Heat pump system

Abstract

The invention discloses a heat pump system. The heat pump system comprises a liquid storage device; a subcooler; the first valve element and the second valve element can adjust the air supply amount. The processing module is configured as follows: when entering a steady state under an extremely cold working condition, according to environment and operation parameters, the processing module generates an air supply proportionality coefficient of a liquid storage device and a subcooler as a reference parameter group of a current period; a first steady-state opening degree and a second steady-state opening degree are generated according to the air supply proportionality coefficients of the liquid storage device and the subcooler; positive disturbance is applied to one of the air supply proportionality coefficients of the liquid storage device and the subcooler, and negative disturbance is applied to the other air supply proportionality coefficient to generate a differential test group; according to the performance indexes, selecting one group as a reference parameter group of the next period; updating the energy efficiency optimization step length according to a preset attenuation ratio, so that the energy efficiency optimization step length is gradually reduced in each iteration period until a set threshold value is reached, and obtaining a corresponding first target weight and a corresponding second target weight; and generating a first target weight and a second target weight according to the first target weight and the second target weight to generate a second target opening degree. According to the invention, the current working condition can be accurately compensated.

Description

Technical Field

[0001] This invention relates to the field of heat pump system technology, and more particularly to a heat pump system. Background Technology

[0002] Traditional air-source heat pump systems experience a significant drop in heating efficiency when outdoor temperatures are extremely low (e.g., below -25°C). The dual-gas-injection enthalpy-enhancing system, by simultaneously utilizing two gas-injection circuits—one in the liquid receiver and the other in the plate heat exchanger—and through precise coordinated control, enables the compressor to maintain high efficiency even in frigid conditions.

[0003] In existing dual-gas-injection enthalpy-increasing systems, a fixed-ratio gas injection is typically used: the operating conditions of the heat pump system are divided into several stages, and in each stage, the opening of the two electronic expansion valves is adjusted according to a preset fixed ratio. However, fixed-ratio gas injection cannot adapt to dynamic load changes. It is prone to over-injection at low loads, increasing the risk of compressor liquid slugging, and under-injection at high loads, which increases the limiting capacity and makes it impossible to maintain the optimal energy efficiency of the heating cycle.

[0004] The information disclosed in this background section is only intended to enhance the understanding of the background technology of this application, and therefore may include prior art that is not known to those skilled in the art. Summary of the Invention

[0005] This application designs and provides a heat pump system, including a liquid receiver and a subcooler. The liquid receiver is fluidly connected to a first valve element, and the subcooler is fluidly connected to a second valve element. The first valve element and the second valve element can respectively adjust the amount of gas supplied to the compressor.

[0006] The heat pump system also includes a processing module configured to: upon entering a steady state under a preset extremely cold operating condition, generate a liquid receiver gas replenishment ratio coefficient and a subcooler gas replenishment ratio coefficient based on environmental and operating parameters, respectively, as the reference parameter set for the current cycle; generate a first steady-state opening of a first valve element based on the liquid receiver gas replenishment ratio coefficient, and a second steady-state opening of a second valve element based on the subcooler gas replenishment ratio coefficient; apply a positive perturbation to one of the liquid receiver gas replenishment ratio coefficient and a negative perturbation to the other to generate a differential test set; select a set from the differential test set as the reference parameter set for the next cycle based on the performance indicators of the differential test set; update the energy efficiency optimization step size according to a preset attenuation ratio, gradually decreasing it in each iteration cycle until a set threshold is reached, and obtain the corresponding first target weight and second target weight; generate a first target opening of the first valve element based on the first target weight, and a second target opening of the second valve element based on the second target weight.

[0007] The above technical solution has the following advantages or beneficial effects: The heat pump system provided in this application, under preset extremely cold conditions and when it enters a steady state, continuously narrows the search range by making small bidirectional perturbations near the current optimal static weight, and finally converges to the local optimal first target weight and second target weight. Thus, under extremely cold conditions, the heat pump system forms a dynamic gas supply coordination control based on the current environmental parameters and unit operating parameters. Without changing the hardware design, it solves the problem that the heating capacity and operating efficiency of the heat pump system are difficult to balance under low temperature, especially extremely low temperature conditions. In particular, it can avoid pressure transients and exhaust temperature runaway caused by the switching of the gas supply source when the heat pump system load fluctuates at the critical point. Under variable load conditions, it can still achieve a smooth transition of the gas supply volume and accurately compensate for the current operating conditions.

[0008] In some embodiments of this application, the environmental parameters include the current ambient temperature, and the operating parameters include the current system load; the processing module is configured to: calculate the liquid receiver gas replenishment ratio coefficient using a first mapping function based on the current ambient temperature and the current system load; and calculate the subcooler gas replenishment ratio coefficient using a second mapping function based on the current ambient temperature and the current system load; wherein the output of the first mapping function decreases exponentially with increasing current ambient temperature, and the output of the second mapping function increases exponentially with increasing current ambient temperature.

[0009] The above technical solution has the following advantages or beneficial effects: In this application, the current ambient temperature and the current system load are used as inputs to construct a first mapping function and a second mapping function in groups, so as to realize the coordinated allocation of the liquid receiver gas supply ratio coefficient and the subcooler gas supply ratio coefficient. The liquid receiver gas supply ratio coefficient is generated through negative feedback. Furthermore, the first steady-state opening degree generated according to the liquid receiver gas supply ratio coefficient can suppress excessive gas supply at high ambient temperatures and avoid liquid slugging. The subcooler gas supply ratio coefficient increases with the increase of the current ambient temperature and the current system load, which can maintain the stability of the heat pump system under high temperature and high load conditions.

[0010] In some embodiments of this application, the processing module is configured to: call a first opening upper limit threshold of the first valve element, and proportionally generate a first steady-state opening of the first valve element based on the first opening upper limit threshold and the liquid reservoir gas replenishment ratio coefficient; call a second opening upper limit threshold of the second valve element, and proportionally generate a second steady-state opening of the second valve element based on the second opening upper limit threshold and the subcooler gas replenishment ratio coefficient.

[0011] In some embodiments of this application, the processing module is further configured to: call a first opening upper limit threshold of the first valve element, and proportionally generate a first target opening of the first valve element based on the first opening upper limit threshold and a first target weight; call a second opening upper limit threshold of the second valve element, and proportionally generate a second target opening of the second valve element based on the second opening upper limit threshold and a second target weight.

[0012] In some embodiments of this application, the upper limit threshold of the first opening is limited to 90%.

[0013] In some embodiments of this application, the upper limit threshold of the second opening is limited to 100%.

[0014] The above technical solution has the following advantages or beneficial effects: In this application, the upper limit threshold of the first opening is limited to 90%, ensuring that the first valve element always operates within the adjustable range. In a heat pump system, the receiver plays a role in gas-liquid separation and buffering, and its outlet flow directly affects the state of the refrigerant entering the compressor. When the opening of the first valve element is close to fully open, the flow regulation sensitivity decreases, and the control characteristics tend to be nonlinear. This may cause changes in the refrigerant state inside the receiver, leading to a decrease in gas-liquid separation effect, an increase in the amount of liquid refrigerant carried, and an increase in the risk of liquid refrigerant entering the compressor. Therefore, limiting the upper limit threshold of the first opening to 90% avoids the first valve element from being close to fully open under any operating condition, thus improving operational stability while ensuring the adjustment capability of the heat pump system. Limiting the upper limit threshold of the second opening to 100% expands the operating range of the second valve element under extreme operating conditions without introducing additional safety risks or control instability problems. This application adopts a differentiated design for the upper limit thresholds of the first and second opening of the first and second valve elements, thereby imposing stability constraints on the one hand and maximizing performance on the other.

[0015] In some embodiments of this application, under preset extremely cold conditions but in a preset cold start phase, the processing module is configured to: configure the compressor's operating frequency to be in a preset high-frequency output range; preset a first reference opening degree of the first valve element based on a linear negative correlation function of the current ambient temperature; calculate the pressure difference between the liquid receiver pressure and the condensing pressure, set a dynamic disturbance factor, and dynamically correct the first reference opening degree to generate a first start-up opening degree, wherein the first start-up opening degree is not lower than a first safety threshold.

[0016] The above technical solution has the following advantages or beneficial effects: Through a frequency locking mechanism, the compressor is forced into a high-power output range. As the compressor frequency increases, the compressor's gas supply circuit begins to generate a sufficient pressure difference, shortening the rise time of the outlet water temperature. For the first valve element, a first reference opening degree is preset based on a linear negative correlation function of the current ambient temperature; the lower the current ambient temperature, the higher the first reference opening degree, achieving pre-compensation. The pressure difference between the receiver pressure and the condensate pressure is calculated, and a dynamic disturbance factor is set to provide safety protection and prevent failure due to insufficient pressure difference; a boundary is set through a first safety threshold to ensure that the receiver can provide basic cyclic compensation under any calculation deviation.

[0017] In some embodiments of this application, under a preset extremely cold operating condition, but in a preset cold start phase, the processing module is configured to: determine a second reference opening of the second valve element by using the first start opening as a reference and a preset coupling coefficient; dynamically correct the second reference opening by using exhaust superheat as a real-time feedback variable; calculate the reference opening increment based on the supercooling; and superimpose the second reference opening and the reference opening increment to generate a second start opening of the second valve element, wherein the second start opening is not higher than a second safety threshold.

[0018] The above technical solution has the following advantages or beneficial effects: by establishing a coupling relationship between the first valve element and the second valve element, and introducing safety constraints based on exhaust superheat and performance optimization increments based on subcooling, the amount of supplementary gas can be dynamically balanced and adjusted between safety and energy efficiency.

[0019] In some embodiments of this application, the processing module is configured to: obtain the current ambient temperature; determine whether the current ambient temperature is lower than a preset extreme cold operating temperature threshold; if the current ambient temperature is lower than the preset extreme cold operating temperature threshold, then presume that the heat pump system is in a preset extreme cold operating condition.

[0020] The above technical solution has the following advantages or beneficial effects: This application estimates the operating environment conditions of the heat pump system by ambient temperature, thereby automatically switching between conventional mode, single gas supply mode and dual gas supply mode.

[0021] In some embodiments of this application, when the heat pump system is presumed to be under a preset extremely cold operating condition, the processing module is configured to: obtain the outlet water temperature of the water module heat exchanger supply branch; determine whether the outlet water temperature is lower than a preset energy efficiency water temperature threshold; when the outlet water temperature is lower than the preset energy efficiency water temperature threshold, presuming that the heat pump system is under a preset extremely cold operating condition but has not entered a steady state; when the outlet water temperature is not lower than the preset energy efficiency water temperature threshold, presuming that the heat pump system is under a preset extremely cold operating condition but has entered a steady state.

[0022] The above technical solution has the following advantages or beneficial effects: This application estimates whether the heat pump system has entered a steady state by measuring the outlet water temperature of the water supply branch of the water module heat exchanger. In the low-temperature start-up stage before entering a steady state, the goal is to maximize output. After entering a steady state, the goal is to optimize energy efficiency, and the globally optimal energy efficiency parameters under the current disclosure are determined through self-optimization.

[0023] In some embodiments of this application, the processing module is configured to: obtain the current ambient temperature; determine whether the current ambient temperature is not lower than a preset extreme cold working condition temperature threshold, but not higher than a normal working condition temperature threshold; if the current ambient temperature is not lower than the preset extreme cold working condition temperature threshold, but not higher than a normal working condition temperature threshold, then open one of the first valve element and the second valve element according to the current load state.

[0024] The above technical solution has the following advantages or beneficial effects: When the current ambient temperature is not lower than the preset extreme cold operating temperature threshold but not higher than the normal operating temperature threshold, this application executes a single gas replenishment mode, determines the gas replenishment priority according to the current load of the heat pump system, and selects one of the liquid receiver and subcooler to perform gas replenishment.

[0025] In some embodiments of this application, the processing module is configured to: acquire the current ambient temperature; determine whether the current ambient temperature is higher than the normal operating temperature threshold; and if the current ambient temperature is higher than the normal operating temperature threshold, close the first valve element and the second valve element.

[0026] The above technical solution has the following advantages or beneficial effects: When the current ambient temperature is higher than the normal operating temperature threshold, this application executes the conventional mode, completely shuts off the gas supply function, and maintains the circulation of the basic heat pump system.

[0027] Other features and advantages of the present invention will become clearer after reading the detailed embodiments of the invention in conjunction with the accompanying drawings. Attached Figure Description

[0028] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0029] Figure 1 This is a schematic diagram of the refrigeration cycle of a heat pump system provided in some embodiments of the present invention;

[0030] Figure 2 This is a schematic diagram of the refrigeration cycle of a heat pump system provided in some embodiments of the present invention;

[0031] Figure 3 This is a schematic block diagram of the processing module in the heat pump system provided by the present invention.

[0032] Figure 4 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0033] Figure 5 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0034] Figure 6 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0035] Figure 7 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0036] Figure 8 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0037] Figure 9 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0038] Figure 10 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0039] Figure 11 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0040] Figure 12 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0041] Figure 13 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0042] Figure 14 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0043] Figure 15 A flowchart of a processing module in a heat pump system provided in some embodiments of the present invention;

[0044] In the picture:

[0045] 1. Compressor; 2. Gas-liquid separator; 3. Oil separator; 4. Switching valve; 5. Outdoor heat exchanger; 6. Outdoor throttling element; 7. Liquid receiver; 8. First valve element; 9. Subcooler; 10. Second valve element; 11. Liquid line shut-off valve; 12. Water module heat exchanger; 13. Gas line shut-off valve; 14. Pressure relief solenoid valve; 15. First capillary tube; 16. Second capillary tube;

[0046] 20. Processing module; 201. Processor; 202. Volatile memory; 203. Non-volatile memory; 204. Display device; 205. Operating device; 206. Communication interface; 207. Drive device; 208. Bus; 209. Storage medium. Detailed Implementation

[0047] The technical solutions of the embodiments 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, and 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.

[0048] This application designs and provides a heat pump system.

[0049] From a thermodynamic perspective, a heat pump system's circulation system includes an evaporator, compressor, condenser, and throttling device connected in sequence. The circulation system involves a series of processes, including compression, condensation, expansion, and evaporation, which can heat indoor spaces and / or heat domestic hot water when heating is needed.

[0050] Specifically, the low-temperature, low-pressure refrigerant enters the compressor, which compresses it into a high-temperature, high-pressure refrigerant gas and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and the heat is released to the water to be heated through the condensation process. The throttling device causes the high-temperature, high-pressure liquid refrigerant formed in the condenser to expand into a low-pressure liquid refrigerant. The evaporator evaporates the refrigerant that expanded in the throttling device and returns the low-temperature, low-pressure refrigerant gas to the compressor.

[0051] Reference Figure 1 This application describes the refrigerant cycle of a heat pump system provided by some embodiments thereof.

[0052] The heat pump system includes compressor 1. Compressor 1 is the core component, used to compress the refrigerant, changing the refrigerant from a low-pressure state to a high-pressure state, so that the refrigerant can effectively transfer heat in the refrigeration cycle.

[0053] The outdoor unit of a heat pump system refers to the part of the refrigerant cycle that includes compressor 1.

[0054] The outdoor unit also includes a gas-liquid separator 2. The gas-liquid separator 2 is located on the suction side of the compressor 1. The gas-liquid separator 2 separates the liquid droplets carried by the gaseous refrigerant from the gaseous refrigerant by utilizing the difference in physical properties between the gaseous and liquid phases of the refrigerant, preventing liquid slugging and improving lubricating oil backflow.

[0055] The outdoor unit also includes an oil separator 3. The oil separator 3 separates lubricating oil droplets carried by the refrigerant from the exhaust of the compressor 1, collects them, and directs them (e.g., through the second capillary tube 16) back to the compressor 1, preventing the lubricating oil from migrating with the refrigerant to other parts of the refrigerant cycle, thus ensuring sufficient lubricating oil in the compressor 1. The oil separator 3 can achieve separation using principles such as gravity settling, inertial separation, and / or centrifugal separation.

[0056] The outdoor unit also includes: switching valve 4. Switching valve 4 is used to switch the flow direction of refrigerant and is usually a four-way valve.

[0057] The outdoor unit also includes an outdoor heat exchanger 5. The outdoor heat exchanger 5 is used for heat exchange between the refrigerant and the air.

[0058] The outdoor unit also includes an outdoor throttling element 6, which is fluidly connected to the outdoor heat exchanger 5.

[0059] The outdoor unit also includes a liquid receiver 7. High-pressure liquid refrigerant from the condenser, after being throttled and depressurized, enters the liquid receiver 7 as a two-phase gas-liquid mixture. Due to the pressure drop, some of the liquid flashes into medium-pressure vapor. The medium-pressure vapor is collected at the top of the liquid receiver 7 and sent to the gas supply port of the compressor 1 through the gas supply branch. The liquid refrigerant at the bottom is then supplied to the evaporator. A first valve element 8 is installed on the gas supply branch. The liquid receiver 7 is fluidly connected to the first valve element 8.

[0060] The outdoor unit also includes a subcooler 9. The subcooler 9 comprises a plate heat exchanger, which is fluidly connected to a second valve element 10. The plate heat exchanger includes a main circuit and an auxiliary branch. High-pressure liquid refrigerant can flow in the main circuit. A portion of the high-pressure liquid refrigerant is separated, throttled and cooled by the second valve element 10, and flows through the auxiliary branch on the other side of the plate heat exchanger. The refrigerant in the auxiliary branch absorbs heat from the refrigerant in the main circuit, undergoes a phase change to become superheated vapor, and then enters the compressor 1's gas injection port. Simultaneously, the liquid in the main circuit is further cooled, allowing it to absorb more heat in the evaporator.

[0061] The first valve element 8 and the second valve element 10 can respectively adjust the amount of gas supplied to the compressor 1.

[0062] Both the first valve element 8 and the second valve element 10 can be electronic expansion valves, or valves or combinations of valves that can achieve the same function.

[0063] The outdoor unit and the indoor unit are connected by a liquid pipe, and a liquid pipe shut-off valve 11 is installed on the liquid pipe.

[0064] The indoor unit is equipped with a water module heat exchanger 12. The water module heat exchanger 12 is used for heat exchange between refrigerant and water, transferring heat from the refrigerant to the water to raise the water temperature. The water module heat exchanger 12 includes a heat exchange branch and a water supply branch. The refrigerant flows in the heat exchange branch, and the water flows in the water supply branch.

[0065] Water heated to a higher temperature can be used for indoor heating, such as by supplying it to underfloor heating, radiant heating, and other heat radiant terminals.

[0066] The heated water can also be used in domestic hot water supply systems to provide hot water, for example, by being delivered to and stored in hot water storage tanks. The water in the storage tanks is then further distributed to water-using terminals via a circulating pipe network. These terminals include bathroom terminals (including but not limited to shower heads, bathtub faucets, and washbasin faucets, with water temperatures typically required to be between 38 and 42°C), kitchen terminals (including but not limited to kitchen sink faucets and dishwashers, with water temperatures typically required to be between 45 and 55°C), laundry terminals (including but not limited to washing machines, with water temperatures typically required to be between 30 and 60°C), cleaning terminals (including but not limited to mop sink faucets and cleaning sink faucets), and other terminals (including but not limited to towel racks and smart toilets).

[0067] Another connection between the indoor and outdoor units is via a gas pipe, which is equipped with a gas pipe shut-off valve 13.

[0068] A pressure relief branch can also be provided between the exhaust side of the compressor 1 and the gas-liquid separator 2, and a pressure relief solenoid valve 14 and a first capillary tube 15 are provided on the pressure relief branch.

[0069] In some embodiments of this application, the processing module is configured to execute a heating mode: In the heating mode, the high-temperature and high-pressure refrigerant gas discharged from the compressor 1 passes through the oil separator 3, the switching valve 4, and enters the water module heat exchanger 12, where it condenses. The water module heat exchanger 12 condenses the compressed refrigerant into a liquid phase. The refrigerant flowing out of the water module heat exchanger 12 first passes through the subcooler 9, then through the liquid receiver 7, and further through the outdoor throttling element 6, which is in the throttling working range, and the outdoor heat exchanger 5, which acts as an evaporator. After flowing out of the outdoor heat exchanger 5, it returns to the compressor 1 for the next cycle.

[0070] In some embodiments of this application, such as Figure 2 As shown, the heat pump system also includes a processing module 20.

[0071] Figure 3 This is a block diagram of the hardware configuration of the processing module 20.

[0072] like Figure 3 As shown, the processing module 20 includes a processor 201. The processor 201 can be a dedicated processor 201, a central execution unit (CPU), etc. The processing module 20 also includes a storage component, which can be volatile memory 202 and / or non-volatile memory 203. The processor 201 can access instructions or application programs stored in the storage component to implement related functions.

[0073] The processing module 20 also includes a display device 204, which is used to display various information.

[0074] The processing module 20 also includes an operating device 205, which is used to perform various operations.

[0075] The processing module 20 also includes a communication interface 206.

[0076] Processing module 20 also includes a drive device 207, which is used to control hardware interrupts that interact with storage medium 209.

[0077] The processing module 20 also includes a bus 208.

[0078] The processor 201, volatile memory 202, non-volatile memory 203, display device 204, operation device 205, communication interface 206 and drive device 207 are interconnected via bus 208.

[0079] In some embodiments of this application, the storage medium 209 includes a compact disc read-only memory (CD-ROM), floppy disk, optical-magnetic disc, or the like, which records information optically, electrically, or magnetically. The storage medium 209 may also be a semiconductor memory that records information electrically, such as a read-only memory (ROM) or flash memory.

[0080] In some embodiments of this application, the processing module 20 may be an on-board system built on a microcontroller unit in the outdoor unit.

[0081] In some other embodiments of this application, the processing module 20 may be an on-board system built on a microcontroller unit in the indoor unit.

[0082] In some other embodiments of this application, some functions of the processing module 20 can be implemented by an on-board system built on a microcontroller unit in the outdoor unit, and other functions can be implemented by an on-board system built on a microcontroller unit in the indoor unit.

[0083] In some other embodiments of this application, some functions of the processing module 20 may be implemented by the edge processing module 20 (e.g., a central controller or gateway) and / or a cloud server, while other functions may be implemented by an on-board system built on a microcontroller unit in the outdoor unit and / or indoor unit.

[0084] In some embodiments of this application, the processing module 20 is configured to perform, as Figure 4 The steps are shown.

[0085] Step S101: Under the preset extreme cold conditions and upon entering a steady state, generate the liquid receiver gas replenishment ratio coefficient and the subcooler gas replenishment ratio coefficient according to the environmental parameters and operating parameters, respectively, as the reference parameter set for the current cycle. Generate the first steady-state opening of the first valve element according to the liquid receiver gas replenishment ratio coefficient, and generate the second steady-state opening of the second valve element according to the subcooler gas replenishment ratio coefficient.

[0086] Step S102: Apply a positive perturbation to one of the liquid reservoir gas supply ratio coefficient and the subcooler gas supply ratio coefficient, and apply a negative perturbation to the other to generate a differential test set.

[0087] Step S103: Based on the performance indicators of the differential test group, select one group from the differential test group as the benchmark parameter group for the next cycle.

[0088] Step S104: Update the energy efficiency optimization step size according to the preset attenuation ratio, so that it gradually decreases in each iteration cycle until the set threshold is reached, and obtain the corresponding first target weight and second target weight.

[0089] Step S105: Generate the first target opening degree of the first valve element according to the first target weight, and generate the second target opening degree of the second valve element according to the second target weight.

[0090] The heat pump system provided in this application, under preset extremely cold operating conditions and upon entering a steady state, continuously narrows the search range by making small bidirectional perturbations near the current optimal static weight, eventually converging to the local optimum of the first and second objective weights. This enables the heat pump system to achieve dynamic gas replenishment coordination control under extremely cold operating conditions based on current environmental parameters and unit operating parameters. Without changing the hardware design, it solves the problem of balancing heating capacity and operating efficiency of heat pump systems under low temperature, especially extremely low temperature conditions. In particular, it can avoid pressure transients and exhaust temperature runaway caused by gas source switching when the heat pump system load fluctuates at the critical point. Under variable load conditions, it can still achieve a smooth transition of gas replenishment volume and accurately compensate for the current operating conditions.

[0091] In some embodiments of this application: the gas replenishment ratio coefficient of the reservoir can be expressed as: The subcooler injection ratio can be expressed as: .

[0092] like Figure 5 As shown, processing module 20 is configured to perform the following steps:

[0093] Step S201: Use the gas replenishment ratio coefficient of the liquid reservoir. and subcooler injection ratio coefficient The reference parameter set for the current period Save the reference parameter set for the current period. And the coefficient of performance (COP) of the current cycle heat pump system.

[0094] The coefficient of performance (COP) of a heat pump system can be obtained using existing online monitoring and evaluation methods, which will not be elaborated upon here. Besides the energy efficiency ratio (EER), other performance indicators of the heat pump system can also be selected.

[0095] Step S202: Apply a positive perturbation to the gas supply ratio of the liquid receiver and a negative perturbation to the gas supply ratio of the subcooler to generate the first test group. ,in To optimize the step size for energy efficiency.

[0096] Step S203: Optimize based on energy efficiency step size A negative perturbation is applied to the gas supply ratio of the liquid receiver, and a positive perturbation is applied to the gas supply ratio of the subcooler to generate the second test group. .

[0097] The range of the gas supply ratio coefficients for the liquid receiver and the subcooler after the perturbation is applied is limited so that they are within the preset neighborhood intervals corresponding to the gas supply ratio coefficients for the liquid receiver and the subcooler.

[0098] Step S204: Record the first test group and the second test group as the differential test group, which is represented as follows: .

[0099] Step S205: Based on the weights after applying the perturbation in the first test group, generate the corresponding opening degree of the first valve element and the second valve element, and drive the heat pump system to run until the end of the test cycle, or configure it to run in the simulation environment until the end of the test cycle.

[0100] In some embodiments of this application, the test period is set to, for example, 5 minutes.

[0101] Step S206: Perform multiple samplings at several sampling points within the test period and calculate the corresponding performance coefficients.

[0102] Step S207: At the end of the test cycle, calculate the average performance coefficient of the first test group during the test cycle.

[0103] Step S208: Based on the weights after applying the perturbation in the second test group, generate the corresponding opening degrees of the first valve element and the second valve element, and drive the heat pump system to run until the end of the test cycle, or configure it to run in the simulation environment until the end of the test cycle.

[0104] Step S209: Perform multiple samplings at several sampling points within the test period and calculate the corresponding performance coefficients.

[0105] Step S210: At the end of the test cycle, calculate the average performance coefficient of the second test group during the test cycle.

[0106] Step S211: Compare the average performance coefficient of the first test group and the average performance coefficient of the second test group, and select the one with the higher average performance coefficient as the benchmark parameter group for the next cycle.

[0107] Step S212: Optimize the step size for energy efficiency Perform decay update: ;in, This is the attenuation coefficient.

[0108] For example, energy efficiency optimization step size It can be set to 95%. That is, the energy efficiency optimization step size is updated with 95% as the decay ratio, so that the energy efficiency optimization step size is reduced to 95% of the previous cycle.

[0109] Repeat the above steps until the energy efficiency optimization step size is reached. Once a preset convergence threshold (e.g., 0.01) is reached, the corresponding first target weight and second target weight are obtained. The first target opening of the first valve element is generated based on the first target weight, and the second target opening of the second valve element is generated based on the second target weight.

[0110] In this embodiment, the processing module 20 employs a decreasing energy efficiency optimization step size to perform iterative optimization. Within the neighborhood of the liquid receiver gas replenishment ratio coefficient and the subcooler gas replenishment ratio coefficient, it symmetrically establishes differential test groups and gradually shrinks the search space based on performance coefficient feedback until the disturbance compensation reaches a set threshold to lock in the optimal parameters. The symmetrical design of the energy efficiency optimization step size achieves directional cancellation of values, realizes control closed loop through performance coefficients, and adopts an exponential convergence method to reduce the search space, ultimately converging and locking in the optimal value.

[0111] In some embodiments of this application, environmental parameters include the current ambient temperature, and operating parameters include the current system load. The current system load is obtained using algorithms disclosed in the prior art, which will not be elaborated here.

[0112] In some embodiments of this application, the processing module 20 is configured to perform, as Figure 6 The steps shown are to calculate the gas supply ratio coefficient for the liquid receiver and the gas supply ratio coefficient for the subcooler.

[0113] Step S301: Calculate the liquid reservoir gas replenishment ratio coefficient based on the current ambient temperature and current system load using the first mapping function.

[0114] Step S302: Calculate the subcooler gas replenishment ratio coefficient using the second mapping function based on the current ambient temperature and current system load.

[0115] The output of the first mapping function decreases exponentially as the current ambient temperature increases, while the output of the second mapping function increases exponentially as the current ambient temperature increases.

[0116] In some embodiments of this application, the first mapping function and the second mapping function are empirical models, based on the current ambient temperature. and current system load .

[0117] In some embodiments of this application, the first mapping function is represented as: ;in, , , as well as For example, a constant. , , , ;

[0118] That is, the first mapping function can be expressed as: ;

[0119] In the first mapping function, the exponential decay term constrains the rate of change with the current ambient temperature. The rise, It will decrease exponentially, thus allowing the reservoir to primarily handle performance improvements in cryogenic environments, while the load correction term ( This indicates the gas replenishment ratio of the reservoir. With current system load There is a negative correlation; when the load is low, the branch containing the first valve element dominates in the air replenishment; when the load increases, the proportional coefficient of the liquid reservoir air replenishment increases. It then decreases.

[0120] In some embodiments of this application, the second mapping function is represented as: ;in, , , as well as For example, a constant. , , , That is, the second mapping function can be expressed as: .

[0121] In the second mapping function, the trend term Constrained by the current ambient temperature The rise, This will increase rapidly, allowing the subcooler to primarily handle performance improvements in medium- and high-temperature environments, while the load correction term ( This indicates the subcooler injection ratio coefficient. With current system load There is a positive correlation; when the load is high, the branch containing the second valve element dominates the gas supply, and as the load increases, the subcooler gas supply ratio coefficient increases. As a result, it increases.

[0122] In the first mapping function and the second mapping function, and Setting it to 25 corresponds to the extreme operating condition of -25°C.

[0123] In other embodiments of this application, experimental data and / or simulation data can be used to establish a system based on ambient temperature. and system load A two-dimensional data table that records the corresponding ambient temperature. and system load corresponding and .

[0124] In some embodiments of this application, the gas replenishment ratio of the liquid reservoir can be adjusted first. and the gas replenishment ratio coefficient of the liquid reservoir After normalization, we have: ; Using the normalized liquid reservoir gas replenishment ratio coefficient and the gas replenishment ratio coefficient of the liquid reservoir Execute the subsequent algorithm.

[0125] In this embodiment, using the current ambient temperature and current system load as inputs, a first mapping function and a second mapping function are constructed in groups to achieve coordinated allocation of the liquid receiver gas supply ratio coefficient and the subcooler gas supply ratio coefficient. The liquid receiver gas supply ratio coefficient is generated through negative feedback. Furthermore, generating a first steady-state opening based on the liquid receiver gas supply ratio coefficient can suppress excessive gas supply at high ambient temperatures and avoid liquid slugging. The subcooler gas supply ratio coefficient increases with the increase of the current ambient temperature and current system load, which can maintain the stability of the heat pump system under high temperature and high load conditions.

[0126] In some embodiments of this application, the processing module 20 is configured to perform, as Figure 7 The following steps are shown:

[0127] Step S401: Call the first opening upper limit threshold of the first valve element, and proportionally generate the first steady-state opening of the first valve element based on the first opening upper limit threshold and the liquid reservoir gas replenishment ratio coefficient.

[0128] Step S402: Call the second opening upper limit threshold of the second valve element, and proportionally generate the second steady-state opening of the second valve element based on the second opening upper limit threshold and the subcooler gas supply ratio coefficient.

[0129] In some embodiments of this application, the upper limit threshold of the first opening is 90%.

[0130] First steady-state opening Represented as: .

[0131] In some embodiments of this application, the upper limit threshold of the second opening is 100%.

[0132] Second steady-state opening Represented as: .

[0133] In some embodiments of this application, the processing module 20 is configured to perform, as Figure 8 The following steps are shown:

[0134] Step S501: Based on the first opening upper limit threshold and the first target weight, proportionally generate the first target opening of the first valve element.

[0135] Step S502: Based on the second opening upper limit threshold and the second target weight, proportionally generate the second target opening of the second valve element.

[0136] In some embodiments of this application, the first upper limit threshold is 90%, and the second upper limit threshold is 100%.

[0137] First target opening degree Represented as: The weight of the first objective is... .

[0138] Second target opening degree Represented as: The weight of the second objective is... .

[0139] In this application, the upper limit threshold of the first opening is limited to 90% to ensure that the first valve element always operates within the adjustable range. In a heat pump system, the receiver acts as a gas-liquid separator and buffer, and its outlet flow directly affects the state of the refrigerant entering the compressor. When the first valve element is close to fully open, the flow regulation sensitivity decreases, and the control characteristics tend to be non-linear. This may cause changes in the refrigerant state inside the receiver, leading to a decrease in gas-liquid separation efficiency, an increase in the amount of liquid refrigerant carried, and an increased risk of liquid refrigerant entering the compressor. Therefore, limiting the upper limit threshold of the first opening to 90% avoids the first valve element from being close to fully open under any operating condition, thus improving operational stability while ensuring the adjustability of the heat pump system. Limiting the upper limit threshold of the second opening to 100% expands the operating range of the second valve element under extreme conditions without introducing additional safety risks or control instability problems. This application employs a differentiated design for the upper limit thresholds of the first and second openings of the first and second valve elements, thereby imposing stability constraints while maximizing performance.

[0140] In extremely cold conditions, heat pump systems will encounter a cold start phase, that is, the outdoor ambient temperature is very low and the temperature difference between the set indoor temperature and the outdoor ambient temperature is huge. Even if the heat pump system is already at full load, the outlet water temperature rises slowly due to the thermal inertia of the water circuit system, showing a significant lag effect. In order for the heat pump system to automatically adjust and smoothly transition from the unsteady state with a low outlet water temperature to the steady state, the system needs to be improved.

[0141] In some embodiments of this application, under preset extremely cold conditions, but during a preset cold start phase, the processing module 20 is configured to perform actions such as... Figure 9 The following steps are shown:

[0142] Step S601: Configure the compressor's operating frequency to be within the preset high-frequency output range.

[0143] For example, the compressor frequency is configured to have a lower limit of 100Hz.

[0144] Through the frequency locking mechanism, the compressor is forced into the high power output range. As the compressor frequency increases, the compressor's gas supply circuit begins to generate a sufficient pressure difference, shortening the time for the outlet water temperature to rise.

[0145] Step S602: Based on the current ambient temperature The linear negative correlation function presets the first reference opening degree of the first valve element.

[0146] For example, based on the current ambient temperature The linear negative correlation function is expressed as: ;

[0147] in, As the first reference opening, , and For example, a constant. , ,

[0148] Step S603: Calculate the pressure difference between the reservoir pressure and the condensation pressure, set the dynamic disturbance factor, and dynamically correct the first reference opening to generate the first start-up opening.

[0149] The initial opening degree shall not be lower than the first safety threshold.

[0150] For the first valve element, a first reference opening degree is preset based on the linear negative correlation function of the current ambient temperature; the lower the current ambient temperature, the higher the first reference opening degree, thus achieving pre-compensation. The pressure difference between the reservoir pressure and the condensation pressure is calculated, and a dynamic disturbance factor is set to provide safety protection and prevent failure when the pressure difference is insufficient; a boundary is set through a first safety threshold to ensure that the reservoir can provide basic cyclic compensation under any calculation deviation.

[0151] Specifically, after generating the first reference opening, the processing module 20 is configured to perform the following: Figure 10 The following steps are shown:

[0152] Step S701: Using the first reference opening degree as a reference, determine the second reference opening degree of the second valve element through a preset coupling coefficient. .

[0153] For example, the second reference opening is represented as: ;

[0154] in, The coupling coefficient ensures that the second reference opening degree is calculated with reference to the first reference opening degree. The two gas supply lines are proportionally linked in total volume, resulting in smooth pressure switching within the heat pump system. For example, set it to 0.6.

[0155] Step S702: Use exhaust superheat as a real-time feedback variable to dynamically correct the second reference opening.

[0156] For example, dynamically correcting the second reference opening. It can be expressed by the following formula: ; ;in, For exhaust superheat, and For example, a preset constant. It can be set to 90. It can be set to 70. 90°C is generally considered a safe threshold for exhaust temperature.

[0157] Step S703: Calculate the baseline opening increment based on the subcooling.

[0158] For example, the baseline opening increment can be expressed as: ;in, The subcooling degree of the plate heat exchanger in the subcooler. and For example, a constant. Set to 0.4. Set to 8.

[0159] When the subcooling is too high, the reference opening increment is positive, automatically increasing the opening of the second valve element. However, if the subcooling is insufficient, because... The correction will cause the reference opening increment to turn negative, thereby reducing the opening of the second valve element. This means that the opening of the second valve element can only be increased when the subcooling is moderate, so as to increase the gas supply and reduce the risk of liquid slugging.

[0160] Step S704: Superimpose the second reference opening degree and the reference opening degree increment to generate the second starting opening degree of the second valve element, wherein the second starting opening degree does not exceed the second safety threshold. .

[0161] For example, the second safety threshold could be 70%.

[0162] That is to say: This prevents overload of the gas supply in extreme cases, which could lead to drastic fluctuations in system pressure.

[0163] In this application, by establishing a coupling relationship between the first valve element and the second valve element, and introducing safety constraints based on exhaust superheat and performance optimization increments based on subcooling, the amount of supplementary gas is dynamically balanced and adjusted between safety and energy efficiency.

[0164] More specifically, under preset extremely cold operating conditions, but during the preset cold start phase, processing module 20 is configured to execute as follows: Figure 11 The following steps are shown:

[0165] Step S801: Configure the compressor's operating frequency to be within the preset high-frequency output range, with the compressor's operating frequency not lower than 100Hz.

[0166] Step S802: Sample the current ambient temperature And based on the current ambient temperature Construct a linear negative correlation function to determine the first reference opening degree of the first valve element. ;in, .

[0167] Step S803: Sampling reservoir pressure .

[0168] Step S804: Calculate the reservoir pressure and condensation pressure Pressure difference between ;

[0169] in, .

[0170] Step S805: Determine the pressure of the liquid reservoir. and condensation pressure Pressure difference between Does the intervention criteria meet? The intervention criteria are:

[0171] ,in, This is the preset scaling factor.

[0172] For example: the intervention condition is the reservoir pressure. and condensation pressure Is the pressure difference between them lower than .

[0173] Step S806: If the reservoir pressure and condensation pressure If the pressure difference between them meets the intervention conditions, then a dynamic perturbation factor is constructed based on the pressure difference. and the first reference opening degree Make corrections to obtain the first starting opening degree.

[0174] in, , The disturbance coefficient can be preset and stored;

[0175] First start-up opening satisfy: .

[0176] The dynamic disturbance factor gradually decreases as the pressure difference decreases, thus affecting the initial opening degree. The adjustment process exhibits a gradual convergence characteristic.

[0177] In a specific example The value can be set to approximately equal to .

[0178] Step S807: Determine whether the first start-up opening degree is lower than the first safety threshold. .

[0179] Step S808: If the first start-up opening degree Below the first safety threshold Then the first safety threshold is used. For the first start-up opening That is to say .

[0180] Step S809: Set the first start-up opening degree As the new first benchmark opening .

[0181] Repeat steps S805 to S808 until the pressure difference is reached. The intervention criteria are no longer met.

[0182] The following is an introduction to the full operating process of a heat pump system.

[0183] Processing module 20 first acquires environmental and system status information through sensors, such as... Figure 12 As shown, it includes the following steps:

[0184] Step S901: Obtain the current ambient temperature .

[0185] Step S902: Determine the current ambient temperature Is it below the preset extreme cold operating temperature threshold?

[0186] In some embodiments of this application, the preset extreme cold working condition temperature threshold can be set to 0°C.

[0187] Step S903: If the current ambient temperature If the temperature is below the preset extreme cold operating temperature threshold, the heat pump system is presumed to be in the preset extreme cold operating condition.

[0188] This application uses ambient temperature The system estimates the operating environment conditions of the heat pump system, thereby automatically switching between normal mode, single gas supply mode, and dual gas supply mode.

[0189] In other embodiments of this application, when the heat pump system is presumed to be under preset extreme cold conditions, the processing module 20 is configured to further perform actions such as... Figure 13 The following steps are shown.

[0190] Step S1001: Obtain the outlet water temperature of the water module heat exchanger supply branch. .

[0191] Step S1002: Determine the outlet water temperature of the water module heat exchanger supply branch. Is it below the preset energy efficiency water temperature threshold?

[0192] In some embodiments of this application, the energy efficiency water temperature threshold is set to 35°C.

[0193] Step S1003: The outlet water temperature of the water supply branch of the water module heat exchanger. When the water temperature is below the preset energy efficiency threshold, it is assumed that the heat pump system is operating under preset extreme cold conditions, but has not yet reached a steady state.

[0194] Step S1004: The outlet water temperature of the water supply branch of the water module heat exchanger. When the water temperature is not lower than the preset energy efficiency water temperature threshold, it is assumed that the heat pump system enters a steady state under the preset extreme cold conditions.

[0195] This application uses the outlet water temperature of the water supply branch of the water module heat exchanger to estimate whether the heat pump system has entered a steady state. In the low-temperature start-up stage before entering a steady state, the goal is to maximize output. After entering a steady state, the goal is to optimize energy efficiency, and the globally optimal energy efficiency parameters under the current disclosure are determined through self-optimization.

[0196] In some embodiments of this application, the processing module 20 is configured to perform, as Figure 14 The following steps are shown:

[0197] Step S1101: Obtain the current ambient temperature .

[0198] Step S1102: Determine the current ambient temperature Whether the temperature is not lower than the preset extreme cold operating temperature threshold, but not higher than the normal operating temperature threshold.

[0199] In some embodiments of this application, the preset extreme cold operating temperature threshold can be set to 0°C, and the preset normal operating temperature threshold can be set to 5°C.

[0200] Step S1103: If the current ambient temperature If the temperature is not lower than the preset extreme cold operating temperature threshold, but not higher than the normal operating temperature threshold, then one of the first valve element and the second valve element will be opened according to the current load status.

[0201] For example, when the judgment satisfies At that time, further determine the current system load. Whether it is not lower than the preset load threshold.

[0202] For example, the preset load threshold is set to 60%.

[0203] If satisfied If the first valve element is activated, the gas is replenished using the liquid reservoir, while the second valve element is closed.

[0204] If satisfied If the first valve element is closed, the second valve element is opened simultaneously, utilizing the subcooler for gas supply. At this point, the exhaust superheat can be used as a basis for... The opening degree of the second valve element is dynamically adjusted.

[0205] When the current ambient temperature is not lower than the preset extreme cold operating temperature threshold but not higher than the normal operating temperature threshold, this application executes a single gas replenishment mode, determines the gas replenishment priority based on the current load of the heat pump system, and selects one of the liquid receiver and subcooler to perform gas replenishment.

[0206] In some embodiments of this application, the processing module 20 is configured to perform, as Figure 15 The following steps are shown:

[0207] Step S1201: Obtain the current ambient temperature .

[0208] Step S1202: Determine the current ambient temperature Is the temperature higher than the normal operating temperature threshold?

[0209] Step S1203: If the current ambient temperature If the temperature exceeds the normal operating temperature threshold, then the first and second valve elements will be closed.

[0210] For example, when the judgment satisfies At that time, the first valve element and the second valve element are closed.

[0211] When the current ambient temperature is higher than the normal operating temperature threshold, this application executes the conventional mode, completely shuts down the gas supply function, and maintains the circulation of the basic heat pump system.

[0212] In the description of the above embodiments, specific features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

[0213] The above are merely specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. Heat pump system, including: A reservoir, which is fluidly connected to a first valve element; The subcooler is fluidly connected to a second valve element; The first valve element and the second valve element can respectively adjust the amount of gas supplied to the compressor; Its characteristic is that it further includes: The processing module is configured as follows: When the system reaches steady state under the preset extreme cold conditions, the liquid tank gas replenishment ratio coefficient and the subcooler gas replenishment ratio coefficient are generated according to the environmental parameters and operating parameters, respectively, and used as the reference parameter set for the current cycle. The first steady-state opening of the first valve element is generated based on the gas supply ratio coefficient of the liquid receiver, and the second steady-state opening of the second valve element is generated based on the gas supply ratio coefficient of the subcooler. A positive perturbation is applied to one of the gas supply ratio coefficient of the liquid reservoir and the gas supply ratio coefficient of the subcooler, and a negative perturbation is applied to the other to generate a differential test set. Based on the performance indicators of the differential test group, select one set from the differential test group as the benchmark parameter group for the next cycle; The energy efficiency optimization step size is updated according to the preset decay ratio, so that it gradually decreases in each iteration cycle until the set threshold is reached, and the corresponding first target weight and second target weight are obtained. A first target opening degree of the first valve element is generated based on a first target weight, and a second target opening degree of the second valve element is generated based on a second target weight.

2. The heat pump system according to claim 1, characterized in that, The environmental parameters include the current ambient temperature, and the operating parameters include the current system load; The processing module is configured as follows: Based on the current ambient temperature and current system load, the liquid reservoir gas replenishment ratio coefficient is calculated using the first mapping function; Based on the current ambient temperature and current system load, the subcooler gas replenishment ratio coefficient is calculated using the second mapping function; The output of the first mapping function decreases exponentially as the current ambient temperature increases, while the output of the second mapping function increases exponentially as the current ambient temperature increases.

3. The heat pump system according to claim 1, characterized in that: The processing module is configured as follows: The first valve element's first opening upper limit threshold is called, and the first steady-state opening of the first valve element is generated proportionally based on the first opening upper limit threshold and the liquid reservoir gas replenishment ratio coefficient. The second valve element's second opening upper limit threshold is invoked, and based on the second opening upper limit threshold and the subcooler gas supply ratio coefficient, the second steady-state opening of the second valve element is proportionally generated.

4. The heat pump system according to claim 1, characterized in that: The processing module is configured as follows: The first valve element's first opening upper limit threshold is invoked, and based on the first opening upper limit threshold and the first target weight, the first target opening of the first valve element is proportionally generated; The second valve element's second opening upper limit threshold is invoked, and based on the second opening upper limit threshold and the second target weight, the second target opening of the second valve element is proportionally generated.

5. The heat pump system according to any one of claims 1 to 4, characterized in that: Under preset extremely cold operating conditions, but during the preset cold start phase, the processing module is configured as follows: The compressor is configured to operate at a frequency within a preset high-frequency output range; The first reference opening degree of the first valve element is preset based on the linear negative correlation function of the current ambient temperature; Calculate the pressure difference between the reservoir pressure and the condensation pressure, set a dynamic disturbance factor, and dynamically correct the first reference opening to generate a first start-up opening, wherein the first start-up opening is not lower than a first safety threshold.

6. The heat pump system according to claim 5, characterized in that: Under preset extremely cold operating conditions, but during the preset cold start phase, the processing module is configured as follows: Using the first starting opening degree as a reference, the second reference opening degree of the second valve element is determined by a preset coupling coefficient; The exhaust superheat is used as a real-time feedback variable to dynamically correct the second reference opening. The baseline opening increment is calculated based on the degree of subcooling. The second reference opening degree and the reference opening degree increment are superimposed to generate the second start-up opening degree of the second valve element, wherein the second start-up opening degree is not higher than the second safety threshold.

7. The heat pump system according to any one of claims 1 to 4, characterized in that: The processing module is configured as follows: Get the current ambient temperature; Determine whether the current ambient temperature is lower than the preset extreme cold working condition temperature threshold; If the current ambient temperature is lower than the preset extreme cold operating temperature threshold, the heat pump system is presumed to be in the preset extreme cold operating condition.

8. The heat pump system according to claim 7, characterized in that: When the heat pump system is presumed to be under a preset extremely cold operating condition, the processing module is configured as follows: Obtain the outlet water temperature of the water supply branch of the water module heat exchanger; Determine whether the outlet water temperature is lower than the preset energy efficiency water temperature threshold; When the outlet water temperature is lower than the preset energy efficiency water temperature threshold, it is assumed that the heat pump system is under preset extreme cold conditions, but has not entered a steady state. When the outlet water temperature is not lower than the preset energy efficiency water temperature threshold, it is assumed that the heat pump system enters a steady state under the preset extreme cold operating conditions.

9. The heat pump system according to any one of claims 1 to 4, characterized in that: The processing module is configured as follows: Get the current ambient temperature; Determine whether the current ambient temperature is not lower than the preset extreme cold working condition temperature threshold, but not higher than the normal working condition temperature threshold. If the current ambient temperature is not lower than the preset extreme cold operating temperature threshold but not higher than the normal operating temperature threshold, then one of the first valve element and the second valve element is opened according to the current load status.

10. The heat pump system according to any one of claims 1 to 4, characterized in that: The processing module is configured as follows: Get the current ambient temperature; Determine whether the current ambient temperature is higher than the normal operating temperature threshold; If the current ambient temperature is higher than the normal operating temperature threshold, then the first valve element and the second valve element are closed.

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