A defrosting method, apparatus, equipment and medium for air source units based on gas-electric complementary technology

Abstract

This invention relates to the field of equipment defrosting technology, specifically to a defrosting method, apparatus, equipment, and medium for air-source heat pump units based on gas-electric complementary systems. The invention first predicts the frost risk factor, and then determines whether to use an anti-frost mode or a defrost mode based on the frost risk factor and the pipe wall temperature of the outdoor heat exchanger. In both modes, the gas-fired heating equipment provides heat to the air-source heat pump unit, rather than consuming the heat from the indoor space served by the air-source heat pump unit. Therefore, this invention ensures normal heating demand while performing anti-frost and defrost operations on the outdoor heat exchanger. Furthermore, the invention incorporates preventative measures before frost formation to minimize or delay frost formation, thereby enabling the air-source heat pump unit to maintain normal heating function.

Description

Technical Field

[0001] This invention relates to the field of equipment defrosting technology, specifically to a defrosting method, apparatus, equipment, and medium for air source units based on gas-electric complementary technology. Background Technology

[0002] When an air source heat pump unit provides indoor heating, it absorbs heat from the outside to supply heat to the room. However, when the outdoor heat exchanger of the air source heat pump unit frosts, the unit will absorb heat from the room to defrost the outdoor heat exchanger. This heat absorption lowers the indoor temperature, leading to abnormal heating. For example, when the air source heat pump unit is an air source heat pump, the outdoor heat exchanger acts as an evaporator. The liquid refrigerant inside the outdoor heat exchanger absorbs heat from the outside air and evaporates into a gaseous state. The compressor then delivers the gaseous refrigerant to the indoor heat exchanger (which acts as a condenser). The gaseous refrigerant liquefies in the indoor heat exchanger, releasing heat into the room during this process to raise the indoor temperature. When the outdoor heat exchanger frosts, current technology switches the outdoor heat exchanger to a condenser and the indoor heat exchanger to an evaporator to absorb heat from the room to defrost the outdoor heat exchanger. This results in a decrease in indoor temperature, affecting the user's heating needs.

[0003] In summary, existing technologies lower the indoor temperature while defrosting air source heat pump units.

[0004] Therefore, existing technologies still need to be improved and enhanced. Summary of the Invention

[0005] To address the aforementioned technical problems, this invention provides a defrosting method, apparatus, equipment, and medium for air source units based on gas-electric complementarity, which solves the problem of reducing indoor temperature while defrosting air source units in existing technologies.

[0006] To achieve the above objectives, the present invention adopts the following technical solution: In a first aspect, the present invention provides a defrosting method for an air-source generator unit based on gas-electric complementarity, comprising: Predict the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located, collect the pipe wall temperature of the outdoor heat exchanger in real time, and determine the frost risk factor of the outdoor heat exchanger based on the frost point temperature and the pipe wall temperature. Based on the frost risk factor and the pipe wall temperature, the defrosting mode provided by the gas heating equipment for the outdoor heat exchanger is determined. Based on the defrosting mode, the heat supplied by the gas heating equipment to the air source unit is controlled.

[0007] In one implementation, predicting the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located includes: Collect the dry-bulb temperature and relative humidity of the current outdoor environment, and predict the frost point temperature based on the dry-bulb temperature and relative humidity; Alternatively, the dry-bulb and wet-bulb temperatures of the current outdoor environment can be collected, and the frost point temperature can be predicted based on the dry-bulb and wet-bulb temperatures.

[0008] In one implementation, determining the defrosting mode provided by the gas heating equipment for the outdoor heat exchanger based on the frosting risk factor and the pipe wall temperature includes: When the frost risk factor is less than or equal to the safety threshold and greater than zero, the gas heating equipment is controlled to provide an anti-frost mode for the outdoor heat exchanger. The anti-frost mode means that the gas heating equipment delivers heat to the outdoor heat exchanger so that the pipe wall temperature rises to the anti-frost temperature. Alternatively, when the frost risk factor is less than or equal to zero and the pipe wall temperature is less than or equal to zero degrees, the gas heating equipment is controlled to provide a defrost mode for the outdoor heat exchanger.

[0009] One implementation also includes: When the gas heating equipment provides the anti-frost mode for the outdoor heat exchanger, the intake superheat of the air source unit is monitored in real time. When the intake superheat is continuously less than the target value, the gas heating equipment is switched from the anti-frost mode to the dynamic load compensation mode. The dynamic load compensation mode represents adjusting the heat load of the gas heating equipment in real time based on the intake superheat. Alternatively, when the gas heating equipment provides the defrosting mode for the outdoor heat exchanger, the intake superheat of the air source unit is monitored. When the intake superheat is continuously less than the target value, the gas heating equipment is switched from the defrosting mode to the dynamic load compensation mode.

[0010] In one implementation, under the dynamic load compensation mode, determining the heat load that the gas heating equipment needs to share includes: Based on the target value and the inhalation superheat, the inhalation superheat deviation is determined; Determine the derivative of the pipe wall temperature with respect to time and the integral of the intake superheat deviation with respect to time; Based on the intake superheat deviation, the differential, and the integral, the heat load to be shared by the gas heating equipment is determined.

[0011] In one implementation, under the dynamic load compensation mode, the gas heating equipment and the air source unit are controlled to jointly bear the total heat load required to raise the intake superheat to the target value, wherein controlling the air source unit to output its share of the heat load includes: The target heating capacity of the air source unit is determined based on the heat load that the air source unit needs to share. Based on prior knowledge, the target frequency of the compressor of the air source unit corresponding to the target heating capacity is determined; The compressor is controlled to operate at the target frequency in order to control the air source unit to output the heat load it needs to share.

[0012] In one implementation, under the dynamic load compensation mode, when the compressor is controlled to operate at the target frequency, the compressor fan is controlled to operate at a target speed so that the fan speed matches the target frequency of the compressor, wherein determining the target speed includes: Based on the aforementioned intake superheat deviation, the target correction amount for the fan speed is determined; The target rotational speed is obtained based on the target correction amount and the reference rotational speed of the wind turbine.

[0013] Secondly, embodiments of the present invention also provide a defrosting device for an air-source unit based on gas-electric complementarity, wherein the device comprises the following components: The frost risk prediction module is used to predict the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located, collect the pipe wall temperature of the outdoor heat exchanger in real time, and determine the frost risk factor of the outdoor heat exchanger based on the frost point temperature and the pipe wall temperature. The mode determination module is used to determine the anti-defrosting mode provided by the gas heating equipment for the outdoor heat exchanger based on the frost risk factor and the pipe wall temperature. The control module is used to control the heat provided by the gas heating equipment to the air source unit based on the defrosting mode.

[0014] Thirdly, embodiments of the present invention also provide a terminal device, wherein the terminal device includes a memory, a processor, and a defrosting program for an air source unit based on gas-electric complementarity stored in the memory and executable on the processor. When the processor executes the defrosting program for an air source unit based on gas-electric complementarity, it implements the steps of the defrosting method for an air source unit based on gas-electric complementarity described above.

[0015] Fourthly, embodiments of the present invention also provide a computer-readable storage medium storing a defrosting program for an air source unit based on gas-electric complementarity. When the defrosting program for an air source unit based on gas-electric complementarity is executed by a processor, it implements the steps of the defrosting method for an air source unit based on gas-electric complementarity described above.

[0016] Beneficial effects: This invention first predicts the frost risk factor, and then determines whether to use anti-frost mode or defrost mode based on the frost risk factor and the pipe wall temperature of the outdoor heat exchanger. In both anti-frost and defrost modes, the gas heating equipment provides heat to the air source unit, rather than consuming the heat from the indoor space served by the air source unit. Therefore, this invention ensures normal heating demand while performing anti-frost and defrost operations on the outdoor heat exchanger. Furthermore, this invention incorporates preventative measures before frost forms to minimize or delay frost formation, thereby enabling the air source unit to maintain normal heating function. Attached Figure Description

[0017] Figure 1 This is an overall flowchart of the present invention; Figure 2 A structural diagram of a defrosting device for an air-source generator unit based on gas-electric complementarity provided by the present invention; Figure 3 This is a block diagram illustrating the internal structure of a terminal device provided in an embodiment of the present invention. Detailed Implementation

[0018] The technical solutions of the present invention will be clearly and completely described below with reference to the embodiments and accompanying drawings. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0019] Research has found that when air source heat pump units provide indoor heating, they absorb heat from the outside to supply heat to the inside. When the outdoor heat exchanger of the air source heat pump unit frosts, the unit will absorb heat from the inside to defrost the outdoor heat exchanger. This heat absorption from the inside lowers the indoor temperature, leading to abnormal indoor heating. For example, when the air source heat pump unit is an air source heat pump, the outdoor heat exchanger acts as an evaporator. The liquid refrigerant inside the outdoor heat exchanger absorbs heat from the outside air and evaporates into a gaseous state. The compressor then delivers the gaseous refrigerant to the indoor heat exchanger (which acts as a condenser). The gaseous refrigerant liquefies into a liquid state in the indoor heat exchanger, releasing heat into the room during the liquefaction process to raise the indoor temperature. When the outdoor heat exchanger frosts, current technology switches the outdoor heat exchanger to a condenser and the indoor heat exchanger to an evaporator to absorb heat from the inside to defrost the outdoor heat exchanger. This results in a decrease in indoor temperature, affecting users' heating needs.

[0020] To address the aforementioned technical problems, this invention provides a defrosting method, apparatus, equipment, and medium for air source units based on gas-electric complementarity, which solves the problem of reducing indoor temperature while defrosting air source units in existing technologies.

[0021] The defrosting method for air-source heat pump units based on gas-electric complementarity in this embodiment can be applied to terminal equipment, which can be a terminal product with data processing capabilities, such as a computer. In this embodiment, as... Figure 1 As shown, the defrosting method for air-source generator units based on gas-electric complementarity specifically includes the following steps: S100, predict the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located, collect the pipe wall temperature of the outdoor heat exchanger in real time, and determine the frost risk factor of the outdoor heat exchanger based on the frost point temperature and the pipe wall temperature. S200, based on the frost risk factor and the pipe wall temperature, determine the anti-defrosting mode provided by the gas heating equipment for the outdoor heat exchanger; S300, based on the defrosting mode, controls the heat provided by the gas heating equipment to the air source unit.

[0022] The air source unit in this embodiment can be an air source heat pump, or it can be any other heat pump that includes an outdoor heat exchanger and an indoor heat exchanger for heating indoor spaces.

[0023] In one embodiment of this application, steps S100, S200, and S300 are all operations performed after the air source unit is turned on and running. If the air source unit is in a shutdown or standby mode, the shutdown or standby state is maintained.

[0024] In one embodiment of this application, the step S100 of predicting the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located includes: collecting the dry-bulb temperature and relative humidity of the current outdoor environment, and based on the dry-bulb temperature... and the relative humidity Predict the frost point temperature.

[0025] Specifically, calculating dry-bulb temperature Corresponding water surface saturated vapor pressure (Unit: hPa):

[0026] Calculate actual water vapor pressure :

[0027] Calculate the frost point temperature :

[0028] When the frost point temperature It may frost over; when At that time, the water vapor pressure was higher than 0°C above the ice surface. At a saturated vapor pressure of 6.112 hPa, frost will not form; the temperature at this point is the dew point temperature.

[0029] The above is based on the formula for relative humidity. and dry bulb temperature In another embodiment of this application, the frost point temperature can also be predicted based on relative humidity. and dry bulb temperature Using empirical knowledge, the frost point temperature can be deduced.

[0030] The data recorded in Table 1 is used as prior knowledge: Table 1

[0031] Table 1 Represents relative humidity, such as when the dry bulb temperature... The value is 5, relative humidity If the value is 50%, then the frost point temperature is -4.04. The " / " in Table 1 represents the dew point temperature, not the frost point temperature. For example, when the dry bulb temperature... The value is 5 and the relative humidity The value is 80%, which means there will be no frost, so there is no need to calculate the dew point temperature under this condition.

[0032] In this embodiment, linear interpolation is performed on the dry-bulb temperature and relative humidity in Table 1 to obtain more frost point temperatures corresponding to dry-bulb temperature and relative humidity. For example, interpolation between the two dry-bulb temperatures of 2 and 0 yields a new dry-bulb temperature of 1.5. Through linear interpolation, the frost point temperature corresponding to dry-bulb temperature 1.5 and relative humidity is obtained. This is the new frost point temperature at 60%. Linear interpolation is used to obtain more accurate correlations between dry-bulb temperature and relative humidity and frost point temperature.

[0033] The real-time collected dry-bulb temperature and relative humidity were matched with the linearly interpolated dry-bulb temperature and relative humidity in Table 1 to determine the corresponding frost point temperature. .

[0034] In another embodiment of this application, the step S100 of predicting the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located includes: collecting the dry-bulb temperature and wet-bulb temperature of the current outdoor environment, and predicting the frost point temperature based on the dry-bulb temperature and the wet-bulb temperature.

[0035] Specifically, calculate the saturated vapor pressure corresponding to the wet-bulb temperature. :

[0036] In the formula, Represents wet-bulb temperature. The unit is ℃. The unit is hPa.

[0037] Calculate the actual water vapor partial pressure :

[0038] In the formula, Represents dry bulb temperature. The unit is ℃; Represents the wet-bulb and dry-bulb constants, under good ventilation conditions. The value is 6.6 × 10 -4 (℃) -1 ); This represents atmospheric pressure (hPa), with standard atmospheric pressure taken as 1013.25.

[0039] Calculate the frost point temperature :

[0040] In one embodiment of this application, the frost risk factor , This represents the tube wall temperature of the outdoor heat exchanger.

[0041] In one embodiment of this application, the anti-frost mode in step S200 includes an anti-frost mode and a defrost mode.

[0042] When the frost risk factor is less than or equal to the safety threshold and greater than zero, the anti-frost mode is activated, i.e., when 0 ≤ When the anti-frost mode is activated, Represents the safety threshold. The value is 2℃.

[0043] When 0≤ There is a possibility of frost formation, but it is not guaranteed. Therefore, it is necessary to start the gas heating equipment to share the heat load of the air source unit, so that the evaporation pressure of the outdoor heat exchanger can rise, thereby increasing the pipe wall temperature of the outdoor heat exchanger. until In the formula This represents the temperature at which frost is prevented.

[0044] When the anti-frost mode is activated, hot water heated by the gas-fired heating equipment flows into the water-side heat exchanger (i.e., the indoor heat exchanger). This allows the gas-fired heating equipment to share the heating load of the air-source unit, reducing the air-source unit's heating demand and consequently lowering the heat absorption demand of the air-source unit's evaporator (i.e., the outdoor heat exchanger). Once the heat absorption demand of the outdoor heat exchanger decreases, the coil temperature of the outdoor heat exchanger will rise, thus preventing frost formation on the outdoor heat exchanger. The gas-fired heating equipment in this embodiment includes a gas boiler.

[0045] In anti-frost mode, in addition to activating the gas heating equipment to assist in heating the circulating water, the frequency of the air source unit is also reduced to a level that maintains basic circulation (not lower than the minimum allowable frequency). Reducing the frequency of the air source unit decreases the speed of the compressor located between the outdoor and indoor heat exchangers. This reduced compressor speed decreases the amount of refrigerant circulating between the outdoor and indoor heat exchangers. The reduced circulation means less heat is removed from the outdoor heat exchanger, indirectly causing the pipe wall temperature of the outdoor heat exchanger to rise, thus preventing frost formation on the outdoor heat exchanger.

[0046] In anti-frost mode, the gas heating equipment and the air source unit share the heat load, which is related to the indoor heating demand. The proportion of the load shared by the gas heating equipment is... The load ratio of the air source unit .in Represents the degree of proximity to the frost point:

[0047] In one embodiment of this application, when the frosting risk factor is less than or equal to zero and the pipe When the wall temperature is less than or equal to zero degrees Celsius, the defrosting mode is activated. and When the defrost mode is activated, the gas heating equipment heats the hot water at full power (i.e., rated power). This hot water flows into the water heat exchange pipes inside the air-side heat exchanger (i.e., the outdoor heat exchanger) to raise the pipe wall temperature, thereby defrosting the outdoor heat exchanger. The water heat exchange pipes are additional pipes added to the outdoor heat exchanger for defrosting.

[0048] Meanwhile, the four-way valve of the air source unit does not switch, and the electronic expansion valve between the outdoor and indoor heat exchangers is opened to its maximum degree to increase the refrigerant flow. The four-way valve is used to control whether the air source unit provides cooling or heating mode to the indoor unit. The fact that the four-way valve does not switch means that the air source unit continues to provide heating mode to the indoor unit during the defrosting process.

[0049] In another embodiment of this application, a dynamic load compensation mode is provided when the intake superheat... Continuously less than the target value ( When the value is 2K, the dynamic load compensation mode is activated, which lasts for 10 seconds. The dynamic load compensation mode maintains the normal operation of the air source unit while the gas heating equipment shares part of the heat load, and at the same time reduces the speed of the heat pump fan or the frequency of the compressor.

[0050] The dynamic load compensation mode has a higher priority than the anti-frost mode. That is, when the activation conditions of both the anti-frost mode and the dynamic load compensation mode are met at the same time, the dynamic load compensation mode will be activated instead of the anti-frost mode.

[0051] The dynamic load compensation mode has a higher priority than the defrost mode. That is, when the activation conditions of both the defrost mode and the dynamic load compensation mode are met, the dynamic load compensation mode will be activated instead of the defrost mode.

[0052] In dynamic load compensation mode, load ratio is used. The calculation of the heat load to be borne by the gas-fired heating equipment includes: determining the suction superheat deviation based on the target value and the suction superheat; determining the derivative of the pipe wall temperature with respect to time and the integral of the suction superheat deviation with respect to time; and determining the heat load to be borne by the gas-fired heating equipment based on the suction superheat deviation, the derivative, and the integral.

[0053] That is, the load ratio is calculated according to the following formula. :

[0054] In the formula, This indicates a deviation in intake superheat. , This represents the differential of the pipe wall temperature with respect to time. This represents the integral of the intake superheat deviation with respect to time. This is a proportionality coefficient, typically ranging from 0.2 to 2.0. This is the integral coefficient, and its value is usually between 0.01 and 0.1. The differential coefficient typically ranges from 10 to 60.

[0055] In dynamic load compensation mode, load ratio is used. This represents the heat load that the air source heat pump unit needs to handle.

[0056] By controlling the air source unit to operate at a target frequency, the air source unit can provide the heat load it needs to share. The calculation of the target frequency includes: determining the target heating capacity of the air source unit based on the heat load it needs to share; and determining the target frequency of the compressor of the air source unit corresponding to the target heating capacity based on prior knowledge.

[0057] Target heating capacity equals load ratio (Should The rated heating capacity (representing the heat load required by the air source heat pump unit) multiplied by the rated frequency corresponds to the rated heating capacity. There is a correlation between the compressor frequency and the heating capacity of the air source heat pump unit; this correlation is prior knowledge. Therefore, knowing the target heating capacity, based on prior knowledge, the target frequency of the compressor corresponding to the target heating capacity can be determined. Operating the compressor at this target frequency will enable the air source heat pump unit to achieve its load ratio target. This is to enable the air source unit and the gas heating equipment to work together to increase the intake superheat to the target value, which requires a total heat load.

[0058] In this embodiment, the compressor frequency is reduced while the fan frequency is also reduced to reduce the fan speed to the target speed, so that the fan speed matches the target frequency of the compressor. The calculation of the target speed includes: determining the target correction amount of the fan speed based on the suction superheat deviation; and obtaining the target speed based on the target correction amount and the reference speed of the fan.

[0059] In other words, a base speed ratio is set based on the compressor frequency:

[0060] Represents the matching coefficient. The value is 1.0 to 1.2 (because the fan flow rate is directly proportional to the speed, and its effect on the refrigerant flow rate is approximately linear with that of the frequency), with a lower limit of 0.4 to ensure the minimum gas flow rate and prevent frost formation / low pressure protection. Target correction amount is generated using PI control. :

[0061] In the formula, This is the proportionality coefficient. The integral coefficient is... The value is between 0.2 and 2.0. The value is between 0.01 and 0.1.

[0062] Target speed :

[0063] When the intake air is overheated Low (i.e.) (There is a risk of liquid impact) → Positive temperature → Increase fan speed to increase heat exchange in outdoor heat exchanger, allowing droplets to fully vaporize and superheat to recover; when Too high (i.e.) (Evaporation was too complete) → Negative values ​​→ reduce fan speed, decrease heat exchange, and reduce superheat.

[0064] In this embodiment, the relationship between the compressor frequency and the heating capacity of the air source unit is recorded in a table, and the target power is obtained by looking up the data in the table.

[0065] In another embodiment of this application, the target power of the compressor is calculated using the following formula. :

[0066] In the formula, This represents the compressor's minimum operating frequency; To ensure the compressor has sufficient The minimum frequency at which the refrigerant flow returns to the lubricating oil must be maintained; the compressor frequency must not be lower than this value. If Then set The shortfall is entirely covered by gas-fired heating equipment.

[0067] This represents the compressor's rated frequency. The superscript represents the ratio of the target heating capacity to the rated heating capacity of the air source heat pump unit. Represents a nonlinear exponent, derived from fitting experimental data (e.g., when the compressor approximates a square relationship). =0.5, linear relationship =1).

[0068] When the pipe wall temperature Once the temperature rises to 5 degrees Celsius or higher and remains there for 30 seconds, exit defrost / anti-frost mode. Gradually restore the heat pump load, and the gas heating equipment switches back to normal supplementary heating mode (e.g., adjusting the output ratio according to water temperature requirements).

[0069] In summary, this invention calculates the current frost point temperature using dry-bulb / wet-bulb temperatures. If (outdoor heat exchanger tube temperature - frost point temperature) < safety threshold (e.g., 2°C), it indicates that frost is imminent. At this time, defrosting is not initiated because frost has not yet formed. Instead, the gas heating equipment is activated to assist in heating the circulating water flowing into the indoor heat exchanger, increasing the condensing temperature, or the compressor frequency is temporarily reduced. The aim is to raise the surface temperature of the outdoor heat exchanger above the frost point, thereby preventing frost formation or delaying the frost formation time.

[0070] When defrosting is required, this invention activates the gas heating equipment at full power, directing the heated water into the water exchange tubes inside the air-side heat exchanger (i.e., the outdoor heat exchanger). The heat pump does not switch to reverse circulation (or only switches briefly); instead, it utilizes the hot water supplied by the gas heating equipment flowing through the outdoor heat exchanger. Combined with the large opening of the electronic expansion valve, the heat of the hot water quickly melts the frost on the outdoor side. During defrosting, the water temperature rises instead of falling, and the user is completely unaware of the defrosting process.

[0071] In extremely cold weather, if the intake superheat is detected to be consistently lower than the set value (indicating that frost is affecting evaporation or there is a risk of liquid slugging), direct defrosting is less efficient. This patent addresses this by turning on the gas heating equipment to share the load, reducing the heat pump load, lowering the fan speed or reducing the compressor frequency, thereby reducing the heat load demand of the outdoor heat exchanger and allowing the frost layer to naturally slow down its growth or be more easily melted by its own heat.

[0072] This embodiment also provides a defrosting device for air-source units based on gas-electric complementarity, such as... Figure 2 As shown, the device comprises the following components: The frost risk prediction module 01 is used to predict the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located, collect the pipe wall temperature of the outdoor heat exchanger in real time, and determine the frost risk factor of the outdoor heat exchanger based on the frost point temperature and the pipe wall temperature. The mode determination module 02 is used to determine the anti-defrosting mode provided by the gas heating equipment for the outdoor heat exchanger based on the frost risk factor and the pipe wall temperature. Control module 03 is used to control the heat provided by the gas heating equipment to the air source unit based on the defrosting mode.

[0073] Based on the above embodiments, the present invention also provides a terminal device, the principle block diagram of which can be as follows: Figure 3 As shown, the terminal device includes a processor, memory, network interface, and display screen connected via a system bus. The processor provides computing and control capabilities. The memory includes non-volatile storage media and internal memory. The non-volatile storage media stores the operating system and computer programs. The internal memory provides the environment for the operation of the operating system and computer programs stored in the non-volatile storage media. The network interface is used for communication with external terminals via a network connection. When the computer program is executed by the processor, it implements a defrosting method for an air-source generator unit based on gas-electric complementary technology. The display screen of the terminal device can be a liquid crystal display (LCD) or an e-ink display.

[0074] Those skilled in the art will understand that Figure 3The schematic diagram shown is only a partial structural diagram related to the present invention and does not constitute a limitation on the terminal device to which the present invention is applied. The specific terminal device may include more or fewer components than shown in the figure, or combine certain components, or have different component arrangements.

[0075] In one embodiment, a terminal device is provided, comprising a memory, a processor, and a defrosting program for an air-source heat pump unit based on gas-electric complementarity stored in the memory and executable on the processor. When the processor executes the defrosting program for the air-source heat pump unit based on gas-electric complementarity, it implements the following operation instructions: Predict the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located, collect the pipe wall temperature of the outdoor heat exchanger in real time, and determine the frost risk factor of the outdoor heat exchanger based on the frost point temperature and the pipe wall temperature. Based on the frost risk factor and the pipe wall temperature, the defrosting mode provided by the gas heating equipment for the outdoor heat exchanger is determined. Based on the defrosting mode, the heat supplied by the gas heating equipment to the air source unit is controlled.

[0076] Those skilled in the art will understand that all or part of the processes in the methods of the above embodiments can be implemented by a computer program instructing related hardware. The computer program can be stored in a non-volatile computer-readable storage medium. When executed, the computer program can include the processes of the embodiments of the above methods. Any references to memory, storage, databases, or other media used in the embodiments provided by this invention can include non-volatile and / or volatile memory. Non-volatile memory can include read-only memory (ROM), programmable ROM (PROM), electrically programmable ROM (EPROM), electrically erasable programmable ROM (EEPROM), or flash memory. Volatile memory can include random access memory (RAM) or external cache memory. By way of illustration and not limitation, RAM is available in various forms, such as static RAM (SRAM), dynamic RAM (DRAM), synchronous DRAM (SDRAM), dual data rate SDRAM (DDRSDRAM), enhanced SDRAM (ESDRAM), synchronous link DRAM (SLDRAM), Rambus direct RAM (RDRAM), direct memory bus dynamic RAM (DRDRAM), and memory bus dynamic RAM (RDRAM), etc.

[0077] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A defrosting method for air-source generator units based on gas-electric complementarity, characterized in that, include: Predict the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located, collect the pipe wall temperature of the outdoor heat exchanger in real time, and determine the frost risk factor of the outdoor heat exchanger based on the frost point temperature and the pipe wall temperature. Based on the frost risk factor and the pipe wall temperature, the defrosting mode provided by the gas heating equipment for the outdoor heat exchanger is determined. Based on the defrosting mode, the heat supplied by the gas heating equipment to the air source unit is controlled.

2. The defrosting method for air-source generator units based on gas-electric complementarity as described in claim 1, characterized in that, Predict the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located, including: Collect the dry-bulb temperature and relative humidity of the current outdoor environment, and predict the frost point temperature based on the dry-bulb temperature and relative humidity; Alternatively, the dry-bulb and wet-bulb temperatures of the current outdoor environment can be collected, and the frost point temperature can be predicted based on the dry-bulb and wet-bulb temperatures.

3. The defrosting method for air-source generator units based on gas-electric complementarity as described in claim 1, characterized in that, Based on the frosting risk factor and the pipe wall temperature, the defrosting mode provided by the gas heating equipment for the outdoor heat exchanger is determined, including: When the frost risk factor is less than or equal to the safety threshold and greater than zero, the gas heating equipment is controlled to provide an anti-frost mode for the outdoor heat exchanger. The anti-frost mode means that the gas heating equipment delivers heat to the outdoor heat exchanger so that the pipe wall temperature rises to the anti-frost temperature. Alternatively, when the frost risk factor is less than or equal to zero degrees and the pipe wall temperature is less than or equal to zero degrees, the gas heating equipment is controlled to provide a defrosting mode for the outdoor heat exchanger.

4. The defrosting method for air-source generator units based on gas-electric complementarity as described in claim 3, characterized in that, Also includes: When the gas heating equipment provides the anti-frost mode for the outdoor heat exchanger, the intake superheat of the air source unit is monitored in real time. When the intake superheat is continuously less than the target value, the gas heating equipment is switched from the anti-frost mode to the dynamic load compensation mode. The dynamic load compensation mode represents adjusting the heat load of the gas heating equipment in real time based on the intake superheat. Alternatively, when the gas heating equipment provides the defrosting mode for the outdoor heat exchanger, the intake superheat of the air source unit is monitored. When the intake superheat is continuously less than the target value, the gas heating equipment is switched from the defrosting mode to the dynamic load compensation mode.

5. The defrosting method for air-source generator units based on gas-electric complementarity as described in claim 4, characterized in that, Under the dynamic load compensation mode, determining the heat load that the gas heating equipment needs to share includes: Based on the target value and the inhalation superheat, the inhalation superheat deviation is determined; Determine the derivative of the pipe wall temperature with respect to time and the integral of the intake superheat deviation with respect to time; Based on the intake superheat deviation, the differential, and the integral, the heat load to be shared by the gas heating equipment is determined.

6. The defrosting method for air-source generator units based on gas-electric complementarity as described in claim 4, characterized in that, In the dynamic load compensation mode, the gas heating equipment and the air source unit are controlled to jointly bear the total heat load required to raise the intake superheat to the target value. This includes controlling the air source unit to output its share of the heat load, which includes: The target heating capacity of the air source unit is determined based on the heat load that the air source unit needs to share. Based on prior knowledge, the target frequency of the compressor of the air source unit corresponding to the target heating capacity is determined; The compressor is controlled to operate at the target frequency in order to control the air source unit to output the heat load it needs to share.

7. The defrosting method for air-source generator units based on gas-electric complementarity as described in claim 6, characterized in that, In the dynamic load compensation mode, when the compressor is controlled to operate at the target frequency, the compressor fan is controlled to operate at the target speed so that the fan speed matches the compressor's target frequency. Determining the target speed includes: Based on the aforementioned intake superheat deviation, the target correction amount for the fan speed is determined; The target rotational speed is obtained based on the target correction amount and the reference rotational speed of the wind turbine.

8. A defrosting device for an air-source generator unit based on gas-electric complementarity, characterized in that, The device comprises the following components: The frost risk prediction module is used to predict the frost point temperature of the current outdoor environment where the outdoor heat exchanger of the air source unit is located, collect the pipe wall temperature of the outdoor heat exchanger in real time, and determine the frost risk factor of the outdoor heat exchanger based on the frost point temperature and the pipe wall temperature. The mode determination module is used to determine the anti-defrosting mode provided by the gas heating equipment for the outdoor heat exchanger based on the frost risk factor and the pipe wall temperature. The control module is used to control the heat provided by the gas heating equipment to the air source unit based on the defrosting mode.

9. A terminal device, characterized in that, The terminal device includes a memory, a processor, and a defrosting program for an air source unit based on gas-electric complementarity stored in the memory and executable on the processor. When the processor executes the defrosting program for an air source unit based on gas-electric complementarity, it implements the steps of the defrosting method for an air source unit based on gas-electric complementarity as described in any one of claims 1-6.

10. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores a defrosting program for an air source unit based on gas-electric complementarity. When the defrosting program for an air source unit based on gas-electric complementarity is executed by a processor, it implements the steps of the defrosting method for an air source unit based on gas-electric complementarity as described in any one of claims 1-6.

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