Air source heat pump unit rapid heating method, control device and air source heat pump unit

Abstract

The embodiment of the application discloses a kind of quick heating method of air source heat pump unit, control device and air source heat pump unit, belong to heat pump system technical field, the quick heating method of air source heat pump unit includes: obtaining the actual water temperature of water tank, determines actual water temperature with the actual water temperature change rate of heating time length;Actual water temperature and target water temperature determine target water temperature change rate;Determine the operating parameter of refrigerant circulation system based on the set parameter value of current working condition;Actual water temperature change rate, target water temperature change rate and set parameter value are used to determine the target parameter value of operating parameter;According to target parameter value, control refrigerant circulation system operation;Wherein, operating parameter includes at least one of compressor frequency increasing rate, compressor air supplement and compressor suction superheat degree.The embodiment can meet target water temperature requirement, realize quick heating, while avoid the problem that heating efficiency and reliability are low due to frequent shutdown protection in the process of compressor frequency increasing.

Description

Technical Field

[0001] This invention relates to the field of heat pump system technology, specifically to a rapid heating method, control device, and air source heat pump unit for an air source heat pump unit. Background Technology

[0002] Air source heat pump units consume electricity to transfer low-grade energy from the environment to the user side to produce hot water for heating and domestic hot water use. This can, to some extent, replace traditional coal-fired heating. Since electricity is a clean energy source, using heat pumps is an environmentally friendly heating method. Furthermore, with the continuous advancement of the "coal-to-electricity" policy, the heat pump market is expanding and gradually becoming more widespread.

[0003] In actual use, air source heat pump units often face the problem of slow heating. For example, in cold winter environments, users usually require a higher target temperature, but the water tank temperature is low at this time, resulting in a long heating time and affecting the user experience. Many usage scenarios in life also have the need for rapid hot water production. Therefore, the rapid heating function of heat pumps is particularly important for the promotion of heat pump products and their daily use.

[0004] In related technologies, the low-temperature heating capacity of the unit is maintained by adjusting the operating frequency of the compressor. However, when the compressor rapidly increases its frequency, various shutdown protection problems are prone to occur, reducing the unit's rapid heating efficiency and reliability. Summary of the Invention

[0005] This application provides a rapid heating method, control device, and air source heat pump unit, which at least solves the technical problem of low rapid heating efficiency and reliability of air source heat pump units caused by rapid frequency increase of the compressor to achieve rapid heating.

[0006] According to a first aspect of the embodiments of this application, a rapid heating method for an air source heat pump unit is provided, the air source heat pump unit comprising a water circulation system and a refrigerant circulation system thermally coupled together, the rapid heating method comprising:

[0007] The actual water temperature of the water tank in the water circulation system is obtained, and the rate of change of the actual water temperature with the heating time is determined.

[0008] The rate of change of the target water temperature is determined based on the actual water temperature and the target water temperature.

[0009] The operating parameters of the refrigerant circulation system are determined based on the set parameter values ​​under the current operating conditions, and the target parameter values ​​are determined according to the actual water temperature change rate, the target water temperature change rate, and the set parameter values.

[0010] Control the operation of the refrigerant circulation system according to the target parameter values;

[0011] The operating parameters include at least one of the following: compressor frequency increase rate, compressor gas supply volume, and compressor suction superheat.

[0012] The rapid heating method of the air source heat pump unit in this embodiment uses the actual water temperature change rate and the target water temperature change rate of the water tank as standards. By combining the set parameter values ​​under the current operating conditions of the unit, the target parameter values ​​of the refrigerant circulation system are determined, thereby adjusting the operating parameters of the refrigerant circulation system to meet the target water temperature requirements and achieve rapid heating. At the same time, it avoids the problem of low heating efficiency and reliability caused by frequent shutdown protection during the compressor frequency increase process.

[0013] In conjunction with the first aspect, in one optional implementation of the embodiments of this application, determining the target water temperature change rate based on the actual water temperature and the target water temperature includes:

[0014] The target water temperature change rate is a function of the actual water temperature and the target water temperature;

[0015] Wherein: under the same actual water temperature conditions, the higher the target water temperature, the greater the rate of change of the target water temperature; under the same target water temperature conditions, the higher the actual water temperature, the smaller the rate of change of the target water temperature.

[0016] In conjunction with the first aspect, in an optional implementation of this application embodiment, the target water temperature change rate satisfies the following formula:

[0017] T' a1 =K1(T a -T s1 );

[0018] Where: T' a1 The target water temperature change rate; K1 is the first proportionality coefficient, and K1 < 1; T a For the target water temperature, T s1 This is the actual water temperature.

[0019] In conjunction with the first aspect, in an optional implementation of this application embodiment, determining the target parameter value of the operating parameters based on the actual water temperature change rate, the target water temperature change rate, and the set parameter value includes:

[0020] The target parameter value is a function of the actual water temperature change rate, the target water temperature change rate, and the set parameter value.

[0021] Wherein, under the same conditions of actual water temperature change rate and target water temperature change rate, the larger the set parameter value, the larger the target parameter value;

[0022] Under the same conditions of actual water temperature change rate and set parameter value, the greater the target water temperature change rate, the greater the target parameter value;

[0023] Under the same target water temperature change rate and the same set parameter value, the greater the actual water temperature change rate, the smaller the target parameter value.

[0024] In conjunction with the first aspect, in an optional implementation of this application embodiment, the target parameter value satisfies the following formula:

[0025]

[0026] Where: M a K1 represents the target parameter value of the refrigerant circulation system; K2 is the second proportional coefficient related to the operating parameters of the refrigerant circulation system, and K2 < 1; M s The operating parameters of the refrigerant circulation system are set based on the current operating conditions; T' a1 T'1 represents the target water temperature change rate.

[0027] In conjunction with the first aspect, in an optional implementation of this application embodiment, the refrigerant circulation system includes an air-side heat exchanger, a water-side heat exchanger, a flash evaporator, and a first electronic expansion valve. The flash evaporator is located in the refrigerant pipeline between the air-side heat exchanger and the water-side heat exchanger, and the first electronic expansion valve is located in the refrigerant pipeline between the water-side heat exchanger and the flash evaporator. When the operating parameters include compressor gas injection, controlling the refrigerant circulation system to operate according to the target parameter value includes:

[0028] Obtain the compressor's suction pressure, replenishment pressure, and discharge pressure;

[0029] The actual gas supply pressure ratio of the compressor is determined based on the intake pressure, the gas supply pressure, and the exhaust pressure. The higher the actual gas supply pressure ratio of the compressor, the greater the gas supply volume of the compressor.

[0030] When the actual gas supply pressure of the compressor is greater than the target gas supply pressure of the compressor, reduce the opening of the first electronic expansion valve.

[0031] When the actual gas supply pressure of the compressor is less than the target gas supply pressure of the compressor, increase the opening of the first electronic expansion valve;

[0032] When the actual gas supply pressure of the compressor equals the target gas supply pressure of the compressor, maintain the current opening of the first electronic expansion valve.

[0033] In conjunction with the first aspect, in an optional implementation of this application embodiment, determining the actual injection pressure ratio of the compressor based on the suction pressure, injection pressure, and discharge pressure includes:

[0034] The actual injection pressure of the compressor is a function of the suction pressure, injection pressure, and discharge pressure.

[0035] Wherein: under the condition that the intake pressure and the replenishment pressure are the same, the greater the exhaust pressure, the smaller the proportion of the actual replenishment pressure;

[0036] Under the condition that the intake pressure and the exhaust pressure are the same, the greater the replenishment pressure, the greater the proportion of the actual replenishment pressure;

[0037] Under the condition that the replenishment pressure and the exhaust pressure are the same, the greater the intake pressure, the smaller the proportion of the actual replenishment pressure.

[0038] In conjunction with the first aspect, in one optional implementation of this application embodiment, the actual gas injection pressure ratio of the compressor satisfies the following formula:

[0039]

[0040] Where: K m P represents the specific gravity of the actual injection pressure of the compressor. m P is the compressor's gas supply pressure. h P is the compressor's discharge pressure. l This refers to the compressor's suction pressure.

[0041] In conjunction with the first aspect, in an optional implementation of this application embodiment, the refrigerant circulation system further includes a second electronic expansion valve. The second electronic expansion valve is located in the refrigerant pipeline between the flash evaporator and the air-side heat exchanger. When the operating parameters include compressor suction superheat, the refrigerant circulation system is controlled to operate according to the target parameter value, including:

[0042] Obtain the compressor's suction temperature and suction pressure;

[0043] Determine the saturation temperature corresponding to the inhalation pressure;

[0044] The actual intake superheat of the compressor is determined based on the intake temperature and the saturation temperature.

[0045] When the actual suction superheat of the compressor is greater than the target parameter value of the suction superheat of the compressor, increase the opening of the second electronic expansion valve;

[0046] If the actual suction superheat of the compressor is less than the target parameter value of the suction superheat of the compressor, reduce the opening of the second electronic expansion valve;

[0047] When the actual suction superheat of the compressor equals the target parameter value of the suction superheat of the compressor, maintain the current opening of the second electronic expansion valve.

[0048] According to a second aspect of the present application, a control device is provided, the control device including a memory and a processor, the memory storing a rapid heating method for an air source heat pump unit, and the processor being used to employ the rapid heating method for an air source heat pump unit proposed in the first aspect of the present application when executing the rapid heating method for the air source heat pump unit.

[0049] According to a third aspect of the present application, an air source heat pump unit is provided, wherein the air source heat pump assembly operates according to the rapid heating method of the air source heat pump unit proposed in the first aspect of the present application, or has the control device proposed in the second aspect of the present application. Attached Figure Description

[0050] The above and other objects, features, and advantages of this disclosure will become more apparent from the detailed description of exemplary embodiments with reference to the accompanying drawings. The drawings described below are merely some embodiments of this disclosure, and those skilled in the art will be able to obtain other drawings based on these drawings without any inventive effort.

[0051] Figure 1 This is a schematic diagram of the air source heat pump unit of this application.

[0052] Figure 2 This is one of the rapid heating process diagrams of the air source heat pump unit provided in the embodiments of this application.

[0053] Figure 3 This is the second rapid heating flowchart of the air source heat pump unit provided in the embodiments of this application.

[0054] Figure 4 This is the third of the rapid heating flowcharts for the air source heat pump unit provided in the embodiments of this application.

[0055] Figure 5 This is a flowchart illustrating the rapid heating process of an air-source heat pump unit, as specifically exemplified in this application.

[0056] Figure 6 This is a structural block diagram of the control device provided in the embodiments of this application.

[0057] In the diagram: 1. Water tank; 2. Water supply pipeline; 3. Compressor; 4. Water-side heat exchanger; 5. First electronic expansion valve; 6. Second electronic expansion valve; 7. Air-side heat exchanger; 8. Gas-liquid separator; 9. Low-pressure sensor; 10. First temperature sensor; 11. Second temperature sensor; 12. Medium-pressure sensor; 13. High-pressure sensor; 14. Injection enthalpy valve; 15. Flash evaporator; 16. Water flow control valve; 17. Four-way valve; 18. Refrigerant pipeline; 100. Processor; 200. Communication bus; 300. User interface; 400. External communication interface; 500. Memory. Detailed Implementation

[0058] To enable those skilled in the art to better understand the present application, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present application, and not all embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative effort should fall within the scope of protection of the present application.

[0059] It should be understood that "multiple" as mentioned herein refers to two or more. In the description of the embodiments of this application, unless otherwise stated, " / " means "or," for example, A / B can mean A or B; "and / or" in this document is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. In addition, to facilitate a clear description of the technical solutions of the embodiments of this application, the terms "first," "second," etc., are used in the embodiments of this application to distinguish identical or similar items with substantially the same function and effect. Those skilled in the art will understand that the terms "first," "second," etc., do not limit the quantity or execution order, and the terms "first," "second," etc., do not necessarily imply that they are different.

[0060] Furthermore, the terms “comprising” and “having”, and any variations thereof, are intended to cover non-exclusive inclusion, such that a process, method, system, product, or apparatus that includes a series of steps or units is not necessarily limited to those steps or units that are explicitly listed, but may include other steps or units that are not explicitly listed or that are inherent to such process, method, product, or apparatus.

[0061] Considering that air source heat pump units heat up slowly in low-temperature environments, the operating frequency of the compressor is usually adjusted to maintain the unit's low-temperature heating capacity. However, the compressor is prone to shutdown protection issues during rapid frequency increase, which reduces the unit's rapid heating efficiency and reliability.

[0062] To address the above technical problems, this embodiment proposes a rapid heating method for an air-source heat pump unit. The air-source heat pump unit includes a water circulation system and a refrigerant circulation system that are thermally coupled together. The rapid heating method includes:

[0063] Obtain the actual water temperature of the water tank in the water circulation system and determine the rate of change of the actual water temperature with the heating time.

[0064] Determine the target water temperature change rate based on the actual water temperature and the target water temperature;

[0065] The operating parameters of the refrigerant circulation system are determined based on the set parameter values ​​under the current operating conditions, and the target parameter values ​​are determined according to the actual water temperature change rate, the target water temperature change rate, and the set parameter values.

[0066] Control the refrigerant circulation system to operate according to target parameter values;

[0067] The operating parameters include at least one of the following: compressor frequency increase rate, compressor gas supply volume, and compressor suction superheat.

[0068] This embodiment uses the actual water temperature change rate and the target water temperature change rate of the water tank as standards. By combining the set parameter values ​​under the current operating conditions of the unit, the target parameter values ​​of the refrigerant circulation system are determined. This allows for the adjustment of the refrigerant circulation system's operating parameters to meet the target water temperature requirements, achieve rapid heating, and avoid the problem of low heating efficiency and reliability caused by frequent shutdown protection during the compressor's frequency increase process.

[0069] The technical solution of this embodiment will be described in detail below with reference to the accompanying drawings. In the absence of conflict, the following embodiments and examples can be combined with each other.

[0070] First, the main body implementing the rapid heating method of the air source heat pump unit in this embodiment will be described in detail.

[0071] The rapid heating method for air source heat pump units in this embodiment is applied to air source heat pump units, such as... Figure 1 As shown, the air source heat pump unit includes a water circulation system and a refrigerant circulation system that are thermally coupled. The water circulation system includes a water tank 1 and a water supply pipeline 2. The air source heat pump unit provides hot water to users through the water tank 1. The water supply pipeline 2 connects the inlet and outlet of the water tank 1 to form a water circulation loop. The refrigerant circulation system includes a compressor 3, a water-side heat exchanger 4, a throttling device, and an air-side heat exchanger 7. The compressor 3, water-side heat exchanger 4, throttling device, and air-side heat exchanger 7 are sequentially connected through a refrigerant pipeline 18 to form a refrigerant circulation loop, and the water supply pipeline 2 is thermally coupled to the water-side heat exchanger 4.

[0072] Furthermore, the water circulation system also includes a first temperature sensor 10 and a water flow control valve 16. The first temperature sensor 10 is located in the water tank 1 and is used to detect the water temperature inside the water tank 1. The water flow control valve 16 is located in the water supply pipeline 2 and is used to control the opening and closing of the water supply pipeline 2.

[0073] Furthermore, the heat pump system also includes a four-way valve 17, which includes a first interface, a second interface, and a third interface. The first interface is connected to the exhaust port of the compressor 3, the second interface is connected to the water-side heat exchanger 4, the third interface is connected to the air-side heat exchanger 7, and the fourth interface is connected to the first suction port of the compressor 3. The refrigerant line 18 between the fourth interface and the first suction port of the compressor 3 is also equipped with a gas-liquid separator 8. The refrigerant line 18 between the gas-liquid separator 8 and the first suction port of the compressor 3 is also equipped with a low-pressure sensor 9. The refrigerant line 18 between the low-pressure sensor 9 and the first suction port of the compressor 3 is also equipped with a second temperature sensor 11, which is used to detect the suction temperature of the compressor 3. The refrigerant line 18 between the exhaust port of the compressor 3 and the first interface is equipped with a high-pressure sensor 13.

[0074] Furthermore, the heat pump system also includes a flash evaporator 15, which is located in the refrigerant pipeline 18 between the air-side heat exchanger 7 and the water-side heat exchanger 4. The gaseous refrigerant outlet of the flash evaporator 15 is connected to the second suction port of the compressor 3. An enthalpy injection valve 14 is also provided between the gaseous refrigerant outlet of the flash evaporator 15 and the second suction port of the compressor 3. A medium pressure sensor 12 is also provided in the refrigerant pipeline 18 between the enthalpy injection valve 14 and the second suction port of the compressor 3.

[0075] Furthermore, the throttling device includes a first electronic expansion valve 5 and a second electronic expansion valve 6. The first electronic expansion valve 5 is located in the refrigerant line 18 between the water-side heat exchanger 4 and the flash evaporator 15, and the second electronic expansion valve 6 is located in the refrigerant line 18 between the flash evaporator 15 and the air-side radiator.

[0076] The rapid heating method of the air source heat pump unit in this embodiment will be described in detail below.

[0077] like Figure 2 The flowchart shown illustrates the rapid heating method for an air-source heat pump unit in this embodiment, which includes the following steps:

[0078] S21. Obtain the actual water temperature of the water tank in the water circulation system and determine the rate of change of the actual water temperature with the heating time.

[0079] Specifically, the combination Figure 5 The flowchart shows that after the unit is started up and running, the user sets the target water temperature T. a Then select the rapid heating mode. The first temperature sensor detects the current actual water temperature T in the water tank. s1The control device records the change in water tank temperature with heating time t. The water tank temperature T1 satisfies the formula: T1 = f(t). The actual rate of change of water tank temperature with heating time t satisfies the formula:

[0080]

[0081] S22. Determine the rate of change of the target water temperature based on the actual water temperature and the target water temperature.

[0082] Specifically, the rate of change of the target water temperature is determined based on the actual water temperature and the target water temperature, including:

[0083] The target water temperature change rate is a function of the actual water temperature and the target water temperature; wherein: under the same actual water temperature conditions, the higher the target water temperature, the greater the target water temperature change rate; under the same target water temperature conditions, the higher the actual water temperature, the smaller the target water temperature change rate. For example, the target water temperature change rate satisfies the following formula: T' a1 =K1(T a -T s1 );

[0084] Where: T' a1 The target water temperature change rate; K1 is the first proportionality coefficient, and K1 < 1; T a For the target water temperature, T s1 This is the actual water temperature.

[0085] S23. Determine the target parameter values ​​of the refrigerant circulation system based on the set parameter values ​​under the current operating conditions, and according to the actual water temperature change rate, the target water temperature change rate, and the set parameter values.

[0086] Specifically, the target parameter value of the operating parameters is determined based on the actual water temperature change rate, the target water temperature change rate, and the set parameter value. This includes: the target parameter value is a function of the actual water temperature change rate, the target water temperature change rate, and the set parameter value.

[0087] Among them, under the same actual water temperature change rate and target water temperature change rate, the larger the set parameter value, the larger the target parameter value.

[0088] Under the same actual water temperature change rate and set parameter value, the greater the target water temperature change rate, the larger the target parameter value; under the same target water temperature change rate and set parameter value, the greater the actual water temperature change rate, the smaller the target parameter value.

[0089] For example, the target parameter value satisfies the following formula:

[0090] Where: M aK1 represents the target parameter value of the refrigerant circulation system; K2 is the second proportional coefficient related to the operating parameters of the refrigerant circulation system, and K2 < 1; M s The operating parameters of the refrigerant circulation system are set based on the current operating conditions; T' a1 T'1 represents the target water temperature change rate.

[0091] S24. Control the operation of the refrigerant circulation system according to the target parameter values;

[0092] Specifically, the operating parameters include at least one of the following: compressor frequency increase rate, compressor gas supply volume, and compressor suction superheat.

[0093] In one example, when the operating parameters include the compressor boost rate, the compressor is controlled to boost at a determined boost rate.

[0094] In one example, such as Figure 3 The flowchart shown illustrates how, with operating parameters including compressor gas supply, the refrigerant circulation system is controlled according to target parameter values, comprising the following steps:

[0095] S31. Obtain the compressor's suction pressure, replenishment pressure, and discharge pressure;

[0096] S32. Determine the actual gas supply pressure ratio of the compressor based on the suction pressure, gas supply pressure, and discharge pressure, wherein the greater the actual gas supply pressure ratio of the compressor, the greater the gas supply volume of the compressor;

[0097] S33. When the actual gas supply pressure ratio of the compressor is greater than the target gas supply pressure ratio of the compressor, reduce the opening of the first electronic expansion valve; when the actual gas supply pressure ratio of the compressor is less than the target gas supply pressure ratio of the compressor, increase the opening of the first electronic expansion valve; when the actual gas supply pressure ratio of the compressor is equal to the target gas supply pressure ratio of the compressor, maintain the current opening of the first electronic expansion valve.

[0098] Specifically, the combination Figure 5 The flowchart shows that the compressor's refrigerant suction pressure, injection pressure, and discharge pressure are measured by low-pressure, medium-pressure, and high-pressure sensors, respectively. The actual injection pressure ratio of the compressor is determined based on the suction pressure, injection pressure, and discharge pressure, and the actual injection pressure ratio of the compressor is a function of the suction pressure, injection pressure, and discharge pressure.

[0099] Among them: under the condition that the intake pressure and the replenishment pressure are the same, the greater the exhaust pressure, the smaller the proportion of the actual replenishment pressure; under the condition that the intake pressure and the exhaust pressure are the same, the greater the replenishment pressure, the larger the proportion of the actual replenishment pressure; under the condition that the replenishment pressure and the exhaust pressure are the same, the greater the intake pressure, the smaller the proportion of the actual replenishment pressure.

[0100] For example, the specific gravity of the actual injection pressure of the compressor satisfies the following formula: Where: K m P is the specific gravity of the actual gas supply pressure of the compressor. m P is the compressor's gas supply pressure. h P is the compressor's discharge pressure. l This refers to the compressor's suction pressure.

[0101] It should be noted that the actual injection pressure specific gravity of the compressor cannot be directly determined, K m K is the specific gravity of the actual gas supply pressure of the compressor. m The higher the value, the higher the compressor's gas supply pressure and the greater the gas supply volume. Therefore, through K... m The value reflects the amount of refrigerant supplied to the compressor, while the first electronic expansion valve controls the amount of refrigerant entering the compressor's gas inlet through the flash evaporator. By controlling the opening of the first electronic expansion valve, the actual gas supply pressure of the compressor can be adjusted.

[0102] After determining the actual gas supply pressure ratio of the compressor, compare the actual gas supply pressure ratio with the target gas supply pressure ratio. If the actual gas supply pressure ratio is greater than the target gas supply pressure ratio, decrease the opening of the first electronic expansion valve to reduce the gas supply volume to the compressor. If the actual gas supply pressure ratio is less than the target gas supply pressure ratio, increase the opening of the first electronic expansion valve to increase the gas supply volume to the compressor. If the actual gas supply pressure ratio is equal to the target gas supply pressure ratio, maintain the current opening of the first electronic expansion valve to maintain the gas supply volume to the compressor.

[0103] In one example, such as Figure 4 The flowchart shown illustrates the process of controlling the refrigerant circulation system according to target parameter values, with operating parameters including compressor suction superheat. The steps include:

[0104] S41. Obtain the compressor's suction temperature and suction pressure;

[0105] S42. Determine the saturation temperature corresponding to the inhalation pressure;

[0106] S43. Determine the actual intake superheat of the compressor based on the intake temperature and saturation temperature;

[0107] S44. When the actual suction superheat of the compressor is greater than the target parameter value of the suction superheat of the compressor, increase the opening of the second electronic expansion valve; when the actual suction superheat of the compressor is less than the target parameter value of the suction superheat of the compressor, decrease the opening of the second electronic expansion valve; when the actual suction superheat of the compressor is equal to the target parameter value of the suction superheat of the compressor, maintain the current opening of the second electronic expansion valve.

[0108] Specifically, the combination Figure 5 The flowchart shows that, in order to maintain the reliability of unit operation, the second temperature sensor detects the compressor suction temperature, the low-pressure sensor detects the compressor suction pressure, and the saturation temperature corresponding to the compressor suction pressure is determined. Then, the actual suction superheat of the compressor can be determined based on the compressor suction temperature and the saturation temperature. The actual suction superheat of the compressor = suction temperature - saturation temperature.

[0109] Since the second electronic expansion valve controls the amount of refrigerant on the low-pressure side, the less refrigerant on the low-pressure side, the higher the compressor suction temperature and the higher the compressor suction superheat. Therefore, the suction temperature and suction superheat can be reduced by increasing the opening of the second electronic expansion valve. Conversely, the lower the compressor suction temperature and the lower the compressor suction superheat, the higher the suction temperature can be increased by decreasing the opening of the second electronic expansion valve.

[0110] After determining the actual suction superheat of the compressor, the actual suction superheat is compared with the target parameter value. The opening of the second electronic expansion valve is then adjusted based on the comparison result. If the actual suction superheat is greater than the target parameter value, the opening of the second electronic expansion valve is increased; if the actual suction superheat is less than the target parameter value, the opening is decreased. If the actual suction superheat equals the target parameter value, the current opening of the second electronic expansion valve is maintained.

[0111] In summary, this embodiment sets the required temperature rise per unit time based on the difference between the target water temperature and the actual water temperature in the tank. By recording the temperature change of the tank over time, the temperature rise rate is calculated. Using this as a standard, the required parameters are calculated and adjusted by combining the unit's frequency increase rate, compressor gas supply, and compressor suction superheat under the current operating conditions. Increasing the compressor frequency increase rate and gas supply increases the heating capacity to meet the target water temperature rise requirement, achieving rapid heating. Adjusting the suction superheat improves the unit's operational reliability.

[0112] This application also provides a control device, which includes a memory and a processor. The memory stores a rapid heating method for an air source heat pump unit, and the processor is used to employ the rapid heating method for an air source heat pump unit proposed in the above embodiments when executing the rapid heating method for the air source heat pump unit.

[0113] Specifically, such as Figure 6 As shown, the electronic device includes a processor 100, at least one communication bus 200, a user interface 300, at least one external communication interface 400, and a memory 500. The communication bus 200 is configured to enable communication between these components. The user interface 300 may include a display screen, and the external communication interface 400 may include standard wired and wireless interfaces. The memory 500 stores control methods for the garment handling device. The processor 100 is used to employ the aforementioned methods when executing the control methods for the garment handling device stored in the memory 500.

[0114] The descriptions of the above computer program products, computer-readable storage media, and electronic devices are similar to those of the above method embodiments, and have similar beneficial effects. For any technical details not disclosed in the computer program products, computer-readable storage media, and electronic devices of this application, please refer to the descriptions of the method embodiments of this application for understanding.

[0115] This embodiment also proposes an air source heat pump unit, wherein the air source heat pump components operate according to the rapid heating method of the air source heat pump unit proposed in the above embodiments, or the control device of the above embodiments.

[0116] The air source heat pump component of this embodiment has been described in detail in the previous section on the execution subject of the rapid heating method of the air source heat pump component, and will not be repeated here.

[0117] The sequence numbers or order of description of the embodiments in this application are for descriptive purposes only and do not represent the superiority or inferiority of the embodiments.

[0118] In the several embodiments provided in this application, it should be understood that the disclosed technical content can be implemented in other ways. The device embodiments described above are merely illustrative; for example, the division of units can be a logical functional division, and in actual implementation, there may be other division methods. For instance, multiple units or components may be combined or integrated into another system, or some features may be ignored or not executed. Furthermore, the displayed or discussed mutual coupling, direct coupling, or communication connection may be through some interfaces; the indirect coupling or communication connection between units or modules may be electrical or other forms.

[0119] The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple units. Some or all of the units can be selected to achieve the purpose of this embodiment according to actual needs.

[0120] Furthermore, the functional units in the various embodiments of this application can be integrated into one processing unit, or each unit can exist physically separately, or two or more units can be integrated into one unit. The integrated unit can be implemented in hardware or as a software functional unit.

[0121] In the above embodiments, implementation can be achieved, in whole or in part, through software, hardware, firmware, or any combination thereof. When implemented in software, it can be implemented, in whole or in part, as a computer program product. The computer program product includes one or more computer instructions. When the computer instructions are loaded and executed on a computer, all or part of the processes or functions described in the embodiments of this application are generated. The computer can be a general-purpose computer, a special-purpose computer, a computer network, or other programmable device. The computer instructions can be stored in a computer-readable storage medium or transmitted from one computer-readable storage medium to another. For example, the computer instructions can be transmitted from one website, computer, server, or data center to another via wired (e.g., coaxial cable, fiber optic, digital subscriber line (DSL)) or wireless (e.g., infrared, wireless, microwave, etc.) means. The computer-readable storage medium can be any available medium accessible to a computer, or a data storage device such as a server or data center that integrates one or more available media. The available medium can be a magnetic medium (e.g., floppy disk, hard disk, magnetic tape), an optical medium (e.g., digital versatile disc (DVD)), or a semiconductor medium (e.g., solid state disk (SSD)). It is worth noting that the computer-readable storage medium mentioned in the embodiments of this application can be a non-volatile storage medium; in other words, it can be a non-transient storage medium.

[0122] It should be noted that the information (including but not limited to user device information, user personal information, etc.), data (including but not limited to data used for analysis, stored data, displayed data, etc.), and signals involved in the embodiments of this application are all authorized by the user or fully authorized by all parties, and the collection, use, and processing of related data must comply with the relevant laws, regulations, and standards of the relevant countries and regions. For example, the scene data of the current frame in the 3D virtual scene involved in the embodiments of this application, the client's device information, and the scene interaction information are all obtained with full authorization.

[0123] The above description is only a preferred embodiment of this application. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the principle of this application, and these improvements and modifications should also be considered within the scope of protection of this application.

Claims

1. A method for rapid heating of an air source heat pump unit, the method comprising: The air source heat pump unit comprises a water circulation system and a refrigerant circulation system which are connected by thermal coupling, and the rapid heating method comprises: acquiring an actual water temperature of a water tank of the water circulation system, and determining an actual water temperature change rate of the actual water temperature with heating time; determining a target water temperature change rate according to the actual water temperature and a target water temperature; determining a target parameter value of an operating parameter of the refrigerant circulation system based on a set parameter value of a current working condition, and determining the target parameter value of the operating parameter according to the actual water temperature change rate, the target water temperature change rate and the set parameter value; controlling the refrigerant circulation system to operate according to the target parameter value; wherein the operating parameter comprises at least one of a compressor frequency increasing rate, a compressor charge amount and a compressor suction gas superheat degree; determining a target water temperature change rate according to the actual water temperature and a target water temperature, comprising: the target water temperature change rate is a function of the actual water temperature and the target water temperature; wherein, under the condition of the same actual water temperature, the greater the target water temperature is, the greater the target water temperature change rate is; under the condition of the same target water temperature, the greater the actual water temperature is, the smaller the target water temperature change rate is; determining a target parameter value of an operating parameter according to the actual water temperature change rate, the target water temperature change rate and the set parameter value, comprising: the target parameter value is a function of the actual water temperature change rate, the target water temperature change rate and the set parameter value; wherein, under the condition of the same actual water temperature change rate and the target water temperature change rate, the greater the set parameter value is, the greater the target parameter value is; under the condition of the same actual water temperature change rate and the set parameter value, the greater the target water temperature change rate is, the greater the target parameter value is; under the condition of the same target water temperature change rate and the set parameter value, the greater the actual water temperature change rate is, the smaller the target parameter value is. the target water temperature change rate satisfies the following formula: the target parameter value satisfies the following formula:

2. The method of claim 1, wherein the air source heat pump unit is a multi- stage air source heat pump unit. the refrigerant circulation system comprises an air side heat exchanger, a water side heat exchanger, a flash evaporator and a first electronic expansion valve, the flash evaporator is arranged in a refrigerant pipeline between the air side heat exchanger and the water side heat exchanger, the first electronic expansion valve is arranged in a refrigerant pipeline between the water side heat exchanger and the flash evaporator, in the case that the operating parameter comprises a compressor charge amount, controlling the refrigerant circulation system to operate according to the target parameter value, comprising: ； Wherein: T a1 is the target water temperature change rate; K1 is a first proportional coefficient, and K1 < 1; T a is the target water temperature, T s1 is the actual water temperature.

3. The method of claim 1, wherein the air source heat pump unit is a multi- stage air source heat pump unit. acquiring suction pressure, charge pressure and discharge pressure of the compressor; ； Wherein: M a is a target parameter value of the refrigerant circulation system; K2 is a second proportional coefficient related to the operating parameter of the refrigerant circulation system, and K2 < 1; M s is a set parameter value of the operating parameter of the refrigerant circulation system based on the current working condition; T’ a1 is a target water temperature change rate; T’1 is an actual water temperature change rate.

4. The method of claim 1, wherein the air source heat pump unit is a multi- stage air source heat pump unit. determining an actual charge pressure ratio of the compressor according to the suction pressure, the charge pressure and the discharge pressure, wherein the greater the actual charge pressure ratio of the compressor is, the greater the compressor charge amount is; in the case that the actual charge pressure ratio of the compressor > a target ratio of the compressor charge pressure, reducing the opening degree of the first electronic expansion valve; in the case that the actual charge pressure ratio of the compressor < the target ratio of the compressor charge pressure, increasing the opening degree of the first electronic expansion valve; ​ ​ In the case that the actual charge pressure ratio of the compressor = the target ratio of the charge pressure of the compressor, the current first electronic expansion valve opening degree is maintained.

5. The method of claim 4, wherein the air source heat pump unit is a multi- stage air source heat pump unit. The actual charge pressure ratio of the compressor is determined according to the suction pressure, the charge pressure and the discharge pressure, comprising: The actual charge pressure ratio of the compressor is a function of the suction pressure, the charge pressure and the discharge pressure; In the case that the suction pressure and the charge pressure are the same, the greater the discharge pressure, the smaller the actual charge pressure ratio; In the case that the suction pressure and the discharge pressure are the same, the greater the charge pressure, the greater the actual charge pressure ratio; In the case that the charge pressure and the discharge pressure are the same, the greater the suction pressure, the smaller the actual charge pressure ratio.

6. The method of claim 5, wherein the air source heat pump unit is a multi- stage air source heat pump unit. The actual charge pressure ratio of the compressor satisfies the following formula: ； wherein: K m is the actual charge pressure ratio of the compressor, P m is the charge pressure of the compressor; P h is the discharge pressure of the compressor; P l is the suction pressure of the compressor.

7. The method of claim 4, wherein the air source heat pump unit is a multi- stage air source heat pump unit. The refrigerant circulation system further comprises a second electronic expansion valve arranged in a refrigerant pipeline between the flash evaporator and the air-side heat exchanger, and in the case that the operating parameter comprises the compressor suction superheat, the refrigerant circulation system is controlled to operate according to the target parameter value, comprising: The suction temperature and the suction pressure of the compressor are obtained; The saturation temperature corresponding to the suction pressure is determined; The actual suction superheat of the compressor is determined according to the suction temperature and the saturation temperature; In the case that the actual suction superheat of the compressor > the target parameter value of the compressor suction superheat, the second electronic expansion valve opening degree is increased; In the case that the actual suction superheat of the compressor < the target parameter value of the compressor suction superheat, the second electronic expansion valve opening degree is decreased; In the case that the actual suction superheat of the compressor = the target parameter value of the compressor suction superheat, the current second electronic expansion valve opening degree is maintained.

8. A control device characterized by comprising: The control device comprises a memory and a processor, the memory stores the rapid heating method of the air source heat pump assembly, and the processor is used to execute the rapid heating method of the air source heat pump assembly.

9. An air source heat pump unit, characterised in that, The air source heat pump assembly operates according to the rapid heating method of the air source heat pump assembly according to any one of claims 1-8, or has the control device according to claim 8.

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