Quick heating method of air source heat pump unit, control device and air source heat pump unit

Abstract

The embodiment of the invention discloses a rapid heating method of an air source heat pump unit, a control device and the air source heat pump unit, and belongs to the technical field of heat pump systems.The rapid heating method of the air source heat pump unit comprises the steps that the actual water temperature of a water tank is obtained, and the actual water temperature change rate of the actual water temperature along with the heating duration is determined; determining a target water temperature change rate according to the actual water temperature and the target water temperature; setting parameter values of operation parameters of the refrigerant circulation system based on the current working condition are determined, and target parameter values of the operation parameters are determined according to the actual water temperature change rate, the target water temperature change rate and the setting parameter values; the refrigerant circulation system is controlled to operate according to the target parameter value; wherein the operation parameters comprise at least one of the compressor frequency increasing rate, the compressor air supply amount and the compressor air suction superheat degree. According to the embodiment, the target water temperature requirement can be met, rapid heating is achieved, and meanwhile the problems of low heating efficiency and reliability caused by frequent shutdown protection in the frequency increasing process of the compressor are solved.

Description

Technical Field

[0001] The present invention relates to the technical field of heat pump systems, and in particular to a rapid heating method and a control device for an air source heat pump unit. Background Art

[0002] Air source heat pump units consume electricity and transfer low-grade energy in the environment to the user side to produce hot water, which can provide heating for users and be used as domestic hot water. It can replace traditional coal-fired heating to a certain extent. Electricity is a clean energy, so using heat pumps for heating is an environmentally friendly heating method. With the continuous advancement of the "coal to electricity" policy, the heat pump market is also expanding and gradually becoming popular.

[0003] In the actual use of air source heat pump units, the heating is often slow. For example, in the cold winter, the target temperature required by the user is usually high, while the water tank temperature is low and the heating time is long, which affects the user experience; in many usage scenarios in life, there is also a need to quickly produce hot water, so the fast heating function of the heat pump is particularly important for the promotion and daily use of heat pump products.

[0004] In the related art, the low-temperature heating capacity of the unit is maintained by adjusting the operating frequency of the compressor. However, when the compressor frequency increases rapidly, various shutdown protection problems are prone to occur, which reduces the rapid heating efficiency and reliability of the unit. Summary of the invention

[0005] The embodiments of the present application provide a rapid heating method, a control device and an air source heat pump unit of an air source heat pump unit, which at least solve the technical problem that rapid heating is achieved by rapid frequency increase of the compressor, resulting in low rapid heating efficiency and reliability of the air source heat pump unit.

[0006] According to a first aspect of an embodiment of the present application, a rapid heating method of an air source heat pump unit is provided, wherein the air source heat pump unit comprises a water circulation system and a refrigerant circulation system that are thermally coupled, and the rapid heating method comprises:

[0007] Obtaining the actual water temperature of a water tank of a water circulation system, and determining the rate of change of the actual water temperature with the actual water temperature during heating;

[0008] Determining a target water temperature change rate according to the actual water temperature and the target water temperature;

[0009] Determine the set parameter value of the operating parameter of the refrigerant circulation system based on the current working condition, and determine 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;

[0010] Controlling the operation of the refrigerant circulation system according to the target parameter value;

[0011] Wherein, the operating parameters include at least one of the compressor frequency increase rate, the compressor air supplement amount and the compressor suction superheat.

[0012] The rapid heating method of the air source heat pump unit of this embodiment is based on the actual water temperature change rate of the water tank and the target water temperature change rate. The target parameter values ​​of the operating parameters of the refrigerant circulation system are determined by combining the set parameter values ​​under the current operating conditions of the unit, 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, the problem of low heating efficiency and reliability due to frequent shutdown protection during the compressor frequency increase process is avoided.

[0013] In combination with the first aspect, in an optional implementation of the embodiment of the present application, determining the target water temperature change rate according to 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 condition, the higher the target water temperature, the greater the target water temperature change rate; under the same target water temperature condition, the higher the actual water temperature, the smaller the target water temperature change rate.

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

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

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

[0019] In combination with the first aspect, in an optional implementation of the embodiment of the present application, 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 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 the actual water temperature change rate and the target water temperature change rate, the larger the set parameter value, the larger the target parameter value;

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

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

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

[0025]

[0026] Where: M a is 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 based on the set parameter values ​​of the current working conditions; T' a1 is the target water temperature change rate; T'1 is the target water temperature change rate.

[0027] In combination with the first aspect, in an optional implementation of the embodiment of the present application, 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 arranged in the refrigerant pipeline between the air-side heat exchanger and the water-side heat exchanger, the first electronic expansion valve is located in the refrigerant pipeline between the water-side heat exchanger and the flash evaporator, and when the operating parameter includes the compressor air supply volume, the refrigerant circulation system is controlled to operate according to the target parameter value, including:

[0028] Obtain the suction pressure, supply pressure and exhaust pressure of the compressor;

[0029] Determine the actual air supply pressure ratio of the compressor according to the suction pressure, the air supply pressure and the exhaust pressure, wherein the greater the actual air supply pressure ratio of the compressor, the greater the air supply volume of the compressor;

[0030] When the actual air supply pressure specific gravity of the compressor is greater than the target air supply pressure specific gravity of the compressor, reducing the opening of the first electronic expansion valve;

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

[0032] When the actual air supply pressure specific gravity of the compressor=the target air supply pressure specific gravity of the compressor, the current opening degree of the first electronic expansion valve is maintained.

[0033] In combination with the first aspect, in an optional implementation of the embodiment of the present application, determining the actual air supply pressure ratio of the compressor according to the suction pressure, the air supply pressure and the exhaust pressure includes:

[0034] The actual charge pressure specific gravity of the compressor is a function of the suction pressure, charge pressure and discharge pressure;

[0035] Wherein: under the condition that the suction pressure and the supplementary air pressure are the same, the greater the exhaust pressure is, the smaller the specific gravity of the actual supplementary air pressure is;

[0036] Under the condition that the suction pressure and the exhaust pressure are the same, the greater the supplementary air pressure is, the greater the specific gravity of the actual supplementary air pressure is;

[0037] Under the condition that the supplementary air pressure and the exhaust pressure are the same, the greater the intake pressure is, the smaller the specific gravity of the actual supplementary air pressure is.

[0038] In combination with the first aspect, in an optional implementation of the embodiment of the present application, the actual air supply pressure specific gravity of the compressor satisfies the following formula:

[0039]

[0040] Where: K m is the actual air supply pressure specific gravity of the compressor, P m P is the air supply pressure of the compressor; h is the exhaust pressure of the compressor; P l is the suction pressure of the compressor.

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

[0042] Get the suction temperature and suction pressure of the compressor;

[0043] determining a saturation temperature corresponding to the suction pressure;

[0044] determining the actual suction superheat of the compressor according to the suction 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, increasing the opening of the second electronic expansion valve;

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

[0047] When the actual suction superheat of the compressor=the target parameter value of the suction superheat of the compressor, the current opening degree of the second electronic expansion valve is maintained.

[0048] According to a second aspect of an embodiment of the present application, a control device is provided, which includes a memory and a processor, wherein the memory stores a rapid heating method for an air source heat pump unit, and the processor is used to adopt the rapid heating method for an air source heat pump unit proposed in the first aspect of the embodiment of the present application when executing the rapid heating method for the air source heat pump unit.

[0049] According to the third aspect of the embodiment of the present application, an air source heat pump unit is provided, and the air source heat pump component operates according to the rapid heating method of the air source heat pump unit proposed in the first aspect of the embodiment of the present application, or has the control device proposed in the second aspect of the embodiment of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0050] The above and other objects, features and advantages of the present disclosure will become more apparent by describing in detail its exemplary embodiments with reference to the accompanying drawings. The accompanying drawings described below are only some embodiments of the present disclosure, and it is clear to a person skilled in the art that other accompanying drawings can be obtained from these accompanying drawings without creative work.

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

[0052] Figure 2 This is one of the rapid heating flow charts of the air source heat pump unit provided in the embodiment of the present application.

[0053] Figure 3 This is the second rapid heating flow chart of the air source heat pump unit provided in the embodiment of the present application.

[0054] Figure 4 This is the third rapid heating flow chart of the air source heat pump unit provided in the embodiment of the present application.

[0055] Figure 5 This is a rapid heating flow chart of an air source heat pump unit according to a specific example of the present application.

[0056] Figure 6 It is a structural block diagram of the control device provided in an embodiment of the present application.

[0057] In the figure: 1. water tank; 2. water 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 sensing package; 11. second temperature sensing package; 12. medium pressure sensor; 13. high pressure sensor; 14. spray 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 DESCRIPTION

[0058] In order to enable those skilled in the art to better understand the solution of the present application, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work should fall within the scope of protection of the present application.

[0059] It should be understood that the "multiple" mentioned herein refers to two or more. In the description of the embodiments of the present application, unless otherwise specified, " / " means or, for example, A / B can mean A or B; "and / or" in this article is only a description of the association relationship of the associated objects, indicating that there can be three relationships, for example, A and / or B can mean: A exists alone, A and B exist at the same time, and B exists alone. In addition, in order to facilitate the clear description of the technical solution of the embodiments of the present application, in the embodiments of the present application, the words "first", "second" and the like are used to distinguish between the same items or similar items with basically the same functions and effects. Those skilled in the art can understand that the words "first", "second" and the like do not limit the quantity and execution order, and the words "first", "second" and the like do not limit them to be necessarily different.

[0060] In addition, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover non-exclusive inclusions. For example, a process, method, system, product, or apparatus that includes a series of steps or elements is not necessarily limited to those steps or elements explicitly listed, but may include other steps or elements not explicitly listed or inherent to such process, method, product, or apparatus.

[0061] Taking into account the fact that air source heat pump units heat more slowly in low-temperature environments, the low-temperature heating capacity of the unit is usually maintained by adjusting the operating frequency of the compressor. However, shutdown protection problems are prone to occur during the rapid frequency increase of the compressor, which reduces the rapid heating efficiency and reliability of the unit.

[0062] In order to solve the above technical problems, this embodiment proposes a rapid heating method of 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, and the rapid heating method includes:

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

[0064] Determine the target water temperature change rate according to the actual water temperature and the target water temperature;

[0065] Determine the operating parameters of the refrigerant circulation system based on the set parameter values ​​of the current working conditions, and determine the target parameter values ​​of the operating parameters according to the actual water temperature change rate, the target water temperature change rate and the set parameter values;

[0066] Control the operation of the refrigerant circulation system according to the target parameter value;

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

[0068] This embodiment uses the actual water temperature change rate of the water tank and the target water temperature change rate as standards, and determines the target parameter values ​​of the operating parameters of the refrigerant circulation system by combining the set parameter values ​​under the current operating conditions of the unit, 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 due to frequent shutdown protection during the compressor frequency increase process.

[0069] The technical solution of this embodiment is described in detail below in conjunction with the accompanying drawings. The following embodiments and examples can be combined with each other if there is no conflict.

[0070] First, the execution body of the rapid heating method of the air source heat pump unit of this embodiment is introduced in detail.

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

[0072] Furthermore, the water circulation system further comprises a first temperature sensing package 10 and a water flow control valve 16. The first temperature sensing package 10 is provided in the water tank 1 for detecting the water temperature in the water tank 1. The water flow control valve 16 is provided in the water delivery pipeline 2 for controlling the on-off of the water delivery 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 air intake port of the compressor 3. The refrigerant pipeline 18 between the fourth interface and the first air intake port of the compressor 3 is also provided with a gas-liquid separator 8, the refrigerant pipeline 18 between the gas-liquid separator 8 and the first air intake port of the compressor 3 is also provided with a low-pressure sensor 9, and the refrigerant pipeline 18 between the low-pressure sensor 9 and the first air intake port of the compressor 3 is also provided with a second temperature sensing package 11, and the second temperature sensing package 11 is used to detect the air intake temperature of the compressor 3. The refrigerant pipeline 18 between the exhaust port of the compressor 3 and the first interface is provided with a high-pressure sensor 13.

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

[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 arranged in the refrigerant pipeline 18 between the water-side heat exchanger 4 and the flash evaporator 15, and the second electronic expansion valve 6 is arranged in the refrigerant pipeline 18 between the flash evaporator 15 and the air-side radiator.

[0076] The following is a detailed description of the rapid heating method of the air source heat pump unit of this embodiment.

[0077] like Figure 2 As shown in the flowchart, the rapid heating method of the air source heat pump unit of this embodiment includes the following steps:

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

[0079] Specifically, combined Figure 5 Flow chart, after the unit is started, the user sets the target water temperature T a Then select the fast heating mode. The first temperature sensing package detects the actual water temperature T of the water tank. s1, the control device records the change of the water tank temperature with the heating time t, then the water tank temperature T1 satisfies the formula: T1 = f(t), and the actual water temperature change rate of the water tank temperature with the heating time t satisfies the formula:

[0080]

[0081] S22. Determine the target water temperature change rate according to the actual water temperature and the target water temperature.

[0082] Specifically, the target water temperature change rate is determined according to 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; where: 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. Exemplarily, the target water temperature change rate satisfies the following formula: T' a1 =K1(T a -T s1 );

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

[0085] S23, determining the set parameter value of the operating parameter of the refrigerant circulation system based on the 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;

[0086] Specifically, 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 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 conditions of 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 conditions of the same actual water temperature change rate and set parameter value, the greater the target water temperature change rate, the greater the target parameter value; under the conditions of 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] Exemplarily, the target parameter value satisfies the following formula:

[0090] Where: M ais 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 based on the set parameter values ​​of the current working conditions; T' a1 is the target water temperature change rate; T'1 is the target water temperature change rate.

[0091] S24, controlling the operation of the refrigerant circulation system according to the target parameter value;

[0092] Specifically, the operating parameters include at least one of a compressor frequency increase rate, a compressor air supplement volume, and a compressor suction superheat.

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

[0094] In one example, if Figure 3 The flowchart shown in the figure, when the operating parameters include the compressor air supply volume, controls the operation of the refrigerant circulation system according to the target parameter value, including the following steps:

[0095] S31, obtaining the suction pressure, the replenishment pressure and the exhaust pressure of the compressor;

[0096] S32, determining the actual air supply pressure ratio of the compressor according to the suction pressure, the air supply pressure and the exhaust pressure, wherein the greater the actual air supply pressure ratio of the compressor, the greater the air supply volume of the compressor;

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

[0098] Specifically, combined Figure 5 The flow chart shows that the suction pressure, supply pressure and exhaust pressure of the compressor refrigerant are measured respectively by a low-pressure sensor, a medium-pressure sensor and a high-pressure sensor, and the actual supply pressure ratio of the compressor is determined according to the suction pressure, supply pressure and exhaust pressure, and the actual supply pressure ratio of the compressor is a function of the suction pressure, supply pressure and exhaust pressure.

[0099] Among them: under the condition that the suction pressure and the supply pressure are the same, the greater the exhaust pressure, the smaller the actual supply pressure ratio; under the condition that the suction pressure and the exhaust pressure are the same, the greater the supply pressure, the greater the actual supply pressure ratio; under the condition that the supply pressure and the exhaust pressure are the same, the greater the suction pressure, the smaller the actual supply pressure ratio.

[0100] Exemplarily, the actual air supply pressure ratio of the compressor satisfies the following formula: Where: K m is the specific gravity of the actual air supply pressure of the compressor, P m P is the air supply pressure of the compressor; h is the exhaust pressure of the compressor; P l is the suction pressure of the compressor.

[0101] It should be noted that the actual air supply pressure specific gravity of the compressor cannot be directly determined. m K is the specific gravity of the actual air supply pressure of the compressor, m The larger the value, the higher the compressor's air supply pressure and the larger the air supply volume. m The value can reflect the amount of air supply of the compressor, and the first electronic expansion valve can control the amount of refrigerant entering the compressor air supply port through the flash evaporator. By controlling the opening of the first electronic expansion valve, the actual air supply pressure specific gravity of the compressor can be adjusted.

[0102] After determining the actual air supply pressure ratio of the compressor, the actual air supply pressure ratio is compared with the target air supply pressure ratio of the compressor. When the actual air supply pressure ratio of the compressor is greater than the target air supply pressure ratio of the compressor, the opening of the first electronic expansion valve is reduced to reduce the air supply volume of the compressor; when the actual air supply pressure ratio of the compressor is less than the target air supply pressure ratio of the compressor, the opening of the first electronic expansion valve is increased to increase the air supply volume of the compressor. When the actual air supply pressure ratio of the compressor is equal to the target air supply pressure ratio of the compressor, the current opening of the first electronic expansion valve is maintained to maintain the air supply volume of the compressor.

[0103] In one example, if Figure 4 The flowchart shown in the figure controls the operation of the refrigerant circulation system according to the target parameter value when the operating parameters include the compressor suction superheat, and includes the following steps:

[0104] S41, obtaining the suction temperature and suction pressure of the compressor;

[0105] S42, determining the saturation temperature corresponding to the suction pressure;

[0106] S43, determining the actual suction superheat of the compressor according to the suction temperature and the 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, reduce 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, combined Figure 5 Flow chart, in order to maintain the reliability of the unit operation, the second temperature sensing package detects the compressor suction temperature, the compressor suction pressure is detected by the low-pressure sensor, and the saturation temperature corresponding to the compressor suction pressure is determined. The actual suction superheat of the compressor can be determined based on the compressor suction temperature and the saturation temperature, wherein 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 the amount of refrigerant on the low-pressure side, the higher the compressor suction temperature and the higher the compressor suction superheat. Therefore, the suction temperature and the suction superheat are 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 suction temperature is increased by reducing the opening of the second electronic expansion valve.

[0110] After determining the actual suction superheat of the compressor, the actual suction superheat of the compressor is compared with the target parameter value of the suction superheat, and the opening of the second electronic expansion valve is regulated according to the comparison result. If the actual suction superheat of the compressor is greater than the target parameter value of the suction superheat of the compressor, the opening of the second electronic expansion valve is increased; if the actual suction superheat of the compressor is less than the target parameter value of the suction superheat of the compressor, the opening of the second electronic expansion valve is reduced. If the actual suction superheat of the compressor is equal to the target parameter value of the suction superheat of the compressor, the current opening of the second electronic expansion valve is maintained.

[0111] In general, this embodiment sets the required temperature rise per unit time according to the difference between the target water temperature and the actual water temperature of the water tank, calculates the temperature rise rate by recording the change of the water tank temperature over time, and uses this as a standard to calculate the required corresponding parameters and adjust them by combining the frequency increase speed, compressor air supply volume and compressor suction superheat of the unit under the current working condition. By increasing the compressor frequency increase rate and air supply volume to increase the heating capacity, the target water temperature rise requirement is met, rapid heating is achieved, and the unit operation reliability is improved by adjusting the suction superheat.

[0112] An embodiment of the present 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 adopt the rapid heating method for an air source heat pump unit proposed in the above embodiment when executing the rapid heating method for the air source heat pump unit.

[0113] Specifically, 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 realize the connection and communication between these components. The user interface 300 may include a display screen, and the external communication interface 400 may include a standard wired interface and a wireless interface. The control method of the clothing processing device is stored in the memory 500. The processor 100 is used to adopt the above method when executing the control method of the clothing processing device stored in the memory 500.

[0114] The description of the above computer program product, computer-readable storage medium, and electronic device is similar to the description of the above method embodiment, and has similar beneficial effects as the method embodiment. For technical details not disclosed in the computer program product, computer-readable storage medium, and electronic device of this application, please refer to the description of the method embodiment of this application for understanding.

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

[0116] The air source heat pump assembly of this embodiment has been introduced in detail in the execution body of the rapid heating method of the air source heat pump assembly in the foregoing text, and will not be repeated here.

[0117] The sequence of serial numbers or introduction of the embodiments of the present application is for description only and does 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. Among them, the device embodiments described above are only schematic. For example, the division of the units can be a logical function division. There may be other division methods in actual implementation. For example, multiple units or components can be combined or integrated into another system, or some features can be ignored or not executed. Another point is that the mutual coupling or direct coupling or communication connection shown or discussed can be through some interfaces, indirect coupling or communication connection of units or modules, which can be electrical or other forms.

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

[0120] In addition, each functional unit in each embodiment of the present application may be integrated into one processing unit, or each unit may exist physically separately, or two or more units may be integrated into one unit. The above-mentioned integrated unit may be implemented in the form of hardware or in the form of software functional units.

[0121] In the above embodiments, it can be implemented in whole or in part by software, hardware, firmware or any combination thereof. When implemented using software, it can be implemented in whole or in part in the form of 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, the process or function described in the embodiment of the present application is generated in whole or in part. 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 computer-readable storage medium. For example, the computer instructions can be transmitted from a website site, computer, server or data center by wired (e.g., coaxial cable, optical fiber, digital subscriber line (DSL)) or wireless (e.g., infrared, wireless, microwave, etc.) mode to another website site, computer, server or data center. The computer-readable storage medium can be any available medium that a computer can access, or a data storage device such as a server or data center that includes one or more available media integrated. The available medium may be a magnetic medium (e.g., a floppy disk, a hard disk, a magnetic tape), an optical medium (e.g., a digital versatile disc (DVD)), or a semiconductor medium (e.g., a solid state disk (SSD)). It is worth noting that the computer-readable storage medium mentioned in the embodiment of the present application may be a non-volatile storage medium, in other words, 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 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 relevant 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 three-dimensional virtual scene, the device information of the client, and the scene interaction information involved in the embodiments of this application are all obtained with full authorization.

[0123] The above is only a preferred implementation of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present application. These improvements and modifications should also be regarded as the scope of protection of the present application.

Claims

1. A rapid heating method of an air source heat pump unit, characterized in that: The air source heat pump unit includes a water circulation system and a refrigerant circulation system that are thermally coupled, and the rapid heating method includes: Obtaining the actual water temperature of a water tank of a water circulation system, and determining the rate of change of the actual water temperature with the actual water temperature during heating; Determining a target water temperature change rate according to the actual water temperature and the target water temperature; Determine the set parameter value of the operating parameter of the refrigerant circulation system based on the current working condition, and determine 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 operation of the refrigerant circulation system according to the target parameter value; Wherein, the operating parameters include at least one of the compressor frequency increase rate, the compressor air supplement amount and the compressor suction superheat.

2. The rapid heating method of the air source heat pump unit according to claim 1, characterized in that: Determining a target water temperature change rate according to the actual water temperature and the target water temperature includes: 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 condition, the higher the target water temperature, the greater the target water temperature change rate; under the same target water temperature condition, the higher the actual water temperature, the smaller the target water temperature change rate.

3. The rapid heating method of the air source heat pump unit according to claim 2, characterized in that: The target water temperature change rate satisfies the following formula: T' a1 =K1(T a -T s1 ); Where: T' a1 is the target water temperature change rate; K1 is the first proportional coefficient, and K1 < 1; T a is the target water temperature, T s1 The actual water temperature.

4. The rapid heating method of the air source heat pump unit according to claim 1, characterized in that: 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 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; Wherein, under the same conditions of the actual water temperature change rate and the target water temperature change rate, the larger the set parameter value, the larger the target parameter value; Under the same conditions of the actual water temperature change rate and the set parameter value, the greater the target water temperature change rate, the greater the target parameter value; Under the conditions of the same target water temperature change rate and the set parameter value, the greater the actual water temperature change rate, the smaller the target parameter value.

5. The rapid heating method of the air source heat pump unit according to claim 4, characterized in that: The target parameter value satisfies the following formula: Where: M a is 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 based on the set parameter values ​​of the current working conditions; T' a1 is the target water temperature change rate; T'1 is the target water temperature change rate.

6. The rapid heating method of the air source heat pump unit according to claim 1, characterized in that: The refrigerant circulation system includes an air-side heat exchanger, a water-side heat exchanger, a flash evaporator and a first electronic expansion valve, wherein the flash evaporator is arranged in a refrigerant pipeline between the air-side heat exchanger and the water-side heat exchanger, and the first electronic expansion valve is located in a refrigerant pipeline between the water-side heat exchanger and the flash evaporator. When the operating parameter includes the compressor air supply volume, the operation of the refrigerant circulation system is controlled according to the target parameter value, including: Obtain the suction pressure, supply pressure and exhaust pressure of the compressor; Determine the actual air supply pressure ratio of the compressor according to the suction pressure, the air supply pressure and the exhaust pressure, wherein the greater the actual air supply pressure ratio of the compressor, the greater the air supply volume of the compressor; When the actual air supply pressure specific gravity of the compressor is greater than the target air supply pressure specific gravity of the compressor, reducing the opening of the first electronic expansion valve; When the actual air supply pressure ratio of the compressor is less than the target air supply pressure ratio of the compressor, increasing the opening of the first electronic expansion valve; When the actual air supply pressure specific gravity of the compressor=the target air supply pressure specific gravity of the compressor, the current opening degree of the first electronic expansion valve is maintained.

7. The rapid heating method of the air source heat pump unit according to claim 6, characterized in that: Determining the actual air supply pressure ratio of the compressor according to the air intake pressure, the air supply pressure and the exhaust pressure includes: The actual charge pressure specific gravity of the compressor is a function of the suction pressure, charge pressure and discharge pressure; Wherein: under the condition that the suction pressure and the supplementary air pressure are the same, the greater the exhaust pressure is, the smaller the specific gravity of the actual supplementary air pressure is; Under the condition that the suction pressure and the exhaust pressure are the same, the greater the supplementary air pressure is, the greater the specific gravity of the actual supplementary air pressure is; Under the condition that the supplementary air pressure and the exhaust pressure are the same, the greater the intake pressure is, the smaller the specific gravity of the actual supplementary air pressure is.

8. The rapid heating method of the air source heat pump unit according to claim 7, characterized in that: The actual air supply pressure specific gravity of the compressor satisfies the following formula: Where: K m is the actual air supply pressure specific gravity of the compressor, P m P is the air supply pressure of the compressor; h is the exhaust pressure of the compressor; P l is the suction pressure of the compressor.

9. The rapid heating method of the air source heat pump unit according to claim 6, characterized in that: The refrigerant circulation system further includes a second electronic expansion valve, which is arranged in a refrigerant pipeline between the flash evaporator and the air-side heat exchanger. When the operating parameter includes the compressor suction superheat, the operation of the refrigerant circulation system is controlled according to the target parameter value, including: Get the suction temperature and suction pressure of the compressor; determining a saturation temperature corresponding to the suction pressure; determining the actual suction superheat of the compressor according to the suction temperature and the saturation temperature; When the actual suction superheat of the compressor is greater than the target parameter value of the suction superheat of the compressor, increasing 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, reducing the opening of the second electronic expansion valve; When the actual suction superheat of the compressor=the target parameter value of the suction superheat of the compressor, the current opening degree of the second electronic expansion valve is maintained.

10. A control device, characterized in that: The control device includes a memory and a processor, wherein the memory stores a rapid heating method for an air source heat pump unit, and the processor is used to adopt the rapid heating method for an air source heat pump unit according to any one of claims 1 to 9 when executing the rapid heating method for an air source heat pump unit.

11. An air source heat pump unit, characterized in that: The air source heat pump assembly operates according to the rapid heating method of the air source heat pump unit according to any one of claims 1-9, or has the control device according to claim 10.

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