Control methods for gas-injection enthalpy-increasing heat pump systems and heat pump systems

Abstract

This application belongs to the field of heat pump technology, specifically relating to a control method and a heat pump system for a gas-fuel-injection enthalpy-increasing heat pump system. The method includes: determining the initial opening degree of the main valve of the heat pump system based on the ambient temperature and outlet water temperature; determining whether to open the auxiliary valve of the heat pump system based on the ambient temperature and compressor frequency, and determining the initial opening degree of the auxiliary valve based on the ambient temperature and outlet water temperature; determining a main valve opening correction value based on at least two of the heat pump's suction temperature, exhaust temperature, evaporator coil temperature, liquid line temperature, and condensation temperature at a first time interval, and adjusting the main valve opening degree according to the main valve opening correction value; and determining an auxiliary valve opening correction value based on at least two of the heat pump system's ambient temperature, economizer auxiliary circuit inlet temperature, and economizer auxiliary circuit outlet temperature at a second time interval, and adjusting the auxiliary valve opening degree according to the auxiliary valve opening correction value. This method improves the control accuracy of the auxiliary valve and the main valve.

Description

Technical Field

[0001] This application belongs to the field of heat pump technology, specifically relating to a control method and a heat pump system for a gas-injection enthalpy-increasing heat pump system. Background Technology

[0002] In a gas-fuel-injection enthalpy-enhancing heat pump system, the main circuit is responsible for the system's regular cooling or heating cycle to ensure basic operation, while the auxiliary circuit increases the refrigerant mass flow rate into the compressor by introducing refrigerant gas with a higher enthalpy value into the compressor's gas injection port, thereby reducing the compression ratio and improving the system's efficiency and performance.

[0003] If the refrigerant flow in the main circuit is too high or too low, the system will be unable to adapt to changes in the environment and load, resulting in low system energy efficiency. If the refrigerant flow in the auxiliary circuit is too high, the system will become unstable due to excessive gas replenishment. If the refrigerant flow in the auxiliary circuit is too low, the gas replenishment effect will be poor due to insufficient gas replenishment, and the system energy efficiency ratio will decrease.

[0004] However, existing technologies have low precision in controlling the flow rate in the main and auxiliary circuits, resulting in low system energy efficiency ratio and stability. Therefore, it is necessary to design a control method for a gas-injection enthalpy-enhancing heat pump system to solve the above problems. Summary of the Invention

[0005] This application provides a control method and a heat pump system for a gas-injection enthalpy-increasing heat pump system, which solves the problem that the existing gas-injection enthalpy-increasing heat pump system has low control accuracy of flow in the main and auxiliary circuits, resulting in low energy efficiency ratio and stability of the system.

[0006] In a first aspect, this application provides a control method for a gas-fuel-injection enthalpy-increasing heat pump system, the method comprising:

[0007] Based on the ambient temperature and outlet water temperature of the heat pump system, the initial opening degree of the main valve of the heat pump system is determined, wherein the main valve is a heating main valve or a cooling main valve.

[0008] Based on the ambient temperature and compressor frequency of the heat pump system, it is determined whether to open the auxiliary valve of the heat pump system. If it is determined that the auxiliary valve should be opened, the initial opening degree of the auxiliary valve is determined based on the ambient temperature and outlet water temperature of the heat pump system. The auxiliary valve is used to regulate the refrigerant flow rate into the economizer auxiliary circuit of the heat pump system.

[0009] According to the first time interval, based on at least two of the suction temperature, exhaust temperature, evaporator coil temperature, liquid pipe temperature and condensation temperature of the heat pump system, the opening correction value of the main valve is determined, and the opening of the main valve is adjusted according to the opening correction value of the main valve.

[0010] According to the second time interval, based on at least two of the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit, the opening correction value of the auxiliary valve is determined, and the opening of the auxiliary valve is adjusted according to the opening correction value of the auxiliary valve.

[0011] Optionally, determining the initial opening degree of the main valve of the heat pump system based on the ambient temperature and outlet water temperature of the heat pump system includes:

[0012] After the heat pump system is turned on, the first initial opening degree of the main valve of the heat pump system is determined based on the ambient temperature and outlet water temperature of the heat pump system.

[0013] After the heat pump system has been running for a first time at the first initial opening of the main valve, the initial opening of the main valve of the heat pump system is determined based on the ambient temperature and outlet water temperature of the heat pump system.

[0014] Optionally, determining the main valve opening correction value based on at least two of the heat pump system's suction temperature, exhaust temperature, evaporator coil temperature, liquid line temperature, and condensation temperature includes:

[0015] The target intake superheat is determined based on the preset initial intake superheat and the exhaust temperature of the heat pump system.

[0016] The current actual suction superheat is determined based on the suction temperature and evaporator coil temperature of the heat pump system.

[0017] Based on the current actual intake superheat, the target intake superheat, and the previous actual intake superheat, determine the first opening correction value of the main valve;

[0018] The current actual subcooling is determined based on the condensing temperature and liquid pipe temperature of the heat pump system.

[0019] Based on the current actual subcooling and the preset target subcooling, determine the second opening correction value of the main valve;

[0020] The sum of the first opening correction value and the second opening correction value of the main valve is determined as the opening correction value of the main valve.

[0021] Optionally, determining the first opening correction value of the main valve based on the current actual intake superheat, the target intake superheat, and the previous actual intake superheat includes:

[0022] Based on the current actual inhalation superheat and the target inhalation superheat, determine the inhalation superheat deviation value;

[0023] The rate of change of intake superheat is determined based on the current actual intake superheat and the previous actual intake superheat.

[0024] The first opening correction value of the main valve is determined based on the intake superheat deviation value and the intake superheat change rate.

[0025] Optionally, determining the second opening correction value of the main valve based on the current actual subcooling and the preset target subcooling includes:

[0026] Based on the current actual subcooling and the preset target subcooling, determine the subcooling deviation value;

[0027] The second opening correction value of the main valve is determined based on the range to which the subcooling deviation value belongs.

[0028] Optionally, determining the opening correction value of the auxiliary valve based on at least two of the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit includes:

[0029] The target superheat of the economizer is determined based on the ambient temperature of the heat pump system.

[0030] The actual superheat of the economizer is determined based on the inlet temperature and outlet temperature of the economizer auxiliary circuit of the heat pump system.

[0031] The opening correction value of the auxiliary valve is determined based on the target superheat of the economizer, the current actual superheat of the economizer, and the previous actual superheat of the economizer.

[0032] Optionally, determining the opening correction value of the auxiliary valve based on the target superheat of the economizer, the current actual superheat of the economizer, and the previous actual superheat of the economizer includes:

[0033] The economizer overheat deviation value is determined based on the target overheat of the economizer and the current actual overheat of the economizer.

[0034] The rate of change of economizer overheat is determined based on the current actual overheat of the economizer and the previous actual overheat of the economizer.

[0035] The opening correction value of the auxiliary valve is determined based on the superheat deviation value of the economizer and the superheat change rate of the economizer.

[0036] Optionally, determining whether to open the auxiliary valve of the heat pump system based on the ambient temperature and compressor frequency of the heat pump system includes:

[0037] After the heat pump system has been running for a first preset time at the first initial opening of the main valve, it is determined whether to open the auxiliary valve of the heat pump system based on the ambient temperature of the heat pump system and the compressor frequency.

[0038] The step of determining the opening correction value of the auxiliary valve according to the second time interval, based on at least two of the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit, includes:

[0039] After the auxiliary valve is opened for a second preset time, the opening correction value of the auxiliary valve is determined according to the second time interval, based on the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit.

[0040] Secondly, this application provides a control device for a gas-fuel-injection enthalpy-increasing heat pump system, comprising:

[0041] The processing module is used to determine the initial opening degree of the main valve of the heat pump system based on the ambient temperature and outlet water temperature of the heat pump system. The main valve is either a heating main valve or a cooling main valve.

[0042] The processing module is also used to determine whether to open the auxiliary valve of the heat pump system based on the ambient temperature and compressor frequency of the heat pump system, and if it is determined that the auxiliary valve is to be opened, to determine the initial opening degree of the auxiliary valve based on the ambient temperature and outlet water temperature of the heat pump system. The auxiliary valve is used to regulate the refrigerant flow rate into the economizer auxiliary circuit of the heat pump system.

[0043] The processing module is further configured to determine the opening correction value of the main valve based on at least two of the suction temperature, exhaust temperature, evaporator coil temperature, liquid pipe temperature and condensation temperature of the heat pump system at a first time interval.

[0044] A control module is used to adjust the opening of the main valve according to the opening correction value of the main valve;

[0045] The processing module is further configured to determine the opening correction value of the auxiliary valve according to a second time interval, based on at least two of the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit.

[0046] The control module is also used to adjust the opening of the auxiliary valve according to the opening correction value of the auxiliary valve.

[0047] Optionally, the processing module is further configured to determine the first initial opening degree of the main valve of the heat pump system based on the ambient temperature and outlet water temperature of the heat pump system after the heat pump system is turned on.

[0048] The processing module is further configured to determine the initial opening of the main valve of the heat pump system based on the ambient temperature and outlet water temperature of the heat pump system after the heat pump system has been running for a first time at the first initial opening of the main valve.

[0049] Optionally, the processing module is further configured to determine the target intake superheat based on a preset initial intake superheat and the exhaust temperature of the heat pump system.

[0050] The processing module is also used to determine the current actual suction superheat based on the suction temperature and evaporator coil temperature of the heat pump system.

[0051] The processing module is also used to determine the first opening correction value of the main valve based on the current actual intake superheat, the target intake superheat, and the previous actual intake superheat.

[0052] The processing module is also used to determine the current actual subcooling based on the condensing temperature and liquid pipe temperature of the heat pump system;

[0053] The processing module is also used to determine the second opening correction value of the main valve based on the current actual subcooling and the preset target subcooling.

[0054] The processing module is further configured to determine the sum of the first opening correction value and the second opening correction value of the main valve as the opening correction value of the main valve.

[0055] Optionally, the processing module is further configured to determine an inhalation superheat deviation value based on the current actual inhalation superheat and the target inhalation superheat.

[0056] The processing module is also used to determine the rate of change of the intake superheat based on the current actual intake superheat and the previous actual intake superheat.

[0057] The processing module is further configured to determine the first opening correction value of the main valve based on the suction superheat deviation value and the suction superheat change rate.

[0058] Optionally, the processing module is further configured to determine a subcooling deviation value based on the current actual subcooling and the preset target subcooling;

[0059] The processing module is also used to determine the second opening correction value of the main valve based on the range to which the subcooling deviation value belongs.

[0060] Optionally, the processing module is further configured to determine the target superheat of the economizer based on the ambient temperature of the heat pump system;

[0061] The processing module is also used to determine the current actual superheat of the economizer based on the inlet temperature and outlet temperature of the economizer auxiliary circuit of the heat pump system.

[0062] The processing module is also used to determine the opening correction value of the auxiliary valve based on the target superheat of the economizer, the current actual superheat of the economizer, and the previous actual superheat of the economizer.

[0063] Optionally, the processing module is further configured to determine the economizer overheat deviation value based on the target superheat of the economizer and the current actual superheat of the economizer.

[0064] The processing module is also used to determine the rate of change of the economizer superheat based on the current actual superheat of the economizer and the previous actual superheat of the economizer.

[0065] The processing module is also used to determine the opening correction value of the auxiliary valve based on the superheat deviation value of the economizer and the superheat change rate of the economizer.

[0066] Optionally, the processing module is further configured to determine whether to open the auxiliary valve of the heat pump system based on the ambient temperature of the heat pump system and the compressor frequency after the heat pump system has been running for a first preset time according to the first initial opening of the main valve.

[0067] The processing module is further configured to, after the second preset time of opening the auxiliary valve, determine the opening correction value of the auxiliary valve according to the second time interval, based on the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit.

[0068] Thirdly, this application provides a heat pump system, including a controller, an economizer, a compressor, an evaporator, a condenser, a four-way valve, a heating main valve, a cooling main valve, and an auxiliary valve;

[0069] The compressor, the four-way valve, the evaporator, the heating main valve, and the economizer are connected in sequence, and the economizer is connected to the compressor; one end of the condenser is connected to the four-way valve, and the other end is connected to the economizer through the refrigeration main valve; the controller is electrically connected to the heating main valve, the refrigeration main valve, and the auxiliary valve respectively, and the controller is used to execute the control method of the gas-injection enthalpy-increasing heat pump system as described in the first aspect and / or various possible embodiments of the first aspect.

[0070] Optionally, the heat pump system further includes: a diversion control module, which is connected to the economizer and the evaporator respectively, to control the refrigerant flowing out of the evaporator to be diverted to the main circuit and the auxiliary circuit of the economizer during cooling, and / or to control the refrigerant flowing out of the economizer to be diverted to the auxiliary circuit and the evaporator during heating.

[0071] Fourthly, this application provides an electronic device, including: a memory and a processor;

[0072] The memory stores computer-executed instructions;

[0073] The processor executes computer execution instructions stored in the memory, causing the processor to perform the control method of the gas-injection enthalpy-increasing heat pump system as described in the first aspect and / or various possible embodiments of the first aspect.

[0074] Fifthly, this application provides a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, are used to implement the control method of the gas-injection enthalpy-increasing heat pump system as described in the first aspect and / or various possible embodiments of the first aspect.

[0075] Sixthly, this application provides a computer program product, including a computer program that, when executed by a processor, implements the control method of the gas-injection enthalpy-increasing heat pump system as described in the first aspect and / or various possible embodiments of the first aspect.

[0076] The control method for the gas-fuel-injection enthalpy-increasing heat pump system provided in this application, after determining the initial opening degree of the main valve of the heat pump, determines whether to open the auxiliary valve of the heat pump based on the ambient temperature of the heat pump and the compressor frequency. If it is determined that the auxiliary valve is open, the initial opening degree of the auxiliary valve is determined based on the ambient temperature of the heat pump and the outlet water temperature. According to a first time interval, the opening degree correction value of the main valve is determined based on the suction temperature, exhaust temperature, evaporator coil temperature, liquid pipe temperature and condensation temperature of the heat pump, and the opening degree of the main valve is adjusted according to the opening degree correction value of the main valve. According to a second time interval, the opening degree correction value of the auxiliary valve is determined based on the ambient temperature of the heat pump, the inlet temperature of the economizer auxiliary circuit and the outlet temperature of the economizer auxiliary circuit, and the opening degree of the auxiliary valve is adjusted according to the opening degree correction value of the auxiliary valve. In this way, the opening degree of the auxiliary valve and the main valve is corrected according to the adjustment cycle of the main valve and the auxiliary valve, which improves the control accuracy of the auxiliary valve and the main valve, and improves the energy efficiency ratio and stability of the heat pump system. Attached Figure Description

[0077] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application.

[0078] Figure 1 This is a schematic diagram of the gas-injection enthalpy-increasing heat pump system provided in this application. Figure 1 ;

[0079] Figure 2 This is a schematic diagram of the gas-injection enthalpy-increasing heat pump system provided in this application. Figure 2 ;

[0080] Figure 3 The flow chart of the control method for the gas-injection enthalpy-increasing heat pump system provided in this application Figure 1 ;

[0081] Figure 4 The flow chart of the control method for the gas-injection enthalpy-increasing heat pump system provided in this application Figure 2 ;

[0082] Figure 5 The flow chart of the control method for the gas-injection enthalpy-increasing heat pump system provided in this application Figure 3 ;

[0083] Figure 6 A schematic diagram of the control device for the gas-injection enthalpy-increasing heat pump system provided in this application;

[0084] Figure 7 A schematic diagram of the structure of the electronic device provided in this application.

[0085] Explanation of reference numerals in the attached figures:

[0086] 1-Compressor; 2-Four-way valve; 3-Condenser; 4-Econverter; 5-Distributor; 6-Evaporator; 7-Refrigeration main valve; 8-Heating main valve; 9-Auxiliary valve;

[0087] 11-Intake temperature sensor; 12-Exhaust temperature sensor; 13-First gas-liquid separator; 14-Second gas-liquid separator;

[0088] 31-Pressure sensor; 32-Outlet water temperature sensor;

[0089] 41 - First entrance / exit of main road; 42 - Second entrance / exit of main road; 43 - Entrance of auxiliary road; 44 - Exit of auxiliary road; 45 - Temperature sensor at the entrance of auxiliary road; 46 - Temperature sensor at the exit of auxiliary road;

[0090] 51 - Auxiliary port of flow divider 5; 52 - Main port of flow divider 5; 53 - Connecting port of flow divider 5;

[0091] 61 - Evaporator coil temperature sensor; 62 - Liquid line temperature sensor.

[0092] The accompanying drawings have illustrated specific embodiments of this application, which will be described in more detail below. These drawings and descriptions are not intended to limit the scope of the concept in any way, but rather to illustrate the concept of this application to those skilled in the art through reference to specific embodiments. Detailed Implementation

[0093] To make the objectives, technical solutions, and advantages of this application clearer, the technical solutions of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0094] The terms "first," "second," "third," "fourth," etc. (if present) in the specification, claims, and accompanying drawings of this invention are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that embodiments of the invention described herein can be implemented in orders other than those illustrated or described herein.

[0095] In this application, the terms "exemplary" or "for example" are used to indicate examples, illustrations, or descriptions. Any embodiment or design described as "exemplary" or "for example" in this application should not be construed as being more preferred or advantageous than other embodiments or designs. Specifically, the use of terms such as "exemplary" or "for example" is intended to present the relevant concepts in a specific manner.

[0096] Existing refrigerant injection heat pump systems have corresponding valves in the main circuit and auxiliary circuit, namely main valves and auxiliary valves. The main valve is used to control the refrigerant flow rate in the main circuit. By adjusting the opening of the main valve, the system can adapt to different ambient temperatures and load changes, ensuring efficient and stable operation under various operating conditions. The auxiliary valve is used to control the refrigerant flow rate in the auxiliary circuit. By adjusting the opening of the auxiliary valve, the refrigerant injection process can be ensured to proceed smoothly. If the refrigerant flow rate in the auxiliary circuit is too high, it will cause system instability due to excessive refrigerant injection; if the refrigerant flow rate in the auxiliary circuit is too low, it will result in low refrigerant injection efficiency and a decrease in the system's energy efficiency ratio.

[0097] Therefore, the control precision of the main valve and auxiliary valve in the existing gas-fuel-injection heat pump system needs to be further optimized to improve the system's energy efficiency ratio and stability.

[0098] In view of this, this application provides a control method for a gas-fuel-injection enthalpy-increasing heat pump system. The method determines the initial opening degree of the main valve of the heat pump system based on the ambient temperature and the outlet water temperature. After a preset compressor running time, it determines whether to open the auxiliary valve of the heat pump system based on the ambient temperature and the current compressor frequency. If it is determined that the auxiliary valve should be opened, the initial opening degree of the auxiliary valve is determined based on the current ambient temperature and the outlet water temperature. When adjusting the main valve, the method adjusts the main valve according to a first time interval based on the heat pump system's suction temperature, discharge temperature, evaporator coil temperature, liquid line temperature, and condensation temperature. The method involves determining the opening correction value of the main valve and adjusting its opening accordingly. When adjusting the auxiliary valve, the opening correction value of the auxiliary valve is determined based on the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit, according to the second time interval. The opening of the auxiliary valve is then adjusted accordingly. This method achieves the correction of the opening of the auxiliary and main valves according to their respective adjustment cycles, improving the control accuracy of the auxiliary and main valves and thus improving the energy efficiency ratio and stability of the gas-fuel-injection enthalpy-increasing heat pump system.

[0099] The technical solution of this application and how the technical solution of this application solves the above-mentioned technical problems are described in detail below with specific embodiments. These specific embodiments can be combined with each other, and the same or similar concepts or processes may not be described again in some embodiments. The embodiments of this application will be described below with reference to the accompanying drawings.

[0100] Figure 1 A schematic diagram of the structure of the gas-injection enthalpy-increasing heat pump system provided in the embodiments of this application. Figure 1 .like Figure 1 As shown, the gas-fuel-injection heat pump system includes: a compressor 1, a four-way valve 2, a condenser 3, an economizer 4, a flow divider 5, an evaporator 6, a refrigeration main valve 7, a heating main valve 8, and an auxiliary valve 9. The condenser 3 is connected to the first inlet / outlet 41 of the main circuit of the economizer 4 via the refrigeration main valve 7. The second inlet / outlet 42 of the main circuit of the economizer 4 is connected to the main port 52 of the flow divider 5. The connecting port 53 of the flow divider 5 is connected to the evaporator 6 via the heating main valve 8. The auxiliary port 51 of the flow divider 5 is connected to the auxiliary inlet 43 of the economizer 4 via the auxiliary valve 9. The auxiliary outlet 44 of the economizer is connected to the gas-fuel injection port of the compressor 1.

[0101] Figure 1When the gas-filled enthalpy-increasing heat pump system is in heating mode, the main cooling valve 7 is fully open. The main heating valve 8 and the auxiliary valve 9 regulate the refrigerant flow rate of the main circuit and the refrigerant flow rate of the auxiliary circuit, respectively. At this time, the high-temperature and high-pressure refrigerant gas is discharged from the exhaust port of the compressor 1 and flows into the condenser 3 through the four-way valve 2. In the condenser 3, the high-temperature and high-pressure refrigerant vapor exchanges heat with the water circuit, and after heating the water circuit, it becomes a low-temperature and high-pressure refrigerant. It then flows into the economizer 4 from the first inlet / outlet 41 of the main circuit. After exchanging heat with the auxiliary circuit and cooling down in the economizer 4, it flows into the splitter 5 from the main outlet 52 of the splitter 5 and is divided into two in the splitter 5.

[0102] The refrigerant in the main circuit flows upward from the connection port 53 of the diversion device 5 to the evaporator 6. After being throttled into a low-temperature and low-pressure refrigerant fluid in the heating main valve 8, it enters the evaporator 6 and exchanges heat with the air. After absorbing heat from the air, the refrigerant passes through the four-way valve 2 and the first gas-liquid separator 13 and then enters the compressor 1 from the air inlet of the compressor 1.

[0103] The refrigerant in the auxiliary circuit flows out from the auxiliary port 51 of the diverter 5, is throttled into a low-temperature, low-pressure refrigerant fluid by the auxiliary valve 9, and then flows through the economizer 4 to be heated and turned into gas. It then enters the compressor 1 through the gas supply port 12 of the compressor 1. It is mixed with the refrigerant in the compressor 1 from the main circuit and then compressed into a high-temperature, high-pressure gas by the compressor 1 and discharged through the exhaust port of the compressor 1. This cycle repeats continuously.

[0104] Figure 1 When the gas-filling enthalpy-increasing heat pump system is in cooling mode, the heating main valve 8 is fully open, and the refrigerant flow rate in the system is regulated by the cooling main valve 7 and the auxiliary valve 9. At this time, the high-temperature and high-pressure refrigerant gas is discharged from the exhaust port of the compressor 1 and flows into the evaporator 6 through the four-way valve 2. In the evaporator 6, it exchanges heat with the outdoor air to form medium-temperature and high-pressure refrigerant vapor. The medium-temperature and high-pressure refrigerant vapor enters the distribution device 5 from the connection port 53 of the distribution device 5 and is divided into two in the distribution device 5.

[0105] The refrigerant path of the auxiliary circuit is similar to that of the heat pump system in heating mode, and will not be described in detail here.

[0106] The refrigerant in the main circuit first flows into the economizer 4 from the second inlet / outlet 42 of the main circuit. After being cooled by the refrigerant in the auxiliary circuit in the economizer 4, it flows out from the first inlet / outlet 41 of the main circuit and flows to the main refrigeration valve 7. After being throttled into a low-temperature and low-pressure refrigerant by the main refrigeration valve 7, it exchanges heat with the water circuit in the condenser 3 to cool the water circuit. After flowing out from the condenser 3, it enters the air inlet of the compressor 1 through the four-way valve 2 and the second gas-liquid separator 14. After mixing with the make-up gas in the compressor 1, it is compressed into a high-temperature and high-pressure gas by the compressor 1 and discharged through the exhaust port of the compressor 1. This cycle repeats continuously.

[0107] In order to improve Figure 1 The control accuracy of the heating main valve and cooling main valve in the aforementioned gas-injection enthalpy-increasing heat pump system is crucial. Therefore, it is necessary to detect the operating parameters of the heat pump system and control the system based on the detected parameters.

[0108] Figure 2 This is a schematic diagram of the structure of the gas-injection enthalpy-increasing heat pump system provided in the embodiments of this application. Figure 2 Please see Figure 1 and Figure 2 The suction temperature sensor 11 is disposed between the four-way valve 2 and the first gas-liquid separator 13. The suction temperature sensor 11 is used to detect the temperature of the refrigerant entering the intake port of the compressor 1. The first gas-liquid separator 13 is used to separate the gaseous and liquid refrigerant entering the compressor 1 to ensure that only gaseous refrigerant enters the intake port of the compressor 1, thereby preventing liquid slugging. The discharge temperature sensor 12 is disposed between the four-way valve 2 and the discharge port of the compressor 1. The discharge temperature sensor 12 is used to detect the temperature of the refrigerant gas discharged from the discharge port of the compressor 1.

[0109] Pressure sensor 31 is installed between four-way valve 2 and condenser 3. Pressure sensor 31 is used to detect the high pressure when the heat pump is heating and the low pressure when it is cooling. Water outlet temperature sensor 32 is used to detect the water temperature of the water outlet pipe that exchanges heat with condenser 3.

[0110] The auxiliary inlet temperature sensor 45 is located between the auxiliary valve 9 and the auxiliary inlet 43 of the economizer 4. The auxiliary inlet temperature sensor 45 is used to detect the temperature of the auxiliary refrigerant flowing out of the auxiliary valve 9. The auxiliary outlet temperature sensor 46 is located between the economizer 4 and the second gas-liquid separator 14. The auxiliary outlet temperature sensor 46 is used to detect the temperature of the auxiliary refrigerant flowing out of the auxiliary outlet 44 of the economizer 4. The second gas-liquid separator is used to separate the gaseous and liquid refrigerant entering the gas supply port of the compressor 1, ensuring that only gaseous refrigerant enters the gas supply port of the compressor 1 and preventing liquid slugging.

[0111] Evaporator coil temperature sensor 61 is located on the outer surface of the coil of evaporator 6 and is used to detect the temperature of evaporator coil; liquid line temperature sensor 62 is used to detect the temperature of refrigerant in the pipe between the distributor 5 and the heating main valve 8.

[0112] In some embodiments, the gas-fuel enthalpy-increasing heat pump system further includes a controller (not shown), the controller being configured to... Figure 2 The operating parameters detected by the various sensors in the system are used to adjust the operating parameters of the heat pump.

[0113] The technical solutions of this application and how they solve the aforementioned technical problems are described in detail below with specific embodiments. These specific embodiments can be implemented independently or in combination with each other. Identical or similar concepts or processes may not be repeated in some embodiments. The embodiments of this application will now be described with reference to the accompanying drawings.

[0114] Figure 3 The flow chart of the control method for the gas-injection enthalpy-increasing heat pump system provided in the embodiments of this application Figure 1 This embodiment is applied to, for example Figure 1 or Figure 2 The gas-injection enthalpy-increasing heat pump system shown in this embodiment can be implemented by, for example, the controller of the gas-injection enthalpy-increasing heat pump system. The implementation scenario of this embodiment can be, for example, as follows: Figure 1 The scenario described in the embodiment of the gas-injection enthalpy-increasing heat pump system operating in cooling mode can also be the scenario of operating in heating mode. For example... Figure 3 As shown, the control method for the gas-injection enthalpy-increasing heat pump system provided in this embodiment includes:

[0115] S301. Based on the ambient temperature and outlet water temperature of the heat pump system, determine the initial opening degree of the main valve of the heat pump system.

[0116] The main valve is either a heating main valve or a cooling main valve, corresponding to the heating mode or cooling mode of the heat pump system, respectively. The ambient temperature is obtained, for example, by an ambient temperature sensor installed outdoors, and the outlet water temperature is obtained, for example, by... Figure 2 The water temperature is detected by the outlet water temperature sensor 32 in the embodiment.

[0117] Understandably, the initial opening degree of the main valve is crucial to the stability of the heat pump system during the initial startup phase. If the initial opening degree of the main valve is not set properly, it may lead to unstable refrigerant flow and affect the stable operation of the system. Therefore, the optimal initial opening degree under different ambient temperature and water temperature conditions can be determined through testing and data analysis and integrated into the controller.

[0118] For example, a specific implementation method for determining the optimal initial opening of the main valve under different ambient and water temperature conditions is given here: Select a test initial opening as the starting point, and select different combinations of ambient and outlet water temperatures to form a test condition. Start the heat pump under this test condition and record the operating status of the heat pump after startup, including compressor frequency, condenser and evaporator temperature, pressure, etc. If the heat pump system fails to quickly enter a stable state, gradually adjust the opening of the main valve until the system is running stably. Then, record the optimal main valve opening under each combination of ambient and outlet water temperature so that in the subsequent actual operation of the heat pump, the main valve opening corresponding to the current ambient temperature and current outlet water temperature of the heat pump can be found based on the test results and used as the initial opening of the heat pump's main valve.

[0119] In some embodiments, after the heat pump system is started up, the initial opening degree also needs to be adjusted accordingly as the ambient temperature and outlet water temperature change. For example, after the heat pump system is started up, the first initial opening degree of the main valve of the heat pump system is determined based on the ambient temperature and outlet water temperature of the heat pump system.

[0120] After the heat pump system has been running at its initial main valve opening for a period of time, the initial opening of the main valve is determined based on the ambient temperature and outlet water temperature of the heat pump system. Here, both the initial and adjusted initial opening of the main valve are determined based on the aforementioned test results, according to the optimal main valve opening corresponding to the current actual ambient temperature and outlet water temperature.

[0121] S302. Based on the ambient temperature and compressor frequency of the heat pump system, determine whether to open the auxiliary valve of the heat pump system, and if it is determined that the auxiliary valve should be opened, determine the initial opening degree of the auxiliary valve based on the ambient temperature and outlet water temperature of the heat pump system.

[0122] The compressor frequency is determined based on the ambient temperature and the outlet water temperature. For example, the compressor frequency can be calculated using the following formula:

[0123]

[0124] Where F is the compressor frequency, For ambient temperature, The outlet water temperature, , , It is a constant parameter.

[0125] In some embodiments, after the heat pump system has been running for a first preset time at the first initial opening of the main valve, it is determined whether to open the auxiliary valve of the heat pump system based on the ambient temperature of the heat pump system and the compressor frequency.

[0126] Understandably, in the initial stage of the heat pump operating at the first initial opening of the main valve, the system is not yet fully stable, so the auxiliary valve is closed. After the heat pump system has been operating at the first initial opening of the main valve for a period of time, the initial opening of the main valve is confirmed and it is determined whether the auxiliary valve meets the opening conditions.

[0127] The opening conditions for the auxiliary valve can be, for example, that the auxiliary valve is opened when the ambient temperature is less than b℃ and the compressor frequency is greater than c Hz. This is because when the ambient temperature is too low, the heating capacity of the heat pump system will decrease. Opening the auxiliary valve to replenish gas and increase enthalpy can improve the system's heating capacity. At the same time, when the compressor is running at a high frequency, it indicates a high system load. As the compressor's pressure ratio increases, the system's energy efficiency ratio will decrease and the discharge temperature will rise rapidly. Opening the auxiliary valve can increase the refrigerant circulation during the compression process, reduce the compressor's discharge temperature, and improve the system's energy efficiency ratio.

[0128] For example, the initial opening degree of the auxiliary valve can be determined by setting a preset ambient temperature threshold and a preset outlet water temperature threshold. The preset ambient temperature threshold includes a low ambient temperature threshold (-20℃) and a high ambient temperature threshold (-10℃); the preset outlet water temperature threshold includes a low outlet water temperature threshold (25℃) and a high outlet water temperature threshold (35℃).

[0129] When the actual ambient temperature is below -20℃ and the actual outlet water temperature is less than 25℃, the initial opening of the auxiliary valve is relatively large; when the actual ambient temperature is in the range of [-20℃, -10℃] and the actual outlet water temperature is in the range of [25℃, 35℃], the initial opening of the auxiliary valve is moderate; when the actual ambient temperature is in the range of [-10℃, b℃] and the actual outlet water temperature is greater than 35℃, b℃ is the ambient temperature at which the auxiliary valve is determined to open, and the initial opening of the auxiliary valve is relatively small.

[0130] S303. Based on at least two of the following: the suction temperature, exhaust temperature, evaporator coil temperature, liquid pipe temperature, and condensation temperature of the heat pump system, determine the opening correction value of the main valve according to the first time interval, and adjust the opening of the main valve according to the opening correction value of the main valve.

[0131] The first time interval refers to the adjustment cycle of the main valve. The first time interval can be adaptively adjusted according to the change of exhaust temperature. For example, when the exhaust temperature is above the target exhaust temperature d℃, the valve adjustment cycle is tp1. When the exhaust temperature is greater than e℃ and less than d℃, the valve adjustment cycle is tp2.

[0132] For example, the current actual suction superheat is determined based on the suction temperature and evaporator coil temperature, and the current target suction superheat is determined based on the exhaust temperature and ambient temperature; the current actual subcooling is determined based on the condenser temperature and liquid line temperature; then the current actual suction superheat is compared with the target suction superheat, and the current actual subcooling is compared with the preset target subcooling, thereby determining the correction value of the main valve, and adjusting the opening of the main valve based on the initial opening of the main valve using the opening correction value.

[0133] S304. According to the second time interval, based on at least two of the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit, determine the opening correction value of the auxiliary valve, and adjust the opening of the auxiliary valve according to the opening correction value of the auxiliary valve.

[0134] The second time interval refers to the adjustment cycle of the auxiliary valve.

[0135] In some embodiments, after a second preset time for opening the auxiliary valve, the opening correction value of the auxiliary valve is determined based on the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit, according to a second time interval.

[0136] Understandably, after the heat pump has been running for a second preset time at the initial opening of the auxiliary valve, the system's heat load will change as the ambient temperature changes. At this time, the opening of the auxiliary valve also needs to be adjusted based on the change in heat load in order to optimize the system's operating state and improve the system's energy efficiency ratio.

[0137] For example, based on the ambient temperature, the target superheat of the economizer is determined. Then, based on the inlet temperature and outlet temperature of the economizer's auxiliary circuit, the actual superheat of the economizer is determined. By comparing the actual superheat of the economizer with the target superheat, the opening correction value of the auxiliary valve is determined. Based on this opening correction value, the opening of the auxiliary valve is adjusted from its initial opening.

[0138] The control method for the gas-fuel-injection enthalpy-increasing heat pump system provided in this embodiment determines the initial opening degree of the main valve of the heat pump system based on the ambient temperature and outlet water temperature of the heat pump. It then determines whether to open the auxiliary valve of the heat pump based on the ambient temperature and compressor frequency. If the auxiliary valve is determined to be open, the initial opening degree of the auxiliary valve is determined based on the ambient temperature and outlet water temperature. At a first time interval, a correction value for the main valve opening degree is determined based on at least two of the heat pump's suction temperature, exhaust temperature, evaporator coil temperature, liquid line temperature, and condensation temperature. The main valve opening degree is adjusted according to this correction value. At a second time interval, a correction value for the auxiliary valve opening degree is determined based on the ambient temperature, economizer auxiliary circuit inlet temperature, and economizer auxiliary circuit outlet temperature. The auxiliary valve opening degree is adjusted according to this correction value. This method achieves correction of the opening degrees of the auxiliary and main valves according to their respective adjustment cycles, improving the control accuracy of the auxiliary and main valves and enhancing the energy efficiency ratio and stability of the heat pump system.

[0139] Figure 4 The flow chart of the control method for the gas-injection enthalpy-increasing heat pump system provided in the embodiments of this application Figure 2 This embodiment is... Figure 3 Based on the embodiments, a method for determining the main valve opening correction value based on at least two of the following: the suction temperature, exhaust temperature, evaporator coil temperature, liquid line temperature, and condensation temperature of the heat pump system is described in detail. Figure 4 As shown, the control method for the gas-injection enthalpy-increasing heat pump system provided in this embodiment includes:

[0140] S401. Determine the target intake superheat based on the preset initial intake superheat and the exhaust temperature of the heat pump system.

[0141] Among them, the exhaust temperature can be Figure 2 The temperature of the refrigerant discharged from the compressor's exhaust port detected by the exhaust temperature sensor 12 in the embodiment is preset based on the ambient temperature.

[0142] For example, the target intake superheat can be calculated using the following formula:

[0143]

[0144] in, To achieve the target intake superheat, The preset initial intake superheat. This is the exhaust temperature correction value. It is determined based on the exhaust temperature of the heat pump, with the aim of utilizing the exhaust temperature and initial suction superheat. Added together, the target intake superheat This allows for adjustments to be made so that when the exhaust temperature is low, the compressor can be prevented from being liquid-slugged by prioritizing the determination of the target intake superheat.

[0145] S402. Determine the current actual suction superheat based on the suction temperature and evaporator coil temperature of the heat pump system.

[0146] The intake temperature can be achieved by... Figure 2 In this embodiment, the suction temperature sensor 11 detects the temperature of the refrigerant drawn into the compressor's intake port; the evaporator coil temperature is determined by... Figure 2 The evaporator coil temperature sensor 61 in the embodiment detects the temperature at the middle part of the evaporator flow path, and the evaporator coil temperature here can be used to indicate the saturated evaporation temperature of the refrigerant.

[0147] For example, the difference between the heat pump's suction temperature and the evaporator coil temperature can be used as the current actual suction superheat.

[0148] S403. Based on the current actual intake superheat, the target intake superheat, and the previous actual intake superheat, determine the first opening correction value of the main valve.

[0149] For example, the intake superheat deviation value can be determined first based on the current actual intake superheat and the target intake superheat.

[0150] For example, a formula can be used. The suction superheat deviation value was calculated, where, This is the deviation value for intake superheat. This represents the actual intake superheat. The target is the intake superheat.

[0151] The rate of change of intake superheat is determined based on the current actual intake superheat and the previous actual intake superheat.

[0152] For example, the rate of change of intake superheat can be calculated using the following formula:

[0153]

[0154] in, The rate of change of intake superheat. This represents the current actual intake superheat. This is the actual intake superheat from the previous test. This is the first time interval, which is the adjustment cycle of the main valve.

[0155] Based on the suction superheat deviation value and the suction superheat change rate, determine the first opening correction value of the main valve. For example, based on different suction superheat deviation values... and rate of change of intake superheat The corresponding first opening correction value n1 is obtained by looking up the table of the first opening correction value. The unit of the first opening correction value n1 is steps.

[0156] S404. Determine the current actual subcooling based on the condensing temperature and liquid pipe temperature of the heat pump system.

[0157] In the heat pump's heating mode, the condensing temperature refers to the temperature determined by... Figure 2 The saturation temperature is calculated from the pressure detected by pressure sensor 31 in the embodiment; while in the heat pump's cooling mode, the condensation temperature refers to the temperature obtained by... Figure 2 The temperature of the middle part of the evaporator flow path is detected by the evaporator coil temperature sensor 61; the liquid line temperature can be detected by... Figure 2 The liquid pipe temperature sensor 62 in the embodiment detects the temperature of the refrigerant in the pipe between the distributor and the heating main valve.

[0158] For example, the difference between the condensing temperature and the liquid pipe temperature of a heat pump system can be used as the current actual subcooling.

[0159] S405. Determine the second opening correction value of the main valve based on the current actual subcooling and the preset target subcooling.

[0160] In one possible implementation, the subcooling deviation value can be determined based on the current actual subcooling and the preset target subcooling, and then the second opening correction value of the main valve can be determined based on the range to which the subcooling deviation value belongs.

[0161] Understandably, the difference between the preset target subcooling and the actual subcooling can be used as the subcooling deviation value. Then, from multiple preset subcooling ranges, the range to which the current subcooling deviation value belongs can be determined, and the correction value corresponding to that range can be used as the second opening correction value n2 of the main valve.

[0162] For example, there are multiple preset subcooling ranges: [0℃, 5℃], [5℃, 10℃], and [10℃, 15℃]. The second opening correction value for the subcooling range [0℃, 5℃] is 'a' steps. If 'a' is negative, it means that the main valve should be reduced by 'a' steps from its initial opening. The second opening correction value for the subcooling range [5℃, 10℃] is 'b' steps. If 'b' is negative, it means that the main valve should be reduced by 'b' steps from its initial opening.

[0163] S406. The sum of the first opening correction value and the second opening correction value of the main valve is determined as the opening correction value of the main valve.

[0164] For example, if the first opening correction value is n1 steps and the second opening correction value is n2 steps, then the total opening correction value of the main valve is n1 + n2. If the main valve opening is 100 steps, then the main valve opening adjusted according to the main valve opening correction value is (100 + n1 + n2) steps.

[0165] The control method for the gas-injection enthalpy-increasing heat pump system provided in this embodiment determines the target suction superheat based on a preset initial suction superheat and the exhaust temperature of the heat pump system. It then determines the current actual suction superheat based on the suction temperature and evaporator coil temperature of the heat pump system. Based on the current actual suction superheat, the target suction superheat, and the previous actual suction superheat, it determines the first opening correction value of the main valve. Finally, it determines the current actual subcooling based on the condensing temperature and liquid line temperature of the heat pump system. Based on the current actual subcooling and the preset target subcooling, it determines the second opening correction value of the main valve. The sum of the first and second opening correction values ​​of the main valve is then used to determine the main valve's opening correction value. This method improves the accuracy of correcting the main valve opening, thereby improving the heat pump's energy efficiency ratio.

[0166] Figure 5 The flow chart of the control method for the gas-injection enthalpy-increasing heat pump system provided in the embodiments of this application Figure 3 This embodiment is... Figure 3 Based on the embodiments, a method for determining the opening correction value of the auxiliary valve based on at least two of the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit is described in detail. Figure 5 As shown, the control method for the gas-injection enthalpy-increasing heat pump system provided in this embodiment includes:

[0167] S501. Determine the target superheat of the economizer based on the ambient temperature of the heat pump system.

[0168] The economizer's function is to evaporate the liquid refrigerant in the auxiliary circuit into gas. This gaseous refrigerant is then used as makeup gas and drawn into the compressor through the compressor's makeup gas port, thereby improving the heat pump's heating / cooling performance. The purpose of setting the economizer's target superheat is to ensure that the makeup gas enters the compressor in a completely gaseous state, avoiding liquid refrigerant entering the compressor and causing liquid slugging.

[0169] Therefore, the target superheat of the economizer can be determined based on the linear relationship between the ambient temperature of the heat pump and the target superheat of the economizer.

[0170] S502. Determine the current actual superheat of the economizer based on the inlet temperature and outlet temperature of the economizer auxiliary circuit of the heat pump system.

[0171] Among them, the inlet temperature of the auxiliary circuit of the economizer is, for example, through... Figure 2 The temperature of the refrigerant liquid detected by the auxiliary circuit inlet temperature sensor 45 in the embodiment, and the economizer auxiliary circuit outlet temperature, for example, are... Figure 2 The temperature of the refrigerant gas detected by the auxiliary outlet temperature sensor 46 in the embodiment.

[0172] For example, the difference between the outlet temperature and the inlet temperature of the economizer's auxiliary circuit can be used as the current actual superheat of the economizer. The magnitude of the actual superheat of the economizer reflects the effectiveness of heat exchange between the auxiliary circuit and the main circuit. The higher the actual superheat of the economizer, the better the evaporation effect of the refrigerant in the auxiliary circuit; conversely, the lower the actual superheat, the worse the evaporation effect of the refrigerant in the auxiliary circuit, which will affect the gas supply effect.

[0173] S503. Determine the auxiliary valve opening correction value based on the target superheat of the economizer, the current actual superheat of the economizer, and the previous actual superheat of the economizer.

[0174] In one possible implementation, the economizer overheat deviation value can be determined based on the target overheat value and the current actual overheat value of the economizer. For example, the difference between the actual overheat value and the target overheat value of the economizer can be used as the economizer overheat deviation value.

[0175] The rate of change of the overheating of the economizer is determined based on the current actual overheating of the economizer and the previous actual overheating of the economizer. For example, the difference between the current actual overheating of the economizer and the previous actual overheating of the economizer is taken as the first difference, and the ratio between the first difference and the second time interval is taken as the rate of change of the overheating of the economizer.

[0176] Finally, based on the economizer superheat deviation value and the economizer superheat change rate, the auxiliary valve opening correction value is determined. If the auxiliary valve opening correction value is n3, and the auxiliary valve opening is 150 steps, then the corrected auxiliary valve opening is (150+n3) steps.

[0177] The control method for the gas-fuel-injection enthalpy-increasing heat pump system provided in this embodiment determines the target superheat of the economizer based on the ambient temperature of the heat pump system, determines the current actual superheat of the economizer based on the inlet temperature and outlet temperature of the economizer auxiliary circuit, and determines the opening correction value of the auxiliary valve based on the target superheat of the economizer, the current actual superheat of the economizer, and the previous actual superheat of the economizer. This method improves the accuracy of the correction of the auxiliary valve opening, thereby improving the energy efficiency ratio and system stability of the heat pump system.

[0178] Figure 6 A schematic diagram of the control device for the gas-fuel-injection enthalpy-increasing heat pump system provided in this application. Figure 6As shown, this application provides a control device for a gas-injection enthalpy-increasing heat pump system. The control device 600 of the gas-injection enthalpy-increasing heat pump system includes:

[0179] The processing module 601 is used to determine the initial opening degree of the main valve of the heat pump system based on the ambient temperature and outlet water temperature of the heat pump system. The main valve is either a heating main valve or a cooling main valve.

[0180] The processing module 601 is further configured to determine whether to open the auxiliary valve of the heat pump system based on the ambient temperature and compressor frequency of the heat pump system, and if it is determined that the auxiliary valve is to be opened, to determine the initial opening degree of the auxiliary valve based on the ambient temperature and outlet water temperature of the heat pump system. The auxiliary valve is used to regulate the refrigerant flow rate into the economizer auxiliary circuit of the heat pump system.

[0181] The processing module 601 is further configured to determine the opening correction value of the main valve based on at least two of the suction temperature, exhaust temperature, evaporator coil temperature, liquid pipe temperature and condensation temperature of the heat pump system according to a first time interval.

[0182] Control module 602 is used to adjust the opening of the main valve according to the opening correction value of the main valve;

[0183] The processing module 601 is further configured to determine the opening correction value of the auxiliary valve according to a second time interval, based on at least two of the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit.

[0184] The control module 602 is also used to adjust the opening of the auxiliary valve according to the opening correction value of the auxiliary valve.

[0185] Optionally, the processing module 601 is further configured to determine the first initial opening degree of the main valve of the heat pump system based on the ambient temperature and outlet water temperature of the heat pump system after the heat pump system is turned on.

[0186] The processing module 601 is further configured to determine the initial opening of the main valve of the heat pump system based on the ambient temperature and outlet water temperature of the heat pump system after the heat pump system has been running for a first time at the first initial opening of the main valve.

[0187] Optionally, the processing module 601 is further configured to determine the target intake superheat based on the preset initial intake superheat and the exhaust temperature of the heat pump system.

[0188] The processing module 601 is also used to determine the current actual suction superheat based on the suction temperature and evaporator coil temperature of the heat pump system.

[0189] The processing module 601 is further configured to determine the first opening correction value of the main valve based on the current actual intake superheat, the target intake superheat, and the previous actual intake superheat.

[0190] The processing module 601 is also used to determine the current actual subcooling based on the condensing temperature and liquid pipe temperature of the heat pump system.

[0191] The processing module 601 is further configured to determine the second opening correction value of the main valve based on the current actual subcooling and the preset target subcooling.

[0192] The processing module 601 is further configured to determine the sum of the first opening correction value and the second opening correction value of the main valve as the opening correction value of the main valve.

[0193] Optionally, the processing module 601 is further configured to determine an intake superheat deviation value based on the current actual intake superheat and the target intake superheat.

[0194] The processing module 601 is also used to determine the rate of change of the intake superheat based on the current actual intake superheat and the previous actual intake superheat.

[0195] The processing module 601 is further configured to determine the first opening correction value of the main valve based on the intake superheat deviation value and the intake superheat change rate.

[0196] Optionally, the processing module 601 is further configured to determine a subcooling deviation value based on the current actual subcooling and the preset target subcooling.

[0197] The processing module 601 is further configured to determine the second opening correction value of the main valve based on the range to which the subcooling deviation value belongs.

[0198] Optionally, the processing module 601 is further configured to determine the target superheat of the economizer based on the ambient temperature of the heat pump system;

[0199] The processing module 601 is also used to determine the current actual superheat of the economizer based on the inlet temperature and outlet temperature of the economizer auxiliary circuit of the heat pump system.

[0200] The processing module 601 is further configured to determine the opening correction value of the auxiliary valve based on the target superheat of the economizer, the current actual superheat of the economizer, and the previous actual superheat of the economizer.

[0201] Optionally, the processing module 601 is further configured to determine the economizer overheat deviation value based on the economizer target overheat and the current actual economizer overheat.

[0202] The processing module 601 is also used to determine the rate of change of the economizer overheat based on the current actual overheat of the economizer and the previous actual overheat of the economizer.

[0203] The processing module 601 is further configured to determine the opening correction value of the auxiliary valve based on the superheat deviation value of the economizer and the superheat change rate of the economizer.

[0204] Optionally, the processing module 601 is further configured to determine whether to open the auxiliary valve of the heat pump system based on the ambient temperature of the heat pump system and the compressor frequency after the heat pump system has been running for a first preset time according to the first initial opening of the main valve.

[0205] The processing module 601 is further configured to, after the second preset time of opening the auxiliary valve, determine the opening correction value of the auxiliary valve according to the second time interval, based on the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit.

[0206] Figure 7 A schematic diagram of the structure of the electronic device provided in this application. Figure 7 As shown, this application provides an electronic device 700, which includes: a receiver 701, a transmitter 702, a processor 703, and a memory 704.

[0207] Receiver 701 is used to receive commands and data;

[0208] Transmitter 702 is used to send commands and data;

[0209] Memory 704 is used to store instructions executed by the computer;

[0210] The processor 703 is used to execute computer execution instructions stored in the memory 704 to implement the various steps performed by the control method of the gas-injection enthalpy-increasing heat pump system in the above embodiments. For details, please refer to the relevant descriptions in the embodiments of the control method for the gas-injection enthalpy-increasing heat pump system.

[0211] Alternatively, the memory 704 can be either standalone or integrated with the processor 703.

[0212] When the memory 704 is set up independently, the electronic device also includes a bus for connecting the memory 704 and the processor 703.

[0213] This application also provides a heat pump system, including a controller, an economizer, a compressor, an evaporator, a condenser, a four-way valve, a heating main valve, a cooling main valve, and an auxiliary valve;

[0214] The compressor, four-way valve, evaporator, heating main valve and economizer are connected in sequence, and the economizer is connected to the compressor; one end of the condenser is connected to the four-way valve, and the other end is connected to the economizer through the refrigeration main valve; the controller is electrically connected to the heating main valve, refrigeration main valve and auxiliary valve respectively, and the controller is used to execute the control method of the gas replenishment enthalpy increase heat pump system.

[0215] Optionally, the heat pump system further includes a diversion control module, which is connected to the economizer and the evaporator control respectively, to control the refrigerant flowing out of the evaporator to divert to the main circuit and the auxiliary circuit of the economizer during cooling, and / or to control the refrigerant flowing out of the economizer to divert to the auxiliary circuit of the economizer and the evaporator during heating.

[0216] In this embodiment, the controller corrects the opening degree of the auxiliary valve and the main valve according to their respective adjustment cycles, thereby improving the control accuracy of the auxiliary valve and the main valve. Furthermore, through this diversion control module, the refrigerant in the heat pump system can be effectively diverted during cooling and / or heating, ensuring the stability of the refrigerant flow entering the economizer auxiliary circuit. This enables the controller to precisely control the opening degree of the auxiliary valve in the economizer auxiliary circuit and the main valve in the economizer main circuit, thereby improving the energy efficiency ratio and stability of the heat pump system.

[0217] This application also provides a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, implement a control method for a gas-fuel-injection enthalpy-increasing heat pump system as described above, thereby enabling the system to be controlled by the aforementioned electronic device.

[0218] This application also provides a computer program product, including a computer program that, when executed by a processor, implements the above-described control method for a gas-fuel-injection enthalpy-increasing heat pump system.

[0219] It will be understood by those skilled in the art that all or some of the steps, systems, or apparatuses disclosed above, and their functional modules / units, can be implemented as software, firmware, hardware, or suitable combinations thereof. In hardware implementations, the division between functional modules / units mentioned in the above description does not necessarily correspond to the division of physical components; for example, a physical component may have multiple functions, or a function or step may be performed collaboratively by several physical components. Some or all physical components may be implemented as software executed by a processor, such as a central processing unit, digital signal processor, or microprocessor, or as hardware, or as an integrated circuit, such as an application-specific integrated circuit (ASIC). Such software may be distributed on a computer-readable medium, which may include computer storage media (or non-transitory media) and communication media (or transient media). As is known to those skilled in the art, the term computer storage media includes volatile and non-volatile, removable and non-removable media implemented in any method or technology for storing information (such as computer-readable instructions, data structures, program modules, or other data). Computer storage media include, but are not limited to, RAM, ROM, EEPROM, flash memory or other memory technologies, CD-ROM, digital versatile disc (DVD) or other optical disc storage, magnetic cartridges, magnetic tape, disk storage or other magnetic storage devices, or any other medium that can be used to store desired information and can be accessed by a computer. Furthermore, it is well known to those skilled in the art that communication media typically contain computer-readable instructions, data structures, program modules, or other data in modulated data signals such as carrier waves or other transmission mechanisms, and may include any information delivery medium.

[0220] Other embodiments of this application will readily occur to those skilled in the art upon consideration of the specification and practice of the invention disclosed herein. This application is intended to cover any variations, uses, or adaptations of this application that follow the general principles of this application and include common knowledge or customary techniques in the art not disclosed herein. The specification and examples are to be considered exemplary only, and the true scope and spirit of this application are indicated by the following claims.

[0221] It should be understood that this application is not limited to the precise structure described above and shown in the accompanying drawings, and various modifications and changes can be made without departing from its scope. The scope of this application is limited only by the appended claims.

Claims

1. A control method for a gas-injection enthalpy-increasing heat pump system, characterized in that, The method includes: Based on the ambient temperature and outlet water temperature of the heat pump system, the initial opening degree of the main valve of the heat pump system is determined, wherein the main valve is a heating main valve or a cooling main valve. Based on the ambient temperature and compressor frequency of the heat pump system, it is determined whether to open the auxiliary valve of the heat pump system. If it is determined that the auxiliary valve should be opened, the initial opening degree of the auxiliary valve is determined based on the ambient temperature and outlet water temperature of the heat pump system. The auxiliary valve is used to regulate the refrigerant flow rate into the economizer auxiliary circuit of the heat pump system. According to the first time interval, based on at least two of the suction temperature, exhaust temperature, evaporator coil temperature, liquid pipe temperature and condensation temperature of the heat pump system, the opening correction value of the main valve is determined, and the opening of the main valve is adjusted according to the opening correction value of the main valve. According to the second time interval, based on at least two of the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit, the opening correction value of the auxiliary valve is determined, and the opening of the auxiliary valve is adjusted according to the opening correction value of the auxiliary valve.

2. The method according to claim 1, characterized in that, Determining the initial opening degree of the main valve of the heat pump system based on the ambient temperature and outlet water temperature of the heat pump system includes: After the heat pump system is turned on, the first initial opening degree of the main valve of the heat pump system is determined based on the ambient temperature and outlet water temperature of the heat pump system. After the heat pump system has been running for a first time at the first initial opening of the main valve, the initial opening of the main valve of the heat pump system is determined based on the ambient temperature and outlet water temperature of the heat pump system.

3. The method according to claim 1, characterized in that, The determination of the main valve opening correction value based on at least two of the heat pump system's suction temperature, exhaust temperature, evaporator coil temperature, liquid line temperature, and condensation temperature includes: The target intake superheat is determined based on the preset initial intake superheat and the exhaust temperature of the heat pump system. The current actual suction superheat is determined based on the suction temperature and evaporator coil temperature of the heat pump system. Based on the current actual intake superheat, the target intake superheat, and the previous actual intake superheat, determine the first opening correction value of the main valve; The current actual subcooling is determined based on the condensing temperature and liquid pipe temperature of the heat pump system. Based on the current actual subcooling and the preset target subcooling, determine the second opening correction value of the main valve; The sum of the first opening correction value and the second opening correction value of the main valve is determined as the opening correction value of the main valve.

4. The method according to claim 3, characterized in that, The step of determining the first opening correction value of the main valve based on the current actual intake superheat, the target intake superheat, and the previous actual intake superheat includes: Based on the current actual inhalation superheat and the target inhalation superheat, determine the inhalation superheat deviation value; The rate of change of intake superheat is determined based on the current actual intake superheat and the previous actual intake superheat. The first opening correction value of the main valve is determined based on the intake superheat deviation value and the intake superheat change rate.

5. The method according to claim 3, characterized in that, The step of determining the second opening correction value of the main valve based on the current actual subcooling and the preset target subcooling includes: Based on the current actual subcooling and the preset target subcooling, determine the subcooling deviation value; The second opening correction value of the main valve is determined based on the range to which the subcooling deviation value belongs.

6. The method according to claim 1, characterized in that, The determination of the auxiliary valve opening correction value based on at least two of the ambient temperature of the heat pump system, the economizer auxiliary circuit inlet temperature, and the economizer auxiliary circuit outlet temperature includes: The target superheat of the economizer is determined based on the ambient temperature of the heat pump system. The actual superheat of the economizer is determined based on the inlet temperature and outlet temperature of the economizer auxiliary circuit of the heat pump system. The opening correction value of the auxiliary valve is determined based on the target superheat of the economizer, the current actual superheat of the economizer, and the previous actual superheat of the economizer.

7. The method according to claim 6, characterized in that, The step of determining the opening correction value of the auxiliary valve based on the target superheat of the economizer, the current actual superheat of the economizer, and the previous actual superheat of the economizer includes: The economizer overheat deviation value is determined based on the target overheat of the economizer and the current actual overheat of the economizer. The rate of change of economizer overheat is determined based on the current actual overheat of the economizer and the previous actual overheat of the economizer. The opening correction value of the auxiliary valve is determined based on the superheat deviation value of the economizer and the superheat change rate of the economizer.

8. The method according to any one of claims 2-7, characterized in that, The step of determining whether to open the auxiliary valve of the heat pump system based on the ambient temperature and compressor frequency of the heat pump system includes: After the heat pump system has been running for a first preset time at the first initial opening of the main valve, it is determined whether to open the auxiliary valve of the heat pump system based on the ambient temperature of the heat pump system and the compressor frequency. The step of determining the opening correction value of the auxiliary valve according to the second time interval, based on at least two of the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit, includes: After the auxiliary valve is opened for a second preset time, the opening correction value of the auxiliary valve is determined according to the second time interval, based on the ambient temperature of the heat pump system, the inlet temperature of the economizer auxiliary circuit, and the outlet temperature of the economizer auxiliary circuit.

9. A heat pump system, characterized in that, This includes the controller, economizer, compressor, evaporator, condenser, four-way valve, heating main valve, cooling main valve, and auxiliary valve; The compressor, the four-way valve, the evaporator, the heating main valve, and the economizer are connected in sequence, and the economizer is connected to the compressor; one end of the condenser is connected to the four-way valve, and the other end is connected to the economizer through the refrigeration main valve; the controller is electrically connected to the heating main valve, the refrigeration main valve, and the auxiliary valve respectively, and the controller is used to execute the method as described in any one of claims 1-8.

10. The system according to claim 9, characterized in that, Also includes: The refrigerant diversion control module is connected to the economizer and the evaporator respectively, so as to control the refrigerant flowing out of the evaporator to divert to the main circuit and the auxiliary circuit of the economizer during cooling, and / or, control the refrigerant flowing out of the economizer to divert to the auxiliary circuit and the evaporator during heating.

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