide a low-power, long-insulation refrigeration system, comprising: The data acquisition module is used to collect data on power supply status, internal temperature, cold storage material unit temperature, vehicle navigation information, user historical parking information, temperature change rate, material historical average temperature, contact temperature, change rate, change amplitude, placement area location, zone temperature, opening and closing status signal, door opening amplitude, door opening speed, ambient temperature value, condenser temperature, and expected shutdown time setting. The memory is used to store the program that implements a low-power, long-heat-preservation refrigeration method for a refrigeration system; The processor is used to load and execute programs stored in memory.

[0201] Those skilled in the art will clearly understand that, for the sake of convenience and brevity, the above-described division of functional modules is used as an example. In practical applications, the above functions can be assigned to different functional modules as needed, that is, the internal structure of the device can be divided into different functional modules to complete all or part of the functions described above. The specific working process of the system, device, and unit described above can be referred to the corresponding process in the foregoing method embodiments, and will not be repeated here.

[0202] The above description is merely a preferred embodiment of the present invention. The scope of protection of the present invention is not limited to the above embodiments. All technical solutions falling within the scope of the present invention's concept are within the scope of protection of the present invention. It should be noted that for those skilled in the art, any improvements and modifications made without departing from the principles of the present invention should also be considered within the scope of protection of the present invention.

Claims

1. A low-power, long-term heat preservation refrigeration method for a refrigeration system, characterized in that, include: Collect the power supply status, internal temperature and cold storage material unit temperature of the vehicle refrigerator (1); The corresponding working mode is matched based on the power supply status. When the matched working mode is rechargeable mode, vehicle navigation information and user historical parking information are collected, and the user's arrival location is retrieved based on the vehicle navigation information. The estimated engine shutdown time is matched based on the user's arrival location and user historical parking information. Based on the expected shutdown time, the temperature inside the chamber, and the temperature of the cold storage material unit, a forward-looking charging command for the cold storage material unit (2) is generated; In response to the forward-looking charging command, the operation of the refrigeration components is controlled before the vehicle is turned off, so as to increase the cold storage material unit (2); When the working mode is switched to non-rechargeable mode, the cooling components are prohibited from operating, and the required cooling capacity is determined based on the internal temperature of the chamber. The number of windows to be opened is determined based on the demand for releasing cold energy, and the corresponding number of release windows (3) are controlled to open in order to adjust the cold energy release rate and maintain the temperature inside the chamber.

2. The low-power, long-term heat preservation refrigeration method for a refrigeration system according to claim 1, characterized in that, It also includes methods for adjusting the number of open windows: The rate of temperature change inside the collection box and the historical average temperature of the cold storage material unit (2) were collected. Compare the rate of temperature change with a rate of change threshold, and compare the material’s historical average temperature with an average temperature threshold. When the rate of temperature change exceeds the rate of change threshold, it is determined that the temperature is rising rapidly, and a compensation instruction to increase the number of release windows is generated. When the historical average temperature of the material is lower than the average temperature threshold, it is determined that the overall cold storage material has sufficient cold capacity reserves, and a restriction instruction to reduce the number of release windows is generated. The number of basic windows to be opened is calculated based on the demand for releasing cooling capacity. Then, by combining compensation instructions and restriction instructions, the number of basic windows to be opened is dynamically added and reduced to obtain the final number of windows to be opened.

3. The low-power, long-term heat preservation refrigeration method for a refrigeration system according to claim 1, characterized in that, It also includes methods for dealing with heat load: The pressure change value of the storage support structure inside the collection box and the contact temperature of the items in direct contact with it were collected. When the pressure change value reaches the pressure characteristic threshold within the preset pressure detection time, it is initially determined that an item has been placed. In response to the initial assessment, the contact temperature is compared with the temperature inside the chamber. When the contact temperature is consistently higher than the temperature inside the chamber and exceeds the contact temperature threshold, the placed item is determined to be a heat-loaded item. In response to the secondary determination, the rate and magnitude of pressure change values ​​are collected during the period when the pressure characteristic threshold is reached; Pressure characteristic factors are calculated based on the rate and magnitude of change. The temperature difference is calculated based on the difference between the contact temperature and the temperature inside the chamber. Based on the pressure characteristic factor and temperature difference, the quantitative thermal shock value of the heat load is obtained through weighted fusion calculation; The thermal load compensation strategy is determined based on the quantified thermal shock value and the operating mode, and the corresponding thermal load compensation strategy is executed.

4. The low-power, long-term heat preservation refrigeration method for a refrigeration system according to claim 3, characterized in that, The heat load compensation strategy includes: If the current matched operating mode is rechargeable mode, the enhanced operating power increment and enhanced operating time of the cooling component are calculated based on the quantified thermal shock value. The location of the heat-loaded item to be placed is recorded; The target surface curvature of the deformable air bladder (4) required to deflect and guide the cold airflow is calculated based on the relative orientation of the placement area and the main air duct inside the box. The target inflation pressure value of each independent air chamber inside the deformable air bladder (4) is determined based on the target surface curvature. The cooling components are controlled to enhance the operating power and operating time. At the same time, according to the target inflation pressure value of each air chamber, the corresponding micro air pump (5) is controlled to inflate the deformable guide air bag (4) so ​​that it is deformed into a shape with the target surface curvature, thereby guiding the cold air flow into the placement area.

5. A low-power, long-term heat preservation refrigeration method for a refrigeration system according to claim 4, characterized in that, The heat load compensation strategy also includes: If the current matching working mode is non-rechargeable mode, the compensation value for the number of additional windows that need to be opened is calculated based on the quantified thermal shock value and the internal temperature of the chamber. Collect the zone temperature of each independent zone in the cold storage material unit (2), and sort them according to the zone temperature to obtain a temperature sorting list. The window number to be opened is determined based on the temperature sorting list and the window quantity compensation value. Control the opening of the heat insulation cover of all release windows (3) corresponding to the window number to be opened, so as to promote heat exchange between the cold storage material unit (2) and the air inside the box.

6. The low-power, long-term heat preservation refrigeration method for a refrigeration system according to claim 1, characterized in that, It also includes transient thermal management methods for door opening: Collect the opening and closing status signal of the refrigerator door; When the open / closed status signal indicates that the door is open, the door opening amplitude, door opening speed, and ambient temperature value are collected. The dynamic thermal intrusion coefficient corresponding to the current door opening action is calculated based on the door opening range, door opening speed, and ambient temperature. The initial start-up wind speed and continuous operating wind pressure of the air curtain device are determined based on the dynamic thermal intrusion coefficient. The control air curtain device starts operating at the initial start-up wind speed and the continuous operating wind pressure, forming an active isolation air curtain inside the door frame.

7. A low-power, long-term heat preservation refrigeration method for a refrigeration system according to claim 6, characterized in that, Also includes: The door opening heat load compensation value is obtained based on the dynamic heat intrusion coefficient; The total number of dynamically opened windows is determined by combining the door opening heat load compensation value with the number of windows opened. Control the heat insulation cover to open the corresponding number of release windows according to the total number of dynamic windows opened (3); When the open / closed status signal indicates that the door is closed, the closing aftereffect timer is started, and the total number of windows open is maintained dynamically based on the current door opening heat load compensation value during the timer period; When the after-effect timer ends after the door is closed, the door opening heat load compensation value is reset to zero, and the control logic is restored to determine the required cooling capacity and the number of windows to be opened based solely on the internal temperature of the box.

8. A low-power, long-term heat preservation refrigeration method for a refrigeration system according to claim 6, characterized in that, It also includes methods for condensate recovery and enhanced heat dissipation: Collect the condenser temperature of the condenser; When the condenser temperature exceeds the preset high temperature alarm threshold and the ambient temperature exceeds the high temperature ambient threshold, the control water collection container will transport the collected evaporator condensate to the ultrasonic atomizing device. The ultrasonic atomizing device is activated to atomize the evaporator condensate into micron-sized water mist and spray it onto the surface of the condenser's heat dissipation fins, thereby updating the condenser temperature. The ultrasonic atomizing device will stop when the temperature of the updated condenser drops below the high-temperature alarm threshold.

9. A low-power, long-term heat preservation refrigeration method for a refrigeration system according to claim 1, characterized in that, It also includes methods for storing cold energy: Collect ambient temperature values ​​and the expected engine shutdown time setting value input by the user through the interactive interface; The estimated shutdown time setting value is compared with the estimated shutdown time, and the larger of the two values ​​is taken as the final estimated shutdown time. The target cold energy reserve value is calculated based on the final estimated shutdown time, the temperature inside the chamber, the temperature of the cold storage material unit, and the ambient temperature. The current cold storage reserve value is determined based on the temperature of the cold storage material unit; The required additional cooling capacity is calculated based on the current and target cooling capacity reserves. Generate forward-looking cooling charge instructions based on the required additional cooling capacity.

10. A low-power, long-insulation refrigeration system, characterized in that, include: The data acquisition module is used to collect information such as power supply status, internal temperature, temperature of cold storage material unit, vehicle navigation information, and user's historical parking information. A memory for storing a program that implements a low-power, long-heat-preservation refrigeration method for a refrigeration system as described in any one of claims 1 to 9; The processor is used to load and execute programs stored in memory.

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