Refrigerator and control method thereof

Abstract

The invention discloses a refrigerator and a control method thereof. The environment temperature of the refrigerator, a first thermal resistance parameter (a thermal resistance parameter between a target heat pipe and a drainage pipe), a second thermal resistance parameter (a thermal resistance parameter between a freezing chamber and the drainage pipe), the chamber temperature of the freezing chamber and the pipeline temperature of the drainage pipe are obtained; according to the first thermal resistance parameter, the environment temperature and the pipeline temperature, calculating heat transferred to the drainage pipe by the target heat pipe in the recent set time period; according to the second thermal resistance parameter, the pipeline temperature and the chamber temperature, the cooling capacity transmitted to the drainage pipe by the freezing chamber in the recent set time period is calculated; calculating a heat demand based on the pipeline temperature and the target temperature; and operating parameters of heating wires near the drainage pipe are adjusted according to the cooling capacity, the heat and the heat demand. The running parameters of the heating wire are controlled according to the cooling capacity transmitted to the water drainage pipe by the freezing chamber, the heat transmitted to the water drainage pipe by the condenser and the heat demand quantity of the water drainage pipe, and energy waste is reduced under the condition that the water drainage pipe is not blocked.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigerators, and in particular to a refrigerator and a control method thereof. Background Art

[0002] When the refrigerator evaporator defrosts, condensation water is produced and needs to be drained through the drain pipe. Since the drain pipe is usually installed near the freezer compartment, which is at a lower temperature, it is prone to internal ice formation in low-temperature environments. When the ice completely blocks the pipe, the condensation water cannot be drained, causing water accumulation inside the refrigerator.

[0003] The current common solution is to install a heating wire on the drain pipe and control the operation of the heating wire by starting and stopping it synchronously with the compressor. In order to ensure that the pipe is completely free of ice, the existing technology often uses a higher-power heating wire. This design has obvious energy waste problems. Summary of the Invention

[0004] The purpose of the embodiment of the present invention is to provide a refrigerator and a control method thereof, which can control the operating parameters of the heating wire according to the cold amount transferred to the water pipe of the freezer, the heat transferred to the water pipe of the condenser, and the heat demand of the drain pipe, thereby reducing energy waste while ensuring that the drain pipe is not blocked.

[0005] To achieve the above object, an embodiment of the present invention provides a refrigerator, comprising:

[0006] Freezer, for storing items;

[0007] A refrigeration system for providing power for the refrigeration cycle of the refrigerator, comprising a compressor, an evaporator, and a heat dissipation unit; a target heat pipe in the heat dissipation unit is also used to provide heat to the drain pipe, and the target heat pipe is arranged near the drain pipe;

[0008] The drain pipe is used to connect the evaporator and the water receiving box, and is used to guide the water generated by the defrosting of the evaporator to the water receiving box;

[0009] a heating wire, disposed near the drain pipe and used for heating the drain pipe;

[0010] The ambient temperature detection device is installed on the refrigerator shell and is used to detect the ambient temperature;

[0011] A freezing temperature detection device is provided in the freezing chamber and is used to detect the real-time temperature of the freezing chamber;

[0012] Controller for:

[0013] Acquire the ambient temperature, a first thermal resistance parameter, a second thermal resistance parameter, a compartment temperature of the freezing chamber, and a pipe temperature of the drain pipe; the first thermal resistance parameter is the thermal resistance parameter between the target heat pipe and the drain pipe, and the second thermal resistance parameter is the thermal resistance parameter between the freezing chamber and the drain pipe;

[0014] Calculating the amount of heat transferred from the target heat pipe to the drain pipe in a recent set time period according to the first thermal resistance parameter, the ambient temperature, and the pipe temperature;

[0015] Calculating the cooling capacity transferred from the freezing chamber to the drain pipe during the most recent set time period based on the second thermal resistance parameter, the pipe temperature, and the compartment temperature;

[0016] Calculating heat demand based on the pipeline temperature and a preset target temperature;

[0017] The operating parameters of the heating wire are controlled according to the cooling capacity, the heating capacity and the heat demand.

[0018] As an improvement to the above solution, the first thermal resistance parameter includes a natural surface heat transfer coefficient and a heat exchange area between the drain pipe and the target heat pipe;

[0019] The controller is configured to calculate the amount of heat transferred from the target heat pipe to the drain pipe during the most recent set time period by:

[0020] calculating a first temperature difference between the ambient temperature and the pipeline temperature;

[0021] The amount of heat transferred from the target heat pipe to the drain pipe during the most recent set time period is calculated based on the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the length of the most recent set time period; wherein the heat is positively correlated with the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the length of the most recent set time period, respectively.

[0022] As an improvement to the above solution, the step of calculating the amount of heat transferred from the target heat pipe to the drain pipe during the most recent set time period based on the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the duration of the most recent set time period includes:

[0023] The heat transferred from the target heat pipe to the drain pipe in the most recent set time period is obtained by multiplying the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the duration of the most recent set time period.

[0024] As an improvement to the above solution, the second thermal resistance parameter includes the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner surface of the freezer compartment, the thermal conductivity of the insulation layer between the freezer compartment and the drain pipe, the thickness of the insulation layer, and the heat exchange area between the drain pipe and the freezer compartment;

[0025] The controller is used to calculate the cooling capacity transferred from the freezing chamber to the drain pipe in the latest set time period by:

[0026] Calculating a second temperature difference between the pipeline temperature and the compartment temperature;

[0027] The amount of cold transferred from the freezer compartment to the drain pipe during a recent set time period is calculated based on the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient on the inner liner surface of the freezer compartment, the thermal conductivity of the insulation layer, the thickness of the insulation layer, the heat exchange area between the drain pipe and the freezer compartment, and the second temperature difference; wherein the cold amount is positively correlated with the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient on the inner liner surface of the freezer compartment, the thermal conductivity of the insulation layer, the heat exchange area between the drain pipe and the freezer compartment, and the second temperature difference, and the cold amount is negatively correlated with the thickness of the insulation layer.

[0028] As an improvement to the above solution, the calculation of the cooling capacity transferred from the freezer compartment to the drain pipe during the most recent set time period based on the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner tank surface of the freezer compartment, the thermal conductivity of the insulation layer, the thickness of the insulation layer, the heat exchange area between the drain pipe and the freezer compartment, and the second temperature difference includes:

[0029] The total heat transfer coefficient is obtained by adding the reciprocal of the convection heat transfer coefficient inside the drain pipe, the reciprocal of the convection heat transfer coefficient on the surface of the inner container of the freezing chamber, the thickness of the insulation layer and the thermal conductivity of the insulation layer, and taking the reciprocal.

[0030] The total heat transfer coefficient, the heat exchange area between the drain pipe and the freezing chamber, and the second temperature difference are multiplied together to obtain the cooling capacity transferred from the freezing chamber to the drain pipe in the most recent set time period.

[0031] As an improvement to the above solution, the controller is used to control the operating parameters of the heating wire in the following manner:

[0032] When the heat is greater than or equal to the sum of the cooling capacity and the heat demand, the heating wire is not turned on;

[0033] When the heat is less than the sum of the cooling capacity and the heat demand, the heating wire is controlled to turn on.

[0034] As an improvement to the above solution, when the heat is less than the sum of the cooling capacity and the heat demand, controlling the heating wire to turn on includes:

[0035] When the heat is less than the sum of the cooling capacity and the heat demand, controlling the heating wire to operate at a target operating rate;

[0036] The target availability is calculated as follows:

[0037] Obtaining the amount of heat that the heating wire can provide per unit time; wherein the unit time is equal to the length of the most recently set time period;

[0038] Add the cooling capacity and the heat demand and then subtract the heat demand to obtain an energy difference;

[0039] The target on-rate is obtained by dividing the energy difference by the amount of heat that the heating wire can provide per unit time.

[0040] As an improvement to the above solution, the controller is used to obtain the pipeline temperature by:

[0041] Based on a preset temperature mapping relationship, determining the pipe temperature of the drain pipe according to the compartment temperature of the freezing chamber;

[0042] The temperature mapping relationship is obtained by fitting the freezing temperature of the freezer compartment and the drain pipe temperature; the freezing temperature and the drain pipe temperature are measured when the heating wire is not working and the target heat pipe does not provide heat to the drain pipe.

[0043] As an improvement to the above scheme, the most recently set time period is the period of compressor operation most recently after the first defrosting of the refrigerator, the compartment temperature of the freezer is the real-time temperature of the freezer after the most recently set time period or the average temperature of the freezer during the most recently set time period, and the target heat pipe includes at least one of a condenser, an anti-condensation tube and a pressure reducer.

[0044] To achieve the above object, an embodiment of the present invention further provides a refrigerator control method, comprising:

[0045] Obtaining the ambient temperature of the refrigerator, a first thermal resistance parameter, a second thermal resistance parameter, a compartment temperature of the refrigerator's freezer compartment, and a pipe temperature of a drain pipe; the first thermal resistance parameter is the thermal resistance parameter between the refrigerator's heat dissipation unit and the drain pipe, and the second thermal resistance parameter is the thermal resistance parameter between the freezer compartment and the drain pipe. The drain pipe is used to guide water generated by defrosting the refrigerator's evaporator to the refrigerator's water receiving box;

[0046] Calculating the amount of heat transferred from the heat dissipation unit to the drain pipe in a recent set time period according to the first thermal resistance parameter, the ambient temperature, and the pipe temperature;

[0047] Calculating the cooling capacity transferred from the freezing chamber to the drain pipe during the most recent set time period based on the second thermal resistance parameter, the pipe temperature, and the compartment temperature;

[0048] Calculating heat demand based on the pipeline temperature and a preset target temperature;

[0049] The operating parameters of the heating wire arranged near the drain pipe are controlled according to the cooling capacity, the heating capacity and the heat demand.

[0050] Compared to the prior art, the refrigerator and its control method disclosed in the embodiment of the present invention first obtain the following data: the ambient temperature of the refrigerator, the first thermal resistance parameter (the thermal resistance parameter between the condenser and the drain pipe), the second thermal resistance parameter (the thermal resistance parameter between the freezer and the drain pipe), the compartment temperature of the freezer, and the pipe temperature of the drain pipe, which is used to guide the water generated by the defrosting of the refrigerator's evaporator to the water receiving box of the refrigerator; then perform energy transfer calculation: calculate the heat transferred from the condenser to the drain pipe in the most recent set time period based on the first thermal resistance parameter, the ambient temperature, and the pipe temperature; calculate the cooling capacity transferred from the freezer to the drain pipe in the most recent set time period based on the second thermal resistance parameter, the pipe temperature, and the compartment temperature; then determine the control demand: calculate the heat demand based on the pipe temperature and the preset target temperature; finally, dynamically adjust the operating parameters of the heating wire near the drain pipe based on the calculated cooling capacity, heat capacity, and heat demand. As can be seen from this, the embodiment of the present invention controls the operating parameters of the heating wire based on the cooling capacity transferred from the freezer to the drain pipe, the heat transferred from the condenser to the drain pipe, and the heat demand of the drain pipe, thereby reducing energy waste while ensuring that the drain pipe is not blocked. BRIEF DESCRIPTION OF THE DRAWINGS

[0051] Figure 1 is a perspective view of a refrigerator provided by an embodiment of the present invention;

[0052] Figure 2 is a three-dimensional diagram of a refrigerator door provided by an embodiment of the present invention;

[0053] Figure 3 is a schematic structural diagram of a refrigeration system provided by an embodiment of the present invention;

[0054] Figure 4 Schematic diagram of the structure of a drain pipe provided by an embodiment of the present invention;

[0055] Figure 5 This is a first working flow diagram of the controller provided by an embodiment of the present invention;

[0056] Figure 6 is a second working flow diagram of the controller provided by an embodiment of the present invention;

[0057] Figure 7 is a third working flow diagram of the controller provided in an embodiment of the present invention;

[0058] Figure 8 Schematic diagram of heat transfer provided by an embodiment of the present invention;

[0059] Figure 9 is a fourth working flow diagram of the controller provided in an embodiment of the present invention;

[0060] Figure 10 is a fifth working flow diagram of the controller provided in an embodiment of the present invention;

[0061] Figure 11 It is a flowchart of a refrigerator control method provided by an embodiment of the present invention.

[0062] Among them, 100, box body, 200, door body, 210, door body shell, 220, door body inner liner, 230, upper end cover, 240, lower end cover; 1, compressor, 2, condenser, 3, anti-condensation tube, 4, drying filter, 5, pressure reducer, 6, evaporator, 7, gas-liquid separator; 8, drain pipe; 9, U-shell anti-condensation tube; 10, freezing liner. DETAILED DESCRIPTION

[0063] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. All other embodiments obtained by ordinary technicians in this field based on the embodiments of the present invention without making any creative efforts shall fall within the scope of protection of the present invention.

[0064] In the description of this application, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on this application.

[0065] The terms "first" and "second" are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, features specified as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of this application, unless otherwise specified, "plurality" means two or more.

[0066] In the description of this application, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this application based on the specific circumstances.

[0067] See also Figure 1 , Figure 1 : is a perspective view of a refrigerator provided by an embodiment of the present invention. The refrigerator of this embodiment has an approximately rectangular parallelepiped shape. The refrigerator includes a box body 100 defining a storage space and a plurality of door bodies 200 provided at the opening of the box body 100. Figure 2 As shown, the door body 200 includes a door body shell 210 located outside the box body 100, a door body liner 220 located inside the box body 100, an upper end cover 230, a lower end cover 240, and an insulation layer located between the door body shell 210, the door body liner 220, the upper end cover 230, and the lower end cover 240; usually, the insulation layer is filled with foam. The box body 100 is provided with a chamber, wherein the chamber includes a component storage chamber for placing components in the refrigerator, such as a compressor, etc., and also includes a storage space for storing food, etc. Among them, the refrigerator in the embodiment of the present invention includes a refrigeration system, see Figure 3 The refrigeration system structure diagram shown in the figure is arranged in the component storage cavity, which is used to provide power for the refrigeration cycle of the refrigerator, including a compressor, evaporator, pressure reducer and condenser; the storage space can be divided into multiple compartments, which can be configured as refrigerators, freezers, etc. according to different uses. Each compartment corresponds to one or more doors, such as Figure 1 The upper compartment is provided with a double-door body, wherein the door body can be pivotally arranged at the opening of the box body, and can also be opened in a drawer-like manner to realize drawer-like storage.

[0068] See also Figure 3 , Figure 3Figure 1 is a schematic diagram of the structure of a refrigerator refrigeration system according to an embodiment of the present invention. The refrigeration system includes a compressor 1, a condenser 2, an anti-condensation tube 3, a filter drier 4, a pressure reducer 5, an evaporator 6, and a gas-liquid separator 7. The condenser 2, anti-condensation tube 3, and pressure reducer 5 all dissipate heat and are therefore referred to as a heat dissipation unit. The operating process of the refrigeration system includes compression, condensation, throttling, and evaporation.

[0069] Among them, combined Figure 3 The compression process is as follows: plug in the refrigerator power cord, when the thermostat contacts are connected, compressor 1 starts working, low-temperature, low-pressure refrigerant is sucked into compressor 1, compressed into high-temperature, high-pressure superheated gas in the compressor cylinder, and then discharged into condenser 2; the condensation process is as follows: the high-temperature, high-pressure refrigerant gas dissipates heat through condenser 2, the temperature continues to drop, and is gradually cooled to a saturated vapor at room temperature and high pressure, and further cooled to a saturated liquid, and the temperature no longer drops. The temperature at this time is called the condensation temperature, and the pressure of the refrigerant remains almost unchanged during the entire condensation process; the throttling process is as follows: after The condensed refrigerant saturated liquid passes through a drying filter 4 to remove moisture and impurities, and then flows into a pressure reducer 5 (such as a capillary tube), where it is throttled and pressure-reduced, and the refrigerant becomes wet vapor at room temperature and low pressure. The evaporation process is as follows: the wet vapor at room temperature and low pressure begins to absorb heat and vaporize in the evaporator 6, which not only lowers the temperature of the evaporator and its surroundings, but also turns the refrigerant into a low-temperature, low-pressure gas. The refrigerant coming out of the evaporator 6 passes through the gas-liquid separator 7 and returns to the compressor 1 again, repeating the above process to transfer the heat in the refrigerator to the air outside the box, thereby achieving the purpose of cooling.

[0070] The freezer compartment is equipped with a freezing temperature detection device, which can be installed on the upper, lower, left, or right walls of the freezer compartment to monitor the freezer compartment's real-time temperature. The refrigerator housing is equipped with an ambient temperature detection device to monitor the ambient temperature. The freezing temperature monitoring device and ambient temperature detection device can be temperature sensors or other devices capable of detecting temperature, without limitation.

[0071] It's worth noting that a temperature sensor is a sensor that senses temperature and converts it into a usable output signal. Based on the measurement method, they can be categorized as contact and non-contact. Based on the sensor material and electronic component characteristics, they can be divided into thermal resistors and thermocouples. Manufacturers can select specific temperature sensor types based on actual application requirements. The specific type and installation location of ambient temperature detection devices and freezer temperature detection devices can be determined based on actual needs and are not specified here.

[0072] like Figure 4The schematic diagram of the structure of the drain pipe shown in the figure shows that the refrigerator also includes a drain pipe 8. The target heat pipe can be a condenser, an anti-condensation pipe or a pressure reducer (i.e., a capillary tube), etc. Assuming that the target heat pipe is the U-shell anti-condensation pipe 9 in the heat dissipation unit, the U-shell anti-condensation pipe 9 is usually located at the door frame or the edge of the refrigerator body, and the residual heat of the condenser is used to prevent condensation on the door frame. In this embodiment, the U-shell anti-condensation pipe 9 is also arranged near the drain pipe 8 to provide heat for the drain pipe 8 and reduce the risk of freezing of the drain pipe 8. The drain pipe 8 is arranged on the outside of the freezing liner 10 of the freezer compartment, and an insulation layer (not shown in the figure) is provided between the drain pipe 8 and the freezing liner 10. The inlet of the drain pipe 8 is arranged at the bottom of the evaporator 6 and extends to the water receiving box of the refrigerator (not shown in the figure) to guide the condensed water generated by the defrosting of the evaporator 6. In order to prevent the drain pipe 8 from freezing, the present embodiment also arranges a heating wire (not shown in the figure) near the drain pipe 8 for heating the drain pipe 8. The heating wire can be in direct contact with the drain pipe 8 (such as being wrapped around the pipe wall or embedded in the pipe wall, etc.), or it can be not in direct contact with the drain pipe 8 but close to the drain pipe 8 (such as being installed close to the outer wall or inner wall of the pipe, but not in physical contact). The specific setting method of the heating wire can be set according to actual conditions and is not limited here.

[0073] Specifically, the refrigerator also includes a controller. In an embodiment of the present invention, the controller is electrically connected to each of the above-mentioned controllable devices, and the controller is configured to: obtain the ambient temperature, a first thermal resistance parameter, a second thermal resistance parameter, the compartment temperature of the freezer compartment, and the pipe temperature of the drain pipe; the first thermal resistance parameter is the thermal resistance parameter between the target heat pipe and the drain pipe, and the second thermal resistance parameter is the thermal resistance parameter between the freezer compartment and the drain pipe; calculate the amount of heat transferred to the drain pipe by the target heat pipe in the most recent set time period based on the first thermal resistance parameter, the ambient temperature, and the pipe temperature; calculate the amount of cold transferred to the drain pipe by the freezer compartment in the most recent set time period based on the second thermal resistance parameter, the pipe temperature, and the compartment temperature; calculate the heat demand based on the pipe temperature and the preset target temperature; and control the operating parameters of the heating wire based on the cold amount, the heat, and the heat demand.

[0074] For example, see Figure 5 , Figure 5 : is a first working flow diagram of a controller provided in an embodiment of the present invention, wherein the controller is configured to execute steps S11 to S15:

[0075] S11. Obtain the ambient temperature, the first thermal resistance parameter, the second thermal resistance parameter, the compartment temperature of the freezing chamber, and the pipe temperature of the drain pipe, and then proceed to step S12.

[0076] Specifically, the first thermal resistance parameter is the thermal resistance parameter between the target heat pipe and the drain pipe, and the second thermal resistance parameter is the thermal resistance parameter between the freezer compartment and the drain pipe. The thermal resistance parameters reflect the resistance information during the heat transfer process. The pipe temperature can be the temperature of the interior space of the drain pipe or the temperature of the inner surface of the drain pipe. Preferably, the pipe temperature refers to the temperature of the interior space of the drain pipe, which is the drain pipe temperature corresponding to the compartment temperature of the freezer compartment when the heating wire is not working and the target heat pipe is not providing heat to the drain pipe. The target heat pipe can be a condenser, a capillary tube, or an anti-condensation tube, etc., which is not limited here.

[0077] S12. Calculate the amount of heat transferred from the target heat pipe to the drain pipe in the most recent set time period based on the first thermal resistance parameter, the ambient temperature, and the pipe temperature, and then proceed to step S13.

[0078] Specifically, since the target heat pipe is located near the drain pipe, when the compressor is running, some of the heat generated by the target heat pipe is transferred to the drain pipe. The amount of heat transferred to the drain pipe by the target heat pipe during this period is calculated at regular intervals. This heat reduces the risk of freezing in the drain pipe to a certain extent. Preferably, the most recently set time period is after the first defrost after the refrigerator is powered on, and during the most recent compressor operation from the current time. Steps S11 to S15 are performed after the compressor operation ends. Optionally, the most recently set time period can also be a preset period time period, and is not limited to the above specific example.

[0079] S13, calculating the cooling capacity transferred from the freezing chamber to the drain pipe in the most recent set time period according to the second thermal resistance parameter, the pipe temperature and the compartment temperature, and then proceeding to step S14.

[0080] Specifically, since the drain pipe is located near the freezer compartment, the cold energy of the freezer compartment is transferred to the drain pipe. The amount of cold energy transferred from the freezer compartment to the drain pipe during this period is calculated at regular intervals, and this amount of cold energy increases the risk of the drain pipe freezing.

[0081] S14. Calculate the heat demand based on the pipeline temperature and the preset target temperature, and then proceed to step S15.

[0082] Specifically, the target temperature is generally greater than 0°C to prevent ice from forming inside the drain pipe. It can be 1°C or 2°C, for example. The specific value can be set based on actual conditions and is not limited here. The specific formula for calculating the heat demand is: Heat demand Q2 = cm(T0 - T1), where c is the specific heat capacity of air; T1 is the current drain pipe temperature; m is the air mass; and TO is the target temperature (2°C is used in this application example). It is worth noting that heat demand Q2 refers to the amount of heat required to heat the drain pipe (e.g., the internal temperature) to the target temperature TO.

[0083] S15. Controlling the operating parameters of the heating wire according to the cooling capacity, the heating capacity, and the heat demand.

[0084] It is understandable that in the same period of time, the cold transferred from the freezer to the drain pipe and the heat transferred from the target heat pipe to the drain pipe will offset each other to a certain extent. In order to avoid clogging of the drain pipe, it is necessary to consider whether the heat received by the drain pipe can offset the cold transferred from the freezer and meet the heat requirements of the drain pipe, and control the operating parameters of the heating wire.

[0085] Compared with the existing technology, this embodiment controls the operating parameters of the heating wire according to the cold amount transferred to the freezer compartment water supply and drainage pipe, the heat transferred to the condenser water supply and drainage pipe, and the heat demand of the drainage pipe, thereby reducing energy waste while ensuring that the drainage pipe is not blocked.

[0086] In a preferred embodiment, the first thermal resistance parameter includes a natural surface heat transfer coefficient and a heat exchange area between the drain pipe and the target heat pipe; the controller is used to calculate the amount of heat transferred by the target heat pipe to the drain pipe in the most recent set time period in the following manner: calculating a first temperature difference between the ambient temperature and the pipe temperature; calculating the amount of heat transferred by the target heat pipe to the drain pipe in the most recent set time period based on the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference and the length of the most recent set time period; wherein the amount of heat is positively correlated with the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference and the length of the most recent set time period, respectively.

[0087] Specifically, this embodiment further limits the calculation method of the heat transferred from the target heat pipe to the drain pipe in the latest set time period. Figure 6 , Figure 6 is a second working flow diagram of the controller provided in an embodiment of the present invention, wherein the controller is further configured to execute steps S16 to S17:

[0088] S16. Calculate a first temperature difference between the ambient temperature and the pipeline temperature, and then proceed to step S17.

[0089] S17. Calculate the amount of heat transferred from the target heat pipe to the drain pipe during the most recent set time period based on the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the duration of the most recent set time period.

[0090] Specifically, assuming the target heat pipe is a condenser, the condenser temperature is typically 3-8°C higher than the ambient temperature. In this embodiment, the ambient temperature is used to offset the negative impact of uncertainties in the manufacturing process on the drain pipe temperature. A first temperature difference ΔT1 is calculated by subtracting the drain pipe temperature T1 from the ambient temperature Te. Then, based on basic heat transfer theory, the heat transfer coefficient of the natural surface and the heat transfer area between the drain pipe and the target heat pipe (thermal resistance parameters) are used to calculate the heat Q3 transferred from the condenser to the drain pipe during the most recently set time period based on the first temperature difference ΔT1.

[0091] In a preferred embodiment, the calculation of the heat transferred by the target heat pipe to the drain pipe in the most recent set time period based on the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference and the length of the most recent set time period includes: multiplying the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference and the length of the most recent set time period to obtain the heat transferred by the target heat pipe to the drain pipe in the most recent set time period.

[0092] Specifically, this embodiment further limits the calculation method of the heat transferred by the target heat pipe to the drain pipe in the most recent set time period and provides a specific calculation formula:

[0093] Q3=α×Al×ΔT1×t

[0094] Where Q3 is the heat transferred from the target heat pipe to the drain pipe in the most recent set time period; A1 is the heat exchange area between the drain pipe and the target heat pipe; ΔT1 is the difference between the ambient temperature and the drain pipe temperature; t is the duration of the most recent set time period; α is the natural surface heat transfer coefficient, assuming α is 7w / m 2 k, in heat transfer, "w / m 2 K″ is the unit of natural surface heat transfer coefficient, which represents the power transferred (i.e., heat transfer rate) per square meter of surface area and per Kelvin temperature difference (or per degree Celsius temperature difference), 7w / m 2 k means that on a surface of 1 square meter, when the temperature difference between the fluid and the solid surface is 1K (or 1°C), the heat transferred by convection per second is 7 joules. It is worth noting that α is 7w / m2 k is just a specific example, and the specific value of α should be determined according to actual conditions.

[0095] In a preferred embodiment, the second thermal resistance parameter includes the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner tank surface of the freezer compartment, the thermal conductivity of the insulation layer between the freezer compartment and the drain pipe, the thickness of the insulation layer and the heat exchange area between the drain pipe and the freezer compartment; the controller is used to calculate the cooling capacity transferred from the freezer compartment to the drain pipe in the most recent set time period by calculating the second temperature difference between the pipe temperature and the compartment temperature; according to the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner tank surface of the freezer compartment, and the heat transfer area between the drain pipe and the freezer compartment, the controller calculates the cooling capacity transferred from the freezer compartment to the drain pipe in the most recent set time period by calculating the second temperature difference between the pipe temperature and the compartment temperature; according to the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner tank surface of the freezer compartment, and the heat transfer area between the drain pipe and the freezer compartment; The cooling capacity transferred from the freezer to the drain pipe in the most recent set time period is calculated based on the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner tank surface of the freezer, the thermal conductivity of the insulation layer between the freezer, the thickness of the insulation layer, the heat exchange area between the drain pipe and the freezer, and the second temperature difference; wherein the cooling capacity is positively correlated with the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner tank surface of the freezer, the thermal conductivity of the insulation layer of the freezer, the heat exchange area between the drain pipe and the freezer, and the second temperature difference, and is negatively correlated with the thickness of the insulation layer.

[0096] Specifically, this embodiment defines the calculation method of the cooling capacity transferred from the freezing chamber to the drain pipe in the latest set time period. Figure 7 , Figure 7 is a third working flow diagram of the controller provided in an embodiment of the present invention, wherein the controller is further configured to execute steps S18 to S19:

[0097] S18, calculating a second temperature difference between the pipeline temperature and the compartment temperature, and then proceeding to step S19.

[0098] S19. Calculate the amount of cooling transferred from the freezer compartment to the drain pipe during the most recent set time period based on the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner liner surface of the freezer compartment, the thermal conductivity of the insulation layer of the freezer compartment, the thickness of the insulation layer, the heat exchange area between the drain pipe and the freezer compartment, and the second temperature difference.

[0099] Specifically, see Figure 8The heat transfer diagram shown in the figure shows that the left side is the drain pipe, whose pipe temperature is T1 and the convection heat transfer coefficient inside the drain pipe is α1; the right side is the freezer, whose compartment temperature is TP and the convection heat transfer coefficient of the inner surface of the freezer is α2; the heat exchange area between the drain pipe and the freezer is A2, the thickness of the insulation layer between the freezer and the drain pipe is d, and the thermal conductivity of the insulation layer is λ. It is worth noting that the insulation layer is the refrigerator foam material. Figure 8 In the example, the freezer compartment temperature is lower than the drain pipe temperature, so heat is transferred from the drain pipe to the freezer compartment. This means the freezer compartment transfers cold energy to the drain pipe. The specific calculation method for the cold energy transferred from the freezer compartment to the drain pipe during the most recently set time period is as follows: First, subtract the drain pipe temperature T1 from the freezer compartment temperature TP to obtain a second temperature difference ΔT2. Then, based on basic heat transfer theory, the cold energy Q1 transferred from the freezer compartment to the drain pipe during the most recently set time period is calculated based on the second temperature difference ΔT2, taking into account the thermal resistance parameters: the convection heat transfer coefficient α1 inside the drain pipe, the convection heat transfer coefficient α2 on the freezer compartment's inner surface, the heat exchange area A2 between the drain pipe and the freezer compartment, the thickness d of the insulation layer between the freezer compartment and the drain pipe, and the thermal conductivity λ of the insulation layer.

[0100] In a preferred embodiment, the amount of cold transferred from the freezer to the drain pipe in the most recent set time period is calculated based on the convective heat transfer coefficient inside the drain pipe, the convective heat transfer coefficient of the inner liner surface of the freezer, the thermal conductivity of the insulation layer, the thickness of the insulation layer, the heat exchange area between the drain pipe and the freezer, and the second temperature difference, including: adding the reciprocal of the quotient of the convective heat transfer coefficient inside the drain pipe, the reciprocal of the convective heat transfer coefficient of the inner liner surface of the freezer, the thickness of the insulation layer, and the thermal conductivity of the insulation layer, and taking the reciprocal to obtain a total heat transfer coefficient; multiplying the total heat transfer coefficient, the heat exchange area between the drain pipe and the freezer, and the second temperature difference to obtain the amount of cold transferred from the freezer to the drain pipe in the most recent set time period.

[0101] Specifically, this embodiment further limits the calculation method of the cooling capacity transferred from the freezing chamber to the drain pipe in the most recent set time period, and provides a specific calculation formula:

[0102]

[0103] Q1=K×A2×ΔT2×t

[0104] Where Q1 is the cooling capacity transferred from the freezer compartment to the drain pipe during the most recent set time period, K is the total heat transfer coefficient, α1 is the convection heat transfer coefficient inside the drain pipe, α2 is the convection heat transfer coefficient of the freezer compartment's inner surface, d is the thickness of the insulation layer between the freezer compartment and the drain pipe, λ is the thermal conductivity of the insulation layer, A2 is the heat exchange area between the drain pipe and the freezer compartment, and t is the duration of the most recent set time period.

[0105] In a preferred embodiment, the controller is used to control the operating parameters of the heating wire in the following manner: when the heat is greater than or equal to the sum of the cooling amount and the heat demand, the heating wire is not turned on; when the heat is less than the sum of the cooling amount and the heat demand, the heating wire is controlled to turn on.

[0106] For example, see Figure 9 , Figure 9 is a fourth working flow diagram of the controller provided in an embodiment of the present invention, wherein the controller is further configured to execute steps S20 to S23:

[0107] S20, adding the cooling capacity Q1 transferred from the freezing chamber to the drain pipe and the heat demand Q2 of the drain pipe to obtain the energy gap, and then proceeding to step S21.

[0108] S21. Determine whether the heat Q3 transferred from the target heat pipe to the drain pipe is greater than or equal to the energy gap, that is, determine whether the following condition is met: Q3 ≥ (Q1 + Q2). If so, proceed to step S22; if not, proceed to step S23.

[0109] S22, the heating wire is not turned on.

[0110] S23, control the heating wire to turn on.

[0111] It is worth noting that the energy gap is the sum of the cooling energy Q1 transferred from the freezer to the drain pipe and the heat demand Q2 of the drain pipe. When adding, only the difference between the energy and zero is considered, without any positive or negative signs. In this embodiment, the operation of the heating wire is controlled by considering whether the heat provided by the target heat pipe can offset the cooling energy provided by the freezer and meet the heat demand of the drain pipe. When the heat provided by the target heat pipe can offset the cooling energy provided by the freezer and meet the heat demand of the drain pipe, the heating wire does not need to be turned on, thus avoiding energy waste. When the heat provided by the target heat pipe cannot offset the cooling energy provided by the freezer and meet the heat demand of the drain pipe, the heating wire is turned on to heat the drain pipe to prevent ice from forming inside the drain pipe.

[0112] In one embodiment, when the heat is less than the sum of the cooling capacity and the heat demand, controlling the heating wire to turn on includes: when the heat is less than the sum of the cooling capacity and the heat demand, controlling the heating wire to operate at a target start-up rate; wherein, the target start-up rate is calculated in the following manner: obtaining the amount of heat that the heating wire can provide per unit time; wherein, the unit time is equal to the length of the most recently set time period; adding the cooling capacity and the heat demand and subtracting the heat to obtain an energy difference; dividing the energy difference by the amount of heat that the heating wire can provide per unit time to obtain the target start-up rate.

[0113] Specifically, when the heat transferred by the target heat pipe to the drain pipe is insufficient to offset the cold transferred by the freezer to the drain pipe and to meet the heat demand of the drain pipe, it is necessary to control the operation of the heating wire to heat the drain pipe to prevent ice from forming inside the drain pipe. Furthermore, in order to minimize energy waste, the target start-up rate is determined based on the energy transferred to the drain pipe and the heat demand of the drain pipe to control the drain pipe. For example, see Figure 10 , Figure 10 5 is a fifth working flow diagram of the controller provided in an embodiment of the present invention, wherein the controller is further configured to execute steps S24 to S26:

[0114] S24, obtaining the amount of heat that the heating wire can provide per unit time, and then proceeding to step S25;

[0115] Specifically, the heating wire power Pt and the loss coefficient are obtained, and the heating wire power Pt is divided by the loss coefficient to determine the heat Q4 that the heating wire can provide per unit time. Optionally, the empirical value of the loss coefficient is 1.2, which can be adjusted according to actual conditions and is not limited here.

[0116] S25, adding the cooling capacity and the heat demand and subtracting the heat demand to obtain an energy difference, and then proceeding to step S26;

[0117] S26. Divide the energy difference by the amount of heat that the heating wire can provide per unit time to obtain the target startup rate.

[0118] Assuming that the target heat pipe is a condenser, the most recently set period is the period after the first defrost and the most recent compressor operation period. In this embodiment, if Q3 ≥ (Q1 + Q2), the heating wire of the drain pipe will not be turned on during the compressor shutdown period; if Q3 < (Q1 + Q2), the heating wire of the drain pipe will be turned on at a rate of η = (Q1 + Q2 - Q3) / Q4 during the compressor shutdown period; wherein Q1 is the cooling capacity transferred from the freezer to the drain pipe, Q2 is the heat demand of the drain pipe, Q3 is the heat transferred from the target heat pipe to the drain pipe, and Q4 is the heat that the heating wire can provide per unit time. Optionally, the target on-rate can be calculated after determining various energies, or after determining that Q3 < (Q1 + Q2). The specific calculation timing can be set according to actual needs and is not limited here.

[0119] In a preferred embodiment, the controller is used to obtain the pipe temperature by: determining the pipe temperature of the drain pipe according to the compartment temperature of the freezer based on a preset temperature mapping relationship; wherein the temperature mapping relationship is obtained by fitting the freezing temperature of the freezer and the drain pipe temperature; wherein the freezing temperature and the drain pipe temperature are measured when the heating wire is not working and the target heat pipe does not provide heat to the drain pipe.

[0120] Specifically, during the test phase, a temperature detection device is provided for the drain pipe to detect the temperature of the drain pipe (preferably, the temperature of the internal space of the drain pipe, optionally, the temperature of the drain pipe surface). When the heating wire and the target heat pipe do not provide heat to the drain pipe, the freezing temperature of the freezer compartment and the temperature of the drain pipe are monitored, and then fitted to obtain a temperature mapping relationship, which is a linear relationship. For example, see the test results of the application product shown in the table below:

[0121] Serial number Freezing temperature Pipe temperature (temperature inside the drain pipe) 1 -13.8 -5.0 2 -17.2 -10.2 3 -20.8 -15.7 4 -24.5 -21.3 5 -30.8 -30.0

[0122] According to the test results, the fitting formula is obtained: Tp = 1.494T1 + 15.497; where Tp is the compartment temperature of the freezer compartment and T1 is the pipe temperature of the drain pipe.

[0123] In a preferred embodiment, the most recently set time period is the period of most recent compressor operation after the first defrost of the refrigerator, the compartment temperature of the freezer is the real-time temperature of the freezer after the most recently set time period or the average temperature of the freezer during the most recently set time period, and the target heat pipe includes at least one of a condenser, an anti-condensation tube, and a pressure reducer.

[0124] For example, the controller's operating logic is introduced by taking the most recent set time period, which is the most recent compressor operation period after the refrigerator's first defrost, as an example: 1. Detect whether the first defrost is completed. Before the first defrost, there is no defrost water inside the drain pipe, and there will be no ice problem. At this time, the drain pipe heating does not need to be turned on. 2. If the first defrost is completed, determine whether the compressor is turned on. If the compressor is turned on, read the real-time temperature of the freezer compartment detected by the freezing temperature detection device at a certain interval until the compressor stops. Calculate the average temperature of the freezer compartment based on the temperatures of all compartments in the freezer compartment read during this period, and record the compressor operation time t1. It is worth noting that the freezer compartment temperature reading interval should be as short as possible. The shorter the interval, the closer the average temperature of the freezer compartment is to the actual situation. However, it is necessary to take into account the capacity and calculation of the control chip. The reading time is usually selected to be 1 minute or 30 seconds. The specific value is set according to the actual situation and is not limited here. 3. ① According to the preset temperature mapping relationship, determine the temperature of the internal space of the drain pipe (i.e., the pipe temperature) according to the average temperature of the freezer, and calculate the cold amount Q1 conducted from the freezer to the inside of the drain pipe based on the basic theory of heat transfer; ② Calculate the heat Q2 = cm(T0-T1) required to heat the drain pipe to the target temperature T0, where c is the specific heat capacity of air, m is the air mass, and T0 is the target temperature; ③ Calculate the heat Q3 generated by the target heat pipe heating the drain pipe during the operation of the compressor; ④ Calculate the heat Q4 that the heating wire can provide per unit time. 4. If Q3 ≥ (Q1+Q2), the drainage pipe heating wire will not be turned on during the compressor shutdown; if Q3 < (Q1+Q2), the drainage pipe heating wire will be turned on at a rate of η = (Q1+Q2-Q3) / Q4 during the compressor shutdown. 5. When the compressor is detected to start again, the drain pipe heating wire stops working. The real-time temperature of the freezer compartment is measured at regular intervals until the compressor stops. The new average temperature of the freezer compartment is calculated. At the same time, the compressor running time t2 is recorded and steps 3 and 4 are repeated. The following are relevant experimental data:

[0125] In this example, the preset heating wire on-rate before improvement is:

[0126] Ambient temperature Te≤14℃ 14℃<Te≤28℃ 28℃<Te≤35℃ 35℃<Te Default power-up rate 40％ 30％ 15％ 0％

[0127] At an ambient temperature of 25°C and a refrigerator compartment position of 5 / -20, the data before and after the control logic adjustment are compared as follows:

[0128]

[0129]

[0130] When the ambient temperature is 10℃ and the refrigerator compartment is at 5 / -20, the data before and after the control logic adjustment are compared as follows:

[0131]

[0132] Note: The nominal power consumption of the refrigerator is 0.95 kW·h / 24 hours. The traditional control logic refers to the control logic that operates the heater coil in conjunction with the compressor. "Optimized in this example" refers to the controller control method used in this embodiment. The experimental data above demonstrates that the refrigerator control method described in this embodiment maintains a temperature above zero in the middle of the drain pipe, preventing ice from forming inside the pipe while also reducing energy consumption.

[0133] Compared with the prior art, the refrigerator disclosed in the embodiment of the present invention first obtains the following data: the ambient temperature of the refrigerator, the first thermal resistance parameter (the thermal resistance parameter between the condenser and the drain pipe), the second thermal resistance parameter (the thermal resistance parameter between the freezer and the drain pipe), the compartment temperature of the freezer, and the pipe temperature of the drain pipe. The drain pipe is used to guide the water generated by the defrosting of the refrigerator's evaporator to the water receiving box of the refrigerator; then performs energy transfer calculation: by calculating the heat transferred to the drain pipe by the condenser in the most recent set time period based on the first thermal resistance parameter, the ambient temperature, and the pipe temperature; by calculating the cooling capacity transferred to the drain pipe by the freezer in the most recent set time period based on the second thermal resistance parameter, the pipe temperature, and the compartment temperature; then determines the control demand: calculates the heat demand based on the pipe temperature and the preset target temperature; finally, dynamically adjusts the operating parameters of the heating wire near the drain pipe based on the calculated cooling capacity, heat capacity, and heat demand. It can be seen that the embodiment of the present invention reduces energy waste while ensuring that the drain pipe is not blocked by controlling the operating parameters of the heating wire based on the cooling capacity transferred to the drain pipe by the freezer, the heat transferred to the drain pipe by the condenser, and the heat demand of the drain pipe.

[0134] See also Figure 11 , Figure 11 1 is a flow chart of a refrigerator control method provided by an embodiment of the present invention. The refrigerator control method according to the embodiment of the present invention is implemented by a controller in the refrigerator, and includes steps S1 to S5:

[0135] S1. Obtaining the ambient temperature of a refrigerator, a first thermal resistance parameter, a second thermal resistance parameter, a compartment temperature of a freezer compartment of the refrigerator, and a pipe temperature of a drain pipe; the first thermal resistance parameter is the thermal resistance parameter between the heat dissipation unit of the refrigerator and the drain pipe, and the second thermal resistance parameter is the thermal resistance parameter between the freezer compartment and the drain pipe. The drain pipe is used to guide water generated by defrosting the refrigerator's evaporator to a water receiving box of the refrigerator;

[0136] S2. Calculating the amount of heat transferred from the heat dissipation unit to the drain pipe in a recent set time period based on the first thermal resistance parameter, the ambient temperature, and the pipe temperature;

[0137] S3, calculating the cooling capacity transferred from the freezing chamber to the drain pipe during the most recent set time period based on the second thermal resistance parameter, the pipe temperature, and the compartment temperature;

[0138] S4. Calculating heat demand based on the pipeline temperature and a preset target temperature;

[0139] S5. Controlling operating parameters of a heating wire disposed near the drain pipe according to the cooling capacity, the heating capacity, and the heat demand.

[0140] In one embodiment, the first thermal resistance parameter includes a natural surface heat transfer coefficient and a heat exchange area between the drain pipe and the target heat pipe; the amount of heat transferred from the target heat pipe to the drain pipe during the most recently set time period is obtained by:

[0141] calculating a first temperature difference between the ambient temperature and the pipeline temperature;

[0142] The amount of heat transferred from the target heat pipe to the drain pipe during the most recent set time period is calculated based on the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the length of the most recent set time period; wherein the heat is positively correlated with the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the length of the most recent set time period, respectively.

[0143] In one embodiment, the calculating the amount of heat transferred by the target heat pipe to the drain pipe in the most recent set time period based on the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the duration of the most recent set time period includes:

[0144] The heat transferred from the target heat pipe to the drain pipe in the most recent set time period is obtained by multiplying the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the duration of the most recent set time period.

[0145] In one embodiment, the second thermal resistance parameter includes the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner surface of the freezer compartment, the thermal conductivity of the insulation layer between the freezer compartment and the drain pipe, the thickness of the insulation layer, and the heat exchange area between the drain pipe and the freezer compartment;

[0146] The cooling capacity transferred from the freezing chamber to the drain pipe during the most recent set time period is obtained in the following manner:

[0147] Calculating a second temperature difference between the pipeline temperature and the compartment temperature;

[0148] The amount of cold transferred from the freezer compartment to the drain pipe during a recent set time period is calculated based on the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient on the inner liner surface of the freezer compartment, the thermal conductivity of the insulation layer, the thickness of the insulation layer, the heat exchange area between the drain pipe and the freezer compartment, and the second temperature difference; wherein the cold amount is positively correlated with the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient on the inner liner surface of the freezer compartment, the thermal conductivity of the insulation layer, the heat exchange area between the drain pipe and the freezer compartment, and the second temperature difference, and the cold amount is negatively correlated with the thickness of the insulation layer.

[0149] In one embodiment, the calculating the cooling capacity transferred from the freezer compartment to the drain pipe during the most recent set time period based on the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner tank surface of the freezer compartment, the thermal conductivity of the insulation layer, the thickness of the insulation layer, the heat exchange area between the drain pipe and the freezer compartment, and the second temperature difference includes:

[0150] The total heat transfer coefficient is obtained by adding the reciprocal of the convection heat transfer coefficient inside the drain pipe, the reciprocal of the convection heat transfer coefficient on the surface of the inner container of the freezing chamber, the thickness of the insulation layer and the thermal conductivity of the insulation layer, and taking the reciprocal.

[0151] The total heat transfer coefficient, the heat exchange area between the drain pipe and the freezing chamber, and the second temperature difference are multiplied together to obtain the cooling capacity transferred from the freezing chamber to the drain pipe in the most recent set time period.

[0152] In one embodiment, the operating parameters of the heating wire are controlled by:

[0153] When the heat is greater than or equal to the sum of the cooling capacity and the heat demand, the heating wire is not turned on;

[0154] When the heat is less than the sum of the cooling capacity and the heat demand, the heating wire is controlled to turn on.

[0155] In one embodiment, when the heat is less than the sum of the cooling capacity and the heat demand, controlling the heating wire to turn on includes:

[0156] When the heat is less than the sum of the cooling capacity and the heat demand, controlling the heating wire to operate at a target operating rate;

[0157] The target availability is calculated as follows:

[0158] Obtaining the amount of heat that the heating wire can provide per unit time; wherein the unit time is equal to the length of the most recently set time period;

[0159] Add the cooling capacity and the heat demand and then subtract the heat demand to obtain an energy difference;

[0160] The target on-rate is obtained by dividing the energy difference by the amount of heat that the heating wire can provide per unit time.

[0161] In one embodiment, the pipeline temperature is obtained by:

[0162] Based on a preset temperature mapping relationship, determining the pipe temperature of the drain pipe according to the compartment temperature of the freezing chamber;

[0163] The temperature mapping relationship is obtained by fitting the freezing temperature of the freezer compartment and the drain pipe temperature; the freezing temperature and the drain pipe temperature are measured when the heating wire is not working and the target heat pipe does not provide heat to the drain pipe.

[0164] In one embodiment, the most recently set time period is the period of most recent compressor operation after the first defrost of the refrigerator, the compartment temperature of the freezer is the real-time temperature of the freezer after the most recently set time period or the average temperature of the freezer during the most recently set time period, and the target heat pipe includes at least one of a condenser, an anti-condensation pipe, and a pressure reducer.

[0165] It is worth noting that the specific steps of the method described in the above embodiment can be found in the working process of the refrigerator in the above embodiment, and will not be described in detail here.

[0166] Compared with the prior art, the refrigerator control method disclosed in the embodiment of the present invention first obtains the following data: the ambient temperature of the refrigerator, the first thermal resistance parameter (the thermal resistance parameter between the condenser and the drain pipe), the second thermal resistance parameter (the thermal resistance parameter between the freezer and the drain pipe), the compartment temperature of the freezer and the pipe temperature of the drain pipe, and the drain pipe is used to guide the water generated by the defrosting of the evaporator of the refrigerator to the water receiving box of the refrigerator; then performs energy transfer calculation: the heat transferred to the drain pipe by the condenser in the most recent set time period is calculated based on the first thermal resistance parameter, the ambient temperature and the pipe temperature; the cooling amount transferred to the drain pipe by the freezer in the most recent set time period is calculated based on the second thermal resistance parameter, the pipe temperature and the compartment temperature; then determines the control demand: the heat demand is calculated based on the pipe temperature and the preset target temperature; finally, according to the calculated cooling amount, heat amount and heat demand, the operating parameters of the heating wire near the drain pipe are dynamically adjusted. It can be seen from this that the embodiment of the present invention controls the operating parameters of the heating wire according to the cold amount transferred from the freezer to the drain pipe, the heat transferred from the condenser to the drain pipe, and the heat demand of the drain pipe, thereby reducing energy waste while ensuring that the drain pipe is not blocked.

[0167] The above is a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present invention. These improvements and modifications are also considered to be within the scope of protection of the present invention.

Claims

1. A refrigerator, characterized in that: include: Freezer, for storing items; A refrigeration system for providing power for the refrigerator's refrigeration cycle, comprising a compressor, an evaporator, and a heat dissipation unit; a target heat pipe in the heat dissipation unit is also used to provide heat to a drain pipe, and the target heat pipe is located near the drain pipe; The drain pipe is used to connect the evaporator and the water receiving box, and is used to guide the water generated by the defrosting of the evaporator to the water receiving box; a heating wire, disposed near the drain pipe and used for heating the drain pipe; The ambient temperature detection device is installed on the refrigerator shell and is used to detect the ambient temperature; A freezing temperature detection device is provided in the freezing chamber and is used to detect the real-time temperature of the freezing chamber; Controller for: Acquire the ambient temperature, a first thermal resistance parameter, a second thermal resistance parameter, a compartment temperature of the freezing chamber, and a pipe temperature of the drain pipe; the first thermal resistance parameter is the thermal resistance parameter between the target heat pipe and the drain pipe, and the second thermal resistance parameter is the thermal resistance parameter between the freezing chamber and the drain pipe; Calculating the amount of heat transferred from the target heat pipe to the drain pipe in a recent set time period according to the first thermal resistance parameter, the ambient temperature, and the pipe temperature; Calculating the cooling capacity transferred from the freezing chamber to the drain pipe during the most recent set time period based on the second thermal resistance parameter, the pipe temperature, and the compartment temperature; Calculating heat demand based on the pipeline temperature and a preset target temperature; The operating parameters of the heating wire are controlled according to the cooling capacity, the heating capacity and the heat demand.

2. The refrigerator according to claim 1, wherein The first thermal resistance parameter includes a natural surface heat transfer coefficient and a heat exchange area between the drain pipe and the target heat pipe; The controller is configured to calculate the amount of heat transferred from the target heat pipe to the drain pipe during the most recent set time period by: calculating a first temperature difference between the ambient temperature and the pipeline temperature; The amount of heat transferred from the target heat pipe to the drain pipe during the most recent set time period is calculated based on the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the length of the most recent set time period; wherein the heat is positively correlated with the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the length of the most recent set time period, respectively.

3. The refrigerator according to claim 2, wherein: The calculating, based on the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the duration of the most recent set time period, of the amount of heat transferred from the target heat pipe to the drain pipe in the most recent set time period includes: The heat transferred from the target heat pipe to the drain pipe in the most recent set time period is obtained by multiplying the natural surface heat transfer coefficient, the heat exchange area between the drain pipe and the target heat pipe, the first temperature difference, and the duration of the most recent set time period.

4. The refrigerator according to claim 1, wherein The second thermal resistance parameter includes the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner tank surface of the freezing chamber, the thermal conductivity of the insulation layer between the freezing chamber and the drain pipe, the thickness of the insulation layer, and the heat exchange area between the drain pipe and the freezing chamber; The controller is used to calculate the cooling capacity transferred from the freezing chamber to the drain pipe in the latest set time period by: Calculating a second temperature difference between the pipeline temperature and the compartment temperature; The amount of cold transferred from the freezer compartment to the drain pipe during a recent set time period is calculated based on the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient on the inner liner surface of the freezer compartment, the thermal conductivity of the insulation layer, the thickness of the insulation layer, the heat exchange area between the drain pipe and the freezer compartment, and the second temperature difference; wherein the cold amount is positively correlated with the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient on the inner liner surface of the freezer compartment, the thermal conductivity of the insulation layer, the heat exchange area between the drain pipe and the freezer compartment, and the second temperature difference, and the cold amount is negatively correlated with the thickness of the insulation layer.

5. The refrigerator according to claim 4, wherein: The calculating, based on the convection heat transfer coefficient inside the drain pipe, the convection heat transfer coefficient of the inner tank surface of the freezer compartment, the thermal conductivity of the insulation layer, the thickness of the insulation layer, the heat exchange area between the drain pipe and the freezer compartment, and the second temperature difference, of the cooling capacity transferred from the freezer compartment to the drain pipe in the most recent set time period includes: The total heat transfer coefficient is obtained by adding the reciprocal of the convection heat transfer coefficient inside the drain pipe, the reciprocal of the convection heat transfer coefficient on the surface of the inner container of the freezing chamber, the thickness of the insulation layer and the thermal conductivity of the insulation layer, and taking the reciprocal. The total heat transfer coefficient, the heat exchange area between the drain pipe and the freezing chamber, and the second temperature difference are multiplied together to obtain the cooling capacity transferred from the freezing chamber to the drain pipe in the most recent set time period.

6. The refrigerator according to claim 1, wherein The controller is used to control the operating parameters of the heating wire in the following manner: When the heat is greater than or equal to the sum of the cooling capacity and the heat demand, the heating wire is not turned on; When the heat is less than the sum of the cooling capacity and the heat demand, the heating wire is controlled to turn on.

7. The refrigerator according to claim 6, wherein When the heat amount is less than the sum of the cooling amount and the heat demand, controlling the heating wire to turn on includes: When the heat is less than the sum of the cooling capacity and the heat demand, controlling the heating wire to operate at a target operating rate; The target availability is calculated as follows: Obtaining the amount of heat that the heating wire can provide per unit time; wherein the unit time is equal to the length of the most recently set time period; Add the cooling capacity and the heat demand and then subtract the heat demand to obtain an energy difference; The target on-rate is obtained by dividing the energy difference by the amount of heat that the heating wire can provide per unit time.

8. The refrigerator according to claim 1, wherein The controller is used to obtain the pipeline temperature by: Based on a preset temperature mapping relationship, determining the pipe temperature of the drain pipe according to the compartment temperature of the freezing chamber; The temperature mapping relationship is obtained by fitting the freezing temperature of the freezer compartment and the drain pipe temperature; the freezing temperature and the drain pipe temperature are measured when the heating wire is not working and the target heat pipe does not provide heat to the drain pipe.

9. The refrigerator according to any one of claims 1 to 8, characterized in that: The most recently set time period is the period of compressor operation most recently after the first defrost of the refrigerator, the compartment temperature of the freezer compartment is the real-time temperature of the freezer compartment after the most recently set time period or the average temperature of the freezer compartment during the most recently set time period, and the target heat pipe includes at least one of a condenser, an anti-condensation pipe, and a pressure reducer.

10. A refrigerator control method, characterized in that: include: Obtaining a refrigerator's ambient temperature, a first thermal resistance parameter, a second thermal resistance parameter, a compartment temperature of the refrigerator's freezer compartment, and a pipe temperature of a drain pipe; the first thermal resistance parameter is the thermal resistance parameter between a target heat pipe in the refrigerator's heat dissipation unit and the drain pipe; the second thermal resistance parameter is the thermal resistance parameter between the freezer compartment and the drain pipe, which is used to guide water generated by defrosting the refrigerator's evaporator to a water receiving box of the refrigerator; Calculating the amount of heat transferred from the target heat pipe to the drain pipe in a recent set time period according to the first thermal resistance parameter, the ambient temperature, and the pipe temperature; Calculating the cooling capacity transferred from the freezing chamber to the drain pipe during the most recent set time period based on the second thermal resistance parameter, the pipe temperature, and the compartment temperature; Calculating heat demand based on the pipeline temperature and a preset target temperature; The operating parameters of the heating wire arranged near the drain pipe are controlled according to the cooling capacity, the heating capacity and the heat demand.

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