A heat recovery air conditioning system and control method thereof

Abstract

The present application relates to the field of air conditioning technology, and in particular to a heat recovery air conditioning system and a control method thereof. The system includes: a heat recovery component, connected to a compressor, a condenser and a target pipeline to be heated, for heat exchange with the target pipeline; a first temperature acquisition device, arranged adjacent to the evaporator, for collecting the current ambient temperature; a second temperature acquisition device, arranged at the outlet of the evaporator, for collecting the actual superheat at the outlet of the evaporator; a controller, respectively connected to the first temperature acquisition device, the second temperature acquisition device and the hot water switch of the target pipeline, for controlling the expansion valve to operate according to the first control strategy, and to operate according to the second control strategy when the hot water switch is turned on; it can effectively avoid the problem that the refrigerant flow control accuracy decreases when the demand for hot water is large, which affects the operating efficiency of the air conditioning system.

Description

Technical Field

[0001] The present application relates to the field of air conditioning technology, and in particular to a heat recovery air conditioning system and a control method thereof. Background Art

[0002] The heat recovery device is a device used for energy reuse and recycling in air conditioning systems. Its setting can significantly improve energy utilization efficiency, reduce energy consumption, and have a positive impact on the environment. The heat recovery device can recover the waste heat generated during the operation of the air conditioning system and convert it into usable thermal energy for heating, hot water preparation, etc., thereby improving the overall energy efficiency of the air conditioning system and reducing dependence on traditional energy.

[0003] After the existing air conditioners are equipped with heat recovery devices, most of them will not adjust the refrigerant flow when hot water supply is needed. As a result, when the demand for hot water is large, the refrigerant flow control accuracy decreases, which affects the operating efficiency of the air conditioning system. Summary of the invention

[0004] Based on this, it is necessary to provide a heat recovery air conditioning system and a control method thereof to address the above technical problems.

[0005] In a first aspect, the present application provides a heat recovery air conditioning system, the system comprising a compressor, a condenser, an expansion valve and an evaporator connected to a controller; the system further comprises:

[0006] A heat recovery component is connected to the compressor, the condenser and the target pipeline to be heated, and is used for heat exchange with the target pipeline;

[0007] A first temperature collection device, disposed adjacent to the evaporator, for collecting the current ambient temperature;

[0008] The second temperature collection device is arranged at the outlet of the evaporator and is used to collect the actual superheat degree at the outlet of the evaporator;

[0009] A controller, connected to the first temperature acquisition device, the second temperature acquisition device and the hot water switch of the target pipeline, respectively, for controlling the expansion valve to operate according to the first control strategy, and to operate according to the second control strategy when the hot water switch is turned on;

[0010] The first control strategy includes: based on the current ambient temperature and the set temperature, calculating the first refrigerant flow required to adjust the current ambient temperature to the set temperature within a preset time; adjusting the expansion valve once according to the first refrigerant flow, and monitoring the actual superheat at the evaporator outlet; in response to a difference between the actual superheat and the preset superheat interval, adjusting the expansion valve twice with the goal of eliminating the difference and minimizing the adjustment amount of the first refrigerant flow;

[0011] The second control strategy includes: calling pre-stored historical data; the historical data includes the refrigerant flow corresponding to each set temperature adjusted to each ambient temperature when the hot water switch is turned on; determining the second refrigerant flow currently required based on the current ambient temperature, the set temperature and the historical data; and adjusting the expansion valve three times according to the second refrigerant flow.

[0012] In one embodiment, the heat recovery component is a double-effect heat recovery component including a first heat recovery device and a second heat recovery device; the first heat recovery device is connected to the exhaust port of the compressor; and the second heat recovery device is connected to the condenser.

[0013] In one embodiment, the compressor is a variable frequency compressor, and the expansion valve is a variable frequency controlled expansion valve; the frequency control of the expansion valve corresponds to the frequency of the variable frequency compressor.

[0014] In a second aspect, the present application provides a heat recovery air conditioning system control method, the method comprising:

[0015] Controlling the expansion valve to operate according to the first control strategy, and when the hot water switch is turned on, operating according to the second control strategy;

[0016] The first control strategy includes: based on the current ambient temperature and the set temperature, calculating the first refrigerant flow required to adjust the current ambient temperature to the set temperature within a preset time; adjusting the expansion valve once according to the first refrigerant flow, and monitoring the actual superheat at the evaporator outlet; in response to a difference between the actual superheat and the preset superheat interval, adjusting the expansion valve twice with the goal of eliminating the difference and minimizing the adjustment amount of the first refrigerant flow;

[0017] The second control strategy includes: calling pre-stored historical data; the historical data includes the refrigerant flow corresponding to each set temperature adjusted to each ambient temperature when the hot water switch is turned on; determining the second refrigerant flow currently required based on the current ambient temperature, the set temperature and the historical data; and adjusting the expansion valve three times according to the second refrigerant flow.

[0018] In one embodiment, the method further comprises:

[0019] The compressor operation is controlled based on the required first refrigerant flow rate, and a plurality of operating states of the compressor during operation are determined; the operating states include a start-stop process state and a load state;

[0020] Corresponding control of the expansion valve opening according to the operating status includes: in response to the compressor being in the start-stop process, controlling the expansion valve to enter a first opening; in response to the compressor being in a load state, controlling the expansion valve to enter a second opening; the second opening includes the openings of multiple valve steps corresponding to the primary adjustment, secondary adjustment and tertiary adjustment of the expansion valve; the opening of each valve step is valve step controlled based on a PID control algorithm; the first opening is smaller than the second opening.

[0021] In one embodiment, the method further comprises:

[0022] In response to a change in the current ambient temperature, the target temperature is calculated based on the following formula:

[0023] Target temperature = set temperature + (starting ambient temperature - current ambient temperature) × preset compensation coefficient.

[0024] In one embodiment, the method further comprises:

[0025] Obtaining the working environment and user needs, and setting preset temperature compensation coefficients of multiple coefficient levels; the working environment includes an extreme environment with a temperature difference greater than a preset temperature difference, and a normal environment with a temperature difference less than a preset temperature difference; user needs include a control mode of rapid control with a control rate greater than a first preset rate, and a control mode of comfortable control with a control rate less than the first preset rate;

[0026] Establish the correlation between each control mode and each coefficient level, including comfortable control in extreme environment, comfortable control in normal environment, rapid control in extreme environment and rapid control in normal environment;

[0027] In response to a change in the current ambient temperature, a temperature compensation coefficient corresponding to the level of the control mode is determined according to the current working environment and user needs.

[0028] In one embodiment, the method further comprises:

[0029] Divide the compressor load into multiple load levels from high to low, and set multiple temperature difference intervals;

[0030] A mapping relationship between the temperature difference interval and each load level is established in order from high to low according to the temperature difference of the temperature difference interval;

[0031] Based on the temperature adjustment difference between the current ambient temperature and the set temperature, determine the temperature difference interval that the temperature adjustment difference satisfies, and select the load level of the compressor based on the mapping relationship;

[0032] Controls compressor operation based on the selected load level.

[0033] In one embodiment, the system further comprises an oil separator; the compressor further comprises an oil return control valve; the load level comprises a load level of 25%, a load level of 50%, a load level of 75% and a load level of 100%; and the method further comprises:

[0034] When the compressor is started for the first preset time, the load level of the compressor is below 50% and the refrigerant flow is less than the first preset flow, the compressor is controlled to enter the oil return mode; the oil return mode includes: controlling the oil return control valve to open, and controlling the expansion valve opening based on the refrigerant flow.

[0035] In one embodiment, the system further comprises a water pump; and the method further comprises:

[0036] In response to the current ambient temperature being less than a preset temperature, the water pump is controlled to run for a second preset time and a prompt to enter an antifreeze mode is output, wherein the antifreeze mode prompt is used to instruct the user to check whether a pipe connected to the water pump is frozen.

[0037] The above-mentioned heat recovery air conditioning system and control method thereof can recover the waste heat generated by the compressor and the condenser through the heat recovery component, and perform heat exchange with the target pipeline; during the operation of the air conditioner, the current ambient temperature is collected by the first temperature collection device, and the actual superheat is collected by the second temperature collection device, and then the controller is controlled to judge the first refrigerant flow required for temperature control according to the current ambient temperature and the user set temperature without heat recovery, and the expansion valve opening is adjusted once according to the first refrigerant flow demand to make the air conditioner run in an orderly manner; then during the operation of the air conditioner, the effectiveness of the air conditioning control is judged by the actual superheat and the impact on the compressor is considered, and the expansion valve is further adjusted for a second time with the goal of eliminating the difference between the actual superheat and the preset superheat to control the efficient operation of the air conditioning system; finally, when hot water supply is required, the impact of the heat loss of the refrigerant on the actual superheat is considered, and the current refrigerant flow is adjusted three times in combination with the second refrigerant flow required to adjust each ambient temperature to the set temperature in the historical data, which effectively avoids the situation where the refrigerant flow control accuracy decreases when the demand for hot water is large, resulting in the problem of affecting the operating efficiency of the air conditioning system. BRIEF DESCRIPTION OF THE DRAWINGS

[0038] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the related technologies, the drawings required for use in the embodiments or the related technical descriptions are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0039] Figure 1A schematic diagram of the connection relationship of a heat recovery air conditioning system in one embodiment;

[0040] Figure 2 A flowchart of the steps of determining the opening of the expansion valve according to the control state of the compressor in one embodiment;

[0041] Figure 3 A flowchart of the steps of setting the temperature compensation coefficient according to the working environment and user needs in one embodiment;

[0042] Figure 4 FIG. 1 is a flow chart of steps for determining a compressor load level in one embodiment. DETAILED DESCRIPTION

[0043] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of the present application, so the present application is not limited by the specific embodiments disclosed below.

[0044] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of this application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0045] In this application, unless otherwise clearly specified and limited, the terms "connected", "connection" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0046] It should be noted that when an element is considered to be "connected" to another element, it can be directly connected to the other element, or connected to the other element through an intermediate element. In addition, the "connection" in the following embodiments should be understood as "electrical connection", "communication connection", etc. if there is transmission of electrical signals or data between the connected objects.

[0047] In an exemplary embodiment, a heat recovery air conditioning system is provided, such as Figure 1As shown, the system includes a compressor, a condenser, an expansion valve and an evaporator connected to a controller; the system also includes:

[0048] A heat recovery component is connected to the compressor, the condenser and the target pipeline to be heated, and is used for heat exchange with the target pipeline;

[0049] A first temperature collection device, disposed adjacent to the evaporator, for collecting the current ambient temperature;

[0050] The second temperature collection device is arranged at the outlet of the evaporator and is used to collect the actual superheat degree at the outlet of the evaporator;

[0051] A controller, connected to the first temperature acquisition device, the second temperature acquisition device and the hot water switch of the target pipeline, respectively, for controlling the expansion valve to operate according to the first control strategy, and to operate according to the second control strategy when the hot water switch is turned on;

[0052] The first control strategy includes: based on the current ambient temperature and the set temperature, calculating the first refrigerant flow required to adjust the current ambient temperature to the set temperature within a preset time; adjusting the expansion valve once according to the first refrigerant flow, and monitoring the actual superheat at the evaporator outlet; in response to a difference between the actual superheat and the preset superheat interval, adjusting the expansion valve twice with the goal of eliminating the difference and minimizing the adjustment amount of the first refrigerant flow;

[0053] The second control strategy includes: calling pre-stored historical data; the historical data includes the refrigerant flow corresponding to each set temperature adjusted to each ambient temperature when the hot water switch is turned on; determining the second refrigerant flow currently required based on the current ambient temperature, the set temperature and the historical data; and adjusting the expansion valve three times according to the second refrigerant flow.

[0054] Specifically, the heat recovery air-conditioning system provided in the present application can provide the waste heat generated by the compressor to the target pipeline to be heated by setting a heat recovery component between the compressor and the condenser; when the pipeline to be heated does not need to be supplied with hot water, the expansion valve is adjusted by the first control strategy, and when the pipeline to be heated needs to be supplied with hot water, the expansion valve is adjusted by the second control strategy, thereby ensuring that the superheat of the refrigerant entering the condenser is not too low, thereby causing the air conditioner to fail to control the ambient temperature, and can also avoid the superheat of the refrigerant entering the condenser not meeting the expectation, which in turn leads to a lengthy feedback adjustment process and inaccurate precision control, and there is also a risk of liquid hammer.

[0055] Specifically, the heat recovery component can be connected to the compressor and the condenser respectively, and is used to absorb the waste heat of the compressor, help the condenser to perform the condensation function, and absorb the waste heat to be volatilized in the condenser.

[0056] Furthermore, the heat recovery component is designed with efficient heat transfer materials and structures to ensure that heat recovery is completed with minimal energy loss.

[0057] Exemplarily, the heat recovery component is also provided with an intelligent temperature sensor, which is connected to the target pipeline to be heated. When the water temperature in the target pipeline reaches a set value, the heat recovery loop is automatically closed to avoid excessive water temperature or energy waste.

[0058] Exemplarily, the heat recovery component can also be connected in series between the compressor and the condenser. The high-temperature gaseous refrigerant discharged from the compressor first enters the heat recovery device and exchanges heat with domestic water (or other gaseous and liquid media), thereby utilizing waste heat to heat the water source. After the heat recovery is completed, the refrigerant continues to enter the condenser, and after further heat release, enters the evaporator through the expansion valve to complete the cooling process. The entire heat recovery and refrigeration process ensures efficient use of energy while realizing the dual functions of air conditioning and hot water supply.

[0059] Specifically, the first temperature collecting device may also be arranged at other locations in the application environment of the air conditioning system.

[0060] Furthermore, the first temperature collecting device may include a plurality of temperature collectors which are dispersedly arranged in the application environment of the air conditioning system.

[0061] A heat recovery air conditioning system provided in an embodiment of the present application can recover waste heat generated by a compressor and a condenser through a heat recovery component and perform heat exchange with a target pipeline; during the operation of the air conditioner, the current ambient temperature is collected through a first temperature collection device, and the actual superheat is collected through a second temperature collection device, and then the controller is controlled to judge the first refrigerant flow required for temperature control according to the current ambient temperature and the user set temperature without heat recovery, and the expansion valve opening is adjusted once according to the first refrigerant flow demand to make the air conditioner run in an orderly manner; then during the operation of the air conditioner, the effectiveness of the air conditioning control is judged by the actual superheat and the impact on the compressor is considered, and the expansion valve is further adjusted for a second time with the goal of eliminating the difference between the actual superheat and the preset superheat to control the efficient operation of the air conditioning system; finally, when hot water supply is required, the impact of the heat loss of the refrigerant on the actual superheat is considered, and the current refrigerant flow is adjusted three times in combination with the second refrigerant flow required to adjust each ambient temperature to the set temperature in historical data, effectively avoiding the problem of reduced refrigerant flow control accuracy when the demand for hot water is large, which affects the operating efficiency of the air conditioning system.

[0062] In an exemplary embodiment, the heat recovery component is a double-effect heat recovery component including a first heat recovery device and a second heat recovery device; the first heat recovery device is connected to the exhaust port of the compressor; and the second heat recovery device is connected to the condenser.

[0063] Specifically, compared with a single heat recovery device, double-effect heat recovery technology can make more comprehensive use of waste heat, and is particularly suitable for large-scale central air-conditioning systems or industrial refrigeration systems to improve overall energy efficiency.

[0064] Specifically, the first heat recovery device and the second heat recovery device are both connected to the target pipeline to be heated.

[0065] In an exemplary embodiment, the compressor is a variable frequency compressor, and the expansion valve is a variable frequency controlled expansion valve; the frequency control of the expansion valve corresponds to the frequency of the variable frequency compressor.

[0066] Specifically, the variable frequency compressor adjusts the cooling capacity by changing the speed of the motor, thereby achieving precise control of the temperature; when the temperature reaches the set value, the speed of the compressor will be reduced to maintain the temperature stable, which can not only provide a more comfortable indoor environment, but also significantly reduce energy consumption.

[0067] In addition, the variable frequency expansion valve controls the cooling effect by adjusting the flow of refrigerant. It can automatically adjust the opening of the expansion valve according to the change of temperature to ensure that the refrigerant flow matches the cooling capacity of the compressor. When the frequency of the variable frequency compressor matches that of the variable frequency expansion valve, it can effectively improve energy efficiency, reduce the wear and air pressure of the compressor and expansion valve, and increase the life of both.

[0068] On the other hand, the present application also provides a heat recovery air conditioning system control method, the method comprising the following steps:

[0069] Controlling the expansion valve to operate according to the first control strategy, and when the hot water switch is turned on, operating according to the second control strategy;

[0070] The first control strategy includes: based on the current ambient temperature and the set temperature, calculating the first refrigerant flow required to adjust the current ambient temperature to the set temperature within a preset time; adjusting the expansion valve once according to the first refrigerant flow, and monitoring the actual superheat at the evaporator outlet; in response to a difference between the actual superheat and the preset superheat interval, adjusting the expansion valve twice with the goal of eliminating the difference and minimizing the adjustment amount of the first refrigerant flow;

[0071] The second control strategy includes: calling pre-stored historical data; the historical data includes the refrigerant flow corresponding to each set temperature adjusted to each ambient temperature when the hot water switch is turned on; determining the second refrigerant flow currently required based on the current ambient temperature, the set temperature and the historical data; and adjusting the expansion valve three times according to the second refrigerant flow.

[0072] Specifically, without performing heat exchange operation with the target pipeline through the heat recovery component, the refrigerant flow rate of the compressor exhaust can be set according to the first refrigerant flow rate calculated when the current ambient temperature is controlled to the set temperature, and then the expansion valve opening is controlled according to the first refrigerant flow rate, so that the first refrigerant flow rate can effectively meet the refrigeration demand for the set temperature.

[0073] Furthermore, the preset superheat interval is used to verify the actual temperature of the refrigerant after passing through the evaporator, and then ensure that the refrigeration demand is met by ensuring the superheat of the refrigerant after participating in the refrigeration; in addition, when the actual superheat is lower than the superheat interval, it means that the refrigerant about to enter the compressor may experience liquid hammer, and that the utilization efficiency of the refrigerant energy is too low. Therefore, the above situation is avoided by setting the superheat interval, and when it is higher than the superheat interval, it means that the refrigeration demand is not fully met.

[0074] Furthermore, the superheat range can be set to 3-7 degrees Celsius.

[0075] Specifically, when heat is exchanged with the target pipeline through the heat recovery component, the temperature of the refrigerant entering the condenser is reduced and further reduced in the condenser, which may affect the superheat of the condenser entering the evaporator; and after the impact is caused, the adjustment method of primary or secondary adjustment may cause the refrigerant flow rate to obviously fail to meet the requirements before the superheat correction. Therefore, in the historical records, when the hot water switch is turned on, each ambient temperature is adjusted to the refrigerant flow rate corresponding to each set temperature, and the second refrigerant flow rate currently required is determined in combination with the current ambient temperature, the set temperature, and the historical data to ensure that the amount of refrigerant does not show obvious deviations at the initial stage of the target pipeline connection.

[0076] In an exemplary embodiment, when the amount of refrigerant meets the temperature control requirement by adjusting the expansion valve opening three times, the expansion valve is further adjusted with the goal of eliminating the difference and minimizing the adjustment amount of the second refrigerant flow.

[0077] In an exemplary embodiment, when the expansion valve is adjusted once, twice or three times, the compressor is adjusted synchronously according to the corresponding refrigerant flow rate, so that the compressor can discharge the refrigerant flow rate corresponding to the once, twice or three times adjustment.

[0078] In an exemplary embodiment, Figure 2 As shown, the method further includes the following steps S102 to S104.

[0079] in:

[0080] S102, controlling the operation of the compressor based on the required first refrigerant flow rate, and determining a plurality of operating states during the operation of the compressor; the operating states include a start-stop process state and a load state.

[0081] Specifically, the pressure difference between the high-pressure side and the low-pressure side of the system has not been fully established, and the system flow is unstable. In this case, the opening of the expansion valve is usually slightly reduced relative to the normal working state to prevent excessive refrigerant from entering the evaporator and causing liquid hammer. When the system pressure stabilizes, the expansion valve opening gradually returns to normal levels.

[0082] Furthermore, the compressor operates under different load conditions according to the refrigeration demand, and the expansion valve needs to adjust the flow rate of the refrigerant accordingly.

[0083] For example, since modern compressors usually use variable frequency technology, the speed of the compressor can be dynamically adjusted according to actual needs, and the opening of the expansion valve should also change accordingly; the variable frequency compressor can flexibly adjust the speed of the compressor according to the actual cold load changes, thereby controlling the refrigerant flow. In this case, the opening of the expansion valve needs to be linked with the variable frequency of the compressor to ensure that the refrigerant flow matches the compressor output; when the compressor speed decreases (load decreases), the expansion valve opening should be reduced accordingly; when the speed increases (load increases), the expansion valve opening needs to be increased. The control of the variable frequency compressor makes the adjustment of the expansion valve opening more refined, which helps to further improve the system efficiency.

[0084] S104, corresponding control of the expansion valve opening according to the operating status includes: in response to the compressor being in the start-stop process, controlling the expansion valve to enter the first opening; in response to the compressor being in the load state, controlling the expansion valve to enter the second opening; the second opening includes the openings of multiple valve steps corresponding to the primary adjustment, secondary adjustment and tertiary adjustment of the expansion valve; the opening of each valve step is valve step controlled based on the PID control algorithm; the first opening is smaller than the second opening.

[0085] Specifically, when the compressor is in a partial load state (e.g., 50% or 75% load), the system's cooling demand is low, and the expansion valve opening should be reduced accordingly to ensure that the refrigerant flow in the system matches the current load level. If the expansion valve is opened too much at this time, it may cause excessive refrigerant, and the refrigerant in the evaporator is not completely evaporated, resulting in liquid refrigerant in the compressor return pipe; therefore, when the compressor is running at partial load, the expansion valve opening is reduced relative to the full load condition to reduce the refrigerant flow. At the same time, by monitoring the superheat, it is ensured that the refrigerant entering the evaporator is completely evaporated to maintain stable system operation.

[0086] Specifically, the compressor is running at full load: When the compressor is running at full load, the cooling demand is high, and the opening of the expansion valve should be increased to provide enough refrigerant to enter the evaporator to ensure that the evaporator can provide sufficient cooling capacity. In this case, it is necessary to control the actual superheat by controlling the opening of the expansion valve to prevent excessive refrigerant from causing the liquid in the evaporator to not be completely evaporated.

[0087] Among them, the opening control of the expansion valve usually adopts PID control or more complex fuzzy control, model predictive control (MPC) algorithm, and inputs parameters such as superheat, compressor load status, compressor speed, and system pressure into the control algorithm to adjust the opening of the expansion valve in real time; by adjusting the proportional (P), integral (I) and differential (D) parameters, the opening of the expansion valve can be dynamically adjusted as the compressor load changes and superheat fluctuations.

[0088] Exemplarily, the expansion valve opening can also be adjusted by fuzzy control. Fuzzy control is suitable for processing uncertainties and nonlinear changes in the system. Through fuzzy logic rules, combined with inputs such as superheat and compressor load, the expansion valve opening can be intelligently adjusted.

[0089] Exemplarily, model predictive control (MPC) can also be used to control the expansion valve opening based on the compressor load: based on the system model, future load changes are predicted and the expansion valve opening is adjusted in advance to ensure that the system is always in the best operating state.

[0090] In an exemplary embodiment, if the compressor is running at 50% load, the opening of the expansion valve will be reduced accordingly to ensure that the flow of the refrigerant matches the load of the evaporator. The superheat control is maintained within an appropriate range (e.g., 4-5°C) to avoid excess or insufficient refrigerant.

[0091] If the flow demand of the compressor increases under high load or full load conditions, the expansion valve opening will increase accordingly to provide more refrigerant to ensure that the evaporator can still effectively exchange heat under high load.

[0092] In an exemplary embodiment, the method further comprises the steps of:

[0093] In response to a change in the current ambient temperature, the target temperature is calculated based on the following formula:

[0094] Target temperature = set temperature + (starting ambient temperature - current ambient temperature) × preset compensation coefficient.

[0095] Specifically, when the ambient temperature changes, the original algorithm for calculating the refrigerant flow rate based on the current ambient temperature and the set temperature will deviate, especially when the ambient temperature difference is too large. This deviation is particularly obvious, so it is necessary to perform temperature compensation according to the target temperature calculation formula. When the ambient temperature drops, the system automatically increases the air conditioning temperature; when the ambient temperature rises, the system lowers the temperature to ensure the stability of the indoor temperature. This compensation mechanism uses multi-condition adaptive adjustment and is not only applicable to cooling conditions, but also to heating and heat recovery conditions. According to the current system mode, the temperature compensation strategy will be automatically adjusted to ensure efficient operation under various conditions.

[0096] Determining the compensation coefficient is an important step in ensuring that the temperature compensation algorithm is accurate and flexible. It determines the sensitivity of the system to the set temperature adjustment when the ambient temperature changes.

[0097] In an exemplary embodiment, the preset compensation coefficient may be preset to 0.2. If the current ambient temperature is 32 degrees Celsius, the starting ambient temperature is 30 degrees Celsius, and the set temperature is 24 degrees Celsius, the target temperature may be 23.6 degrees Celsius.

[0098] Specifically, based on the above examples, it can be seen that when the ambient temperature changes, the target temperature is calculated by formulating a temperature compensation strategy, and the set temperature is replaced by the target temperature for temperature compensation. Then, when the current ambient temperature rises, the target temperature can effectively compensate for the refrigerant flow deviation caused by the temperature rise.

[0099] In an exemplary embodiment, the compensation coefficient is generally determined based on the following factors: system performance, the range of change in ambient temperature, the requirements for control speed, equipment load capacity, and historical operation conditions.

[0100] Different air-conditioning systems (such as household air-conditioning, industrial cooling systems, central air-conditioning, etc.) have different response speeds and temperature control accuracy requirements for system characteristics and performance requirements; the compensation coefficient needs to be adjusted according to the specific system characteristics and design goals; if the system responds slowly to temperature changes, the compensation coefficient can be appropriately increased to speed up the response to ambient temperature changes; if the system has high requirements for temperature control accuracy, the compensation coefficient should be appropriately reduced to avoid large temperature fluctuations.

[0101] Regarding the impact of the amplitude of ambient temperature changes, the amplitude of ambient temperature changes may vary significantly in different usage scenarios; for systems with large ambient temperature differences, the compensation coefficient can be appropriately increased to quickly adapt to changes; for systems with small temperature differences, the compensation coefficient should be reduced to avoid frequent temperature adjustments. Large temperature differences: such as outdoor air-conditioning systems or cooling systems in extreme environments, the ambient temperature may change greatly, so a higher compensation coefficient is required to quickly respond to temperature changes; under small temperature differences, when the indoor environment is relatively stable (such as air conditioning inside an office building), the temperature difference changes less, and the compensation coefficient can be set lower to prevent excessive temperature adjustments.

[0102] The user's comfort requirements, user sensitivity to temperature and comfort requirements will also affect the setting of the compensation coefficient. If the user is sensitive to temperature fluctuations, or has high requirements for temperature control accuracy when the ambient temperature changes, a smaller compensation coefficient is required to ensure a smoother temperature change; if faster adjustment is allowed, the compensation coefficient can be increased. Under high comfort requirements, if it is used in high-end residences or places that require precise temperature control, the compensation coefficient should be smaller and the temperature adjustment will be smoother; under ordinary comfort requirements, such as for general environments, such as factories or public places, the compensation coefficient can be slightly larger to adapt to temperature changes more quickly.

[0103] Too high a compensation coefficient may lead to frequent and drastic adjustments in the system, increasing energy consumption and equipment wear. Therefore, the load capacity and energy-saving requirements of the equipment are also an important reference for determining the compensation coefficient. Systems with strong load capacity, such as industrial-grade or central air-conditioning systems, can appropriately increase the compensation coefficient to quickly adapt to environmental changes. Systems with high energy-saving requirements, such as energy-saving air conditioners, should choose a smaller compensation coefficient to reduce energy consumption and extend the service life of the equipment.

[0104] Furthermore, the method for obtaining the temperature compensation coefficient may specifically include: determining the optimal compensation coefficient through experimental debugging; during the actual operation of the system, gradually adjusting the compensation coefficient, and observing whether the system's response to changes in ambient temperature meets the load requirements; through multiple tests and data recording, ultimately determining the most suitable compensation coefficient.

[0105] Furthermore, the system's thermodynamic characteristics can be modeled to calculate the system's response to ambient temperature changes, and the compensation coefficient can be determined based on the model. For example, the range of the compensation coefficient can be determined based on the system's thermal inertia and response speed.

[0106] Furthermore, the compensation coefficient can be automatically adjusted through machine learning or adaptive algorithms; the system will automatically optimize the compensation coefficient based on historical operating data to improve temperature control accuracy and efficiency. By collecting long-term ambient temperature changes and system response data, the compensation coefficient is automatically adjusted so that it can be adaptively optimized under different time periods and load conditions.

[0107] Furthermore, in some application scenarios, the compensation coefficient itself can also be dynamically changed. For example, the compensation coefficient can be dynamically adjusted according to external conditions such as the ambient temperature fluctuation range, system load conditions and other factors. Dynamic compensation can be achieved by real-time monitoring of the rate of change of the ambient temperature: when the ambient temperature changes rapidly, the compensation coefficient can be appropriately increased to quickly respond to temperature changes. When the ambient temperature changes slowly or is relatively stable, the compensation coefficient can be automatically reduced to prevent over-adjustment.

[0108] For example, according to different application scenarios, the typical compensation coefficient value range can be referred to as follows: Home air conditioning system: 0.1-0.3 (smaller adjustment range, adapting to slower environmental changes) Commercial central air conditioning system: 0.3-0.6 (adapting to larger temperature changes, fast response) Industrial cooling system: 0.6-1.0 (requires higher response speed, adapting to drastic temperature changes)

[0109] For example, assuming that the ambient temperature changes by about 10°C and the system can withstand an adjustment range of 2°C, the compensation coefficient can be calculated according to the following formula: Compensation coefficient = allowable adjustment temperature / ambient temperature change range = 2°C / 10°C = 0.2. Through the above formula, a preliminary estimate of the compensation coefficient can be obtained, which can be further adjusted according to actual operating conditions.

[0110] In an exemplary embodiment, Figure 3 As shown, the method further includes the following steps S202 to S206. Among them:

[0111] S202, obtaining the working environment and user needs, and setting preset temperature compensation coefficients of multiple coefficient levels; the working environment includes an extreme environment with a temperature difference greater than a preset temperature difference, and a normal environment with a temperature difference less than a preset temperature difference; user needs include rapid control with a control rate greater than a first preset rate, and comfortable control with a control rate less than a first preset rate.

[0112] Specifically, the preset temperature difference can be determined based on the time for the air-conditioning system with preset power to adjust the preset temperature difference during the adjustment process, and no specific limitation is made here.

[0113] Furthermore, the control rate is directly linked to the user's comfort. When the control rate is fast, the user may be sensitive to temperature changes, causing discomfort. Therefore, by setting the first preset rate, the control method is selected based on the user.

[0114] S204, establishing correlations between various control modes for comfortable control in extreme environments, comfortable control in normal environments, rapid control in extreme environments, and rapid control in normal environments and various coefficient levels.

[0115] Specifically, given environmental changes and user needs, the choice of control coefficient can correspond to multiple combinations of working environment and user needs. By formulating the impact of each combination on the control rate, more detailed temperature difference compensation can be performed without corresponding to the working environment and user needs.

[0116] S206, in response to a change in the current ambient temperature, determining a temperature compensation coefficient corresponding to a level of the control method according to the current working environment and user needs.

[0117] Specifically, the setting value of the temperature compensation coefficient can be derived and given based on the aforementioned embodiment, and is not specifically limited here.

[0118] It should be noted that the temperature compensation coefficients corresponding to different working environments and user needs are different; among them, they can be corresponded one by one with the various control modes of comfort control in extreme environments, comfort control in normal environments, rapid control in extreme environments and rapid control in normal environments based on the coefficient levels from small to large.

[0119] In an exemplary embodiment, when the refrigerant flow rate after the secondary adjustment is given, if the user sets the set temperature for a secondary time so that the temperature difference between the set temperature and the current ambient temperature is larger, it means that the user needs a more intensive temperature control method, and thus the coefficient of the temperature compensation coefficient is upgraded by one coefficient level; if the user sets the set temperature for a secondary time so that the temperature difference between the set temperature and the current ambient temperature is smaller, it means that the user needs a less intensive temperature control method, and thus the coefficient of the temperature compensation coefficient is upgraded by one coefficient level.

[0120] In an exemplary embodiment, Figure 4 As shown, the method also includes the following steps S302 to S308.

[0121] in:

[0122] S302, dividing the compressor load into multiple load levels from high to low, and setting multiple temperature difference intervals.

[0123] Specifically, based on the change of ambient temperature, different load levels of the compressor can be set. By setting the load level of the compressor, the compressor can work at the corresponding load level in the corresponding temperature difference range, so that the compressor can start quickly when the user requires a large temperature difference. When the user requires a small temperature difference, the compressor does not need to be overloaded to cause energy waste.

[0124] S304: Establish mapping relationships between the temperature difference intervals and the load levels in order from high to low according to the temperature differences in the temperature difference intervals.

[0125] Specifically, by establishing a mapping relationship, the set load level of the compressor is made to correspond one-to-one with the temperature difference intervals established in sequence from high to low.

[0126] Exemplarily, the load levels may include load levels of 25%, 50%, 75% and 100% load; the temperature difference range may be divided into corresponding load levels based on the maximum temperature and the minimum temperature that the air conditioner can adjust, combined with the national average maximum temperature and the minimum temperature, to ensure the universality of the air-conditioning system provided in the embodiment of the present application.

[0127] S306: Based on the temperature adjustment difference between the current ambient temperature and the set temperature, determine the temperature difference interval satisfied by the temperature adjustment difference, and select the load level of the compressor based on the mapping relationship.

[0128] Specifically, according to the user's setting of the set temperature and the current ambient temperature, combined with the aforementioned mapping relationship, the load level of the compressor is adjusted so that the compressor can operate at a reasonable load.

[0129] S308, controlling the operation of the compressor based on the selected load level.

[0130] In an exemplary embodiment, the load regulation mechanism of the compressor optimizes energy consumption through different load levels to ensure that the system operates efficiently under different cooling requirements. This regulation can not only reduce unnecessary energy consumption, but also extend the life of the equipment and improve system stability. The load level adjustment is usually based on multiple factors such as ambient temperature, set temperature difference, current cooling load, and system operating efficiency. The following is a detailed description of the circumstances under which the compressor is adjusted to different load levels:

[0131] Specifically, the applicable scenario of the 25% load level (low-load operation) is when the current ambient temperature is slightly different from the set set temperature (usually between 1-2°C). At this time, the system's cooling demand is low, and only a small amount of refrigerant needs to flow into the evaporator to meet the demand. At night or during periods of low workload, the air-conditioning load is low and the ambient temperature does not change much. At this time, it is only necessary to maintain the system's low-load operation state. When the ambient temperature has reached the set temperature, in order to maintain the temperature, the system can maintain the ambient temperature by running the compressor at a low load, avoiding frequent starting and stopping of the compressor. Advantages: Lowest energy consumption: When the compressor runs at a low load, the energy consumption is the lowest, which can effectively avoid over-cooling. Strong system stability: 25% load is suitable for slight adjustment or maintenance of the current temperature, which will not cause large temperature fluctuations, and will contribute to the smooth operation and energy saving of the equipment.

[0132] For example, if the set temperature is 24° C. and the current ambient temperature is 25° C., the system only needs to slightly adjust the ambient temperature to reach the set temperature, and the compressor can operate at a load level of 25%.

[0133] Specifically, the applicable scenario of the 50% load level (medium load operation) is when the difference between the ambient temperature and the set temperature is between 2-4°C, the system requires medium cooling capacity, and the compressor can be switched to 50% load to increase the cooling capacity, but not to full speed operation. Milder time period in the morning or afternoon: When the temperature begins to rise in the morning or afternoon, but has not yet reached the peak, the system only needs an appropriate amount of cooling. At this time, using 50% load can not only respond quickly to temperature changes, but also save energy. Transition adjustment stage: When the system is in the transition stage from low load to high load, 50% load can be temporarily used to balance demand and avoid temperature fluctuations caused by excessive load switching. Advantages: Compared with low load operation, 50% load can achieve temperature adjustment in a shorter time, which is suitable for medium demand. Moderate energy consumption: saves energy compared to 75% or 100% load, and also has a certain balance in ensuring the temperature adjustment speed.

[0134] For example, if the set temperature is 24° C. and the current ambient temperature is 27° C., the compressor can be operated at 50% load to gradually reduce the temperature in a more economical manner.

[0135] Specifically, the applicable scenario of the 75% load level (high load operation) is when the difference between the ambient temperature and the set temperature is between 4-6°C, the system needs to cool quickly, and the compressor can switch to 75% load to enhance the cooling capacity. During the period of the highest temperature during the day or in scenarios with high frequency of use (such as peak hours in office buildings and production workshops), the ambient temperature rises rapidly. At this time, the system needs a stronger cooling capacity to cope with the rise in external temperature. Or when the user wants to reach the set temperature quickly, the system will enter the 75% load level in a short time to quickly lower the temperature. Advantages: 75% load can significantly reduce the ambient temperature in a shorter period of time, which is suitable for high-demand scenarios. Compared with 100% load, 75% load can provide sufficient cooling effect while avoiding the high energy consumption caused by the system running at maximum load for a long time.

[0136] For example, if the set temperature is 24° C., and the current ambient temperature is 30° C., and the system is running at 75% load, the temperature can be lowered to the target level relatively quickly.

[0137] Specifically, the applicable scenario of the 100% load level (full load operation) is when the ambient temperature is much higher than the set temperature (for example, in hot summer weather, the ambient temperature is as high as 35°C or above), the system needs to work at full capacity to quickly cool down, and the compressor will switch to 100% load operation. In very hot environments (such as the noon period during the peak summer season), the system needs to run at full load to meet the extremely high cooling load demand. When the system is just started or restarted from a shutdown state, the ambient temperature difference is large. At this time, the compressor will briefly run at 100% load and quickly restore the set temperature. Advantages: At 100% load, the compressor can provide the maximum cooling capacity of the system, which is suitable for hot weather and emergency cooling needs. Quickly restore a comfortable environment: For sudden changes in ambient temperature, full load operation can restore comfortable indoor temperature in the shortest time.

[0138] For example, if the set temperature is 24°C and the current ambient temperature is as high as 32°C or above, the system will start 100% load operation to reduce the temperature to the target value as quickly as possible.

[0139] In addition, the switching of compressors between different load levels usually depends on the system's control algorithms, such as PID control, fuzzy logic control, etc. These algorithms dynamically adjust the load by monitoring the following key parameters in real time: Ambient temperature: The difference between the ambient temperature and the set temperature is an important basis for load adjustment. As the ambient temperature changes, the load level is dynamically adjusted to ensure that energy consumption is minimized while maintaining the cooling effect. Set temperature change: When the user adjusts the set temperature, the system will quickly adjust the load according to the new temperature difference. For example, when the user adjusts the set temperature from 28°C to 24°C, the system will automatically increase the load to accelerate cooling. Time and usage mode: The system can automatically adjust the load according to different time periods or usage modes set by the user. For example, during the day when the temperature is higher, the system will prioritize 75% or 100% load operation, and automatically switch to 25% or 50% load operation at night.

[0140] For example, 25% load: suitable for small temperature difference, maintaining temperature or low usage period, with the lowest energy consumption. 50% load: suitable for medium temperature difference or mild environment, balancing energy consumption and cooling effect. 75% load: suitable for large temperature difference or peak period, fast response to temperature change. 100% load: suitable for extreme high temperature or rapid cooling demand, providing maximum cooling capacity. Through dynamic adjustment of load, the system can maintain efficient operation under different temperature conditions, while optimizing energy consumption and meeting the comfort needs of users.

[0141] In an exemplary embodiment, the system further includes an oil separator; the compressor further includes an oil return control valve; the load level includes a load level of 25%, a load level of 50%, a load level of 75% and a load level of 100%; and the method further includes the following steps:

[0142] When the compressor is started for the first preset time, the load level of the compressor is below 50% and the refrigerant flow is less than the first preset flow, the compressor is controlled to enter the oil return mode; the oil return mode includes: controlling the oil return control valve to open, and controlling the expansion valve opening based on the refrigerant flow.

[0143] Specifically, the oil return mode refers to the process of the compressor recovering lubricating oil in the refrigeration system. During the operation of the compressor, the lubricating oil is mixed with the refrigerant and circulates in the system with the refrigerant. When operating at low load or partial load, the refrigerant flow rate in the system decreases, and the lubricating oil in the oil-gas mixture may be retained in the system pipes or evaporator and other components, which may cause the compressor to lack lubrication, thereby affecting its operating efficiency and life; therefore, the main goal of the oil return mode is to ensure that the lubricating oil returns to the compressor in a timely manner to avoid oil being retained in other parts of the system.

[0144] Specifically, when it is detected that the system is in a low-load state, the oil return control valve opens, and the lubricating oil flows back from other system components (such as evaporator, condenser, etc.) to the oil chamber of the compressor through the oil return pipe, ensuring that the compressor can still be fully lubricated under low load.

[0145] In an exemplary embodiment, the air conditioning system may further include an oil separator, which is a device used to separate refrigerant and lubricating oil in the refrigeration system. The lubricating oil enters the high-pressure gaseous refrigerant from the compressor, and the oil separator can separate the lubricating oil from the high-temperature and high-pressure gaseous refrigerant and return the lubricating oil to the crankcase of the compressor, while the separated gaseous refrigerant continues to flow to the condenser and other components.

[0146] For example, the oil return mode of some systems returns oil through the suction pipe of the compressor, that is, the lubricating oil is brought back to the compressor through the refrigerant reflux. When running at partial load, the refrigerant flow rate decreases, and the mixed lubricating oil may be retained in the evaporator or pipeline. The oil return mode increases the refrigerant flow rate by adjusting the expansion valve opening and system pressure, and brings the retained lubricating oil back to the compressor.

[0147] For example, in oil return mode, the electronic expansion valve will be precisely adjusted according to the refrigerant flow and load status. The opening of the expansion valve needs to balance the refrigerant flow and pressure to ensure that the lubricating oil will not be retained in other parts of the system due to too low a flow rate. Too large or too small an expansion valve opening will result in inappropriate refrigerant flow, thus affecting the oil return effect.

[0148] In an exemplary embodiment, the specific working process of the oil return mode includes: the system monitors the refrigerant flow, compressor load and oil separator status in real time through sensors; when the system detects low load operation, the oil return control valve opens, and the lubricating oil in the oil separator begins to flow back to the compressor through the oil return pipe or the suction pipe.

[0149] On the other hand, in the oil return mode, when the system load is low (such as 25% load level), the opening of the expansion valve needs to be appropriately reduced to increase the pressure difference and flow rate in the system, thereby accelerating the return of the lubricating oil; when the system load is high (such as above 50% load level), the opening of the expansion valve can be slightly larger to ensure the appropriate refrigerant flow, thereby maintaining the oil return effect. When the system is in a low load or partial load state, the refrigerant flow is small and the oil return effect becomes worse. At this time, the system needs to start the oil return mode. When the load of the compressor is lower than a preset value (such as 25% or 50% load), the oil return mode will be automatically activated to ensure that there is still enough lubricating oil return when the compressor is running at low load. The oil separator will detect the effect of oil and gas separation to ensure that the separated lubricating oil can return to the compressor through the oil return pipeline or other means.

[0150] In an exemplary embodiment, the system further includes a water pump; and the method further includes the following steps:

[0151] In response to the current ambient temperature being less than a preset temperature, the water pump is controlled to run for a second preset time and a prompt to enter an antifreeze mode is output, wherein the antifreeze mode prompt is used to instruct the user to check whether a pipe connected to the water pump is frozen.

[0152] Specifically, the air-conditioning system provided in the present application may be a water circulation air-conditioning system. In winter or low-temperature environments, the system introduces an anti-freeze protection mechanism to ensure that the air-conditioning system will not be damaged by freezing due to low temperatures.

[0153] On the other hand, the continuous operation of the water pump ensures that the water channel is unobstructed, and during the operation of the water pump, the pipeline is checked to see if it is frozen to prevent the pipeline from rupturing due to the water pump pressure.

[0154] For example, the system monitors the outlet and return water temperatures of the air conditioner and water source in real time through water temperature sensors. When the temperature is lower than the set antifreeze protection value, the system automatically starts the air conditioner pump and water source pump to circulate the water flow to prevent the pipes from freezing. When the ambient temperature probe detects that the temperature is lower than a certain threshold, the system starts the antifreeze protection mode and runs the water pump regularly to ensure that the water flow in the pipes will not freeze even in non-cooling and heating modes.

[0155] It should be understood that, although the steps in the flowcharts involved in the above embodiments are displayed in sequence according to the indication of the arrows, these steps are not necessarily executed in sequence according to the order indicated by the arrows. Unless there is a clear explanation in this article, the execution of these steps is not strictly limited in order, and these steps can be executed in other orders. Moreover, at least a part of the steps in the flowcharts involved in the above embodiments may include multiple steps or multiple stages, and these steps or stages are not necessarily executed at the same time, but can be executed at different times, and the execution order of these steps or stages is not necessarily carried out in sequence, but can be executed in turn or alternately with other steps or at least a part of the steps or stages in other steps.

[0156] In a third aspect, the present application further provides a computer device, including a memory and a processor, wherein the memory stores a computer program, and the processor implements the steps of the remote update method of the above application when executing the computer program.

[0157] In a fourth aspect, the present application also provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the steps of the automatic deployment and recovery method of the buoy as described above.

[0158] In a fifth aspect, the present application provides a computer program product, comprising a computer program, which, when executed by a processor, implements the steps of the automatic deployment and recovery method of the buoy as described above.

[0159] Those skilled in the art can understand that all or part of the processes in the above-mentioned embodiment methods can be completed by instructing the relevant hardware through a computer program, and the computer program can be stored in a non-volatile computer-readable storage medium. When the computer program is executed, it can include the processes of the embodiments of the above-mentioned methods. Among them, any reference to the memory, database or other medium used in the embodiments provided in the present application can include at least one of non-volatile and volatile memory. Non-volatile memory can include read-only memory (ROM), magnetic tape, floppy disk, flash memory, optical memory, high-density embedded non-volatile memory, resistive random access memory (ReRAM), magnetoresistive random access memory (MRAM), ferroelectric random access memory (FRAM), phase change memory (PCM), graphene memory, etc. Volatile memory can include random access memory (RAM) or external cache memory, etc. As an illustration and not limitation, RAM can be in various forms, such as static random access memory (SRAM) or dynamic random access memory (DRAM). The database involved in each embodiment provided in this application may include at least one of a relational database and a non-relational database. Non-relational databases may include distributed databases based on blockchains, etc., but are not limited to this. The processor involved in each embodiment provided in this application may be a general-purpose processor, a central processing unit, a graphics processor, a digital signal processor, a programmable logic device, a data processing logic device based on quantum computing, etc., but are not limited to this.

[0160] The technical features of the above embodiments may be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0161] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the present application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the present application shall be subject to the attached claims.

Claims

1. A heat recovery air conditioning system, characterized in that: The system includes a compressor, a condenser, an expansion valve and an evaporator connected to a controller; the system also includes: a heat recovery component connected to the compressor, the condenser and the target pipeline to be heated, and used for performing heat exchange with the target pipeline; A first temperature collection device, disposed adjacent to the evaporator, for collecting the current ambient temperature; A second temperature collection device is provided at the outlet of the evaporator and is used to collect the actual superheat at the outlet of the evaporator; The controller is connected to the first temperature acquisition device, the second temperature acquisition device and the hot water switch of the target pipeline respectively, and is used to control the expansion valve to operate according to the first control strategy, and to operate according to the second control strategy when the hot water switch is turned on; The first control strategy includes: based on the current ambient temperature and the set temperature, calculating the first refrigerant flow required to adjust the current ambient temperature to the set temperature in a preset time; adjusting the expansion valve once according to the first refrigerant flow, and monitoring the actual superheat at the evaporator outlet; in response to a difference between the actual superheat and the preset superheat interval, adjusting the expansion valve twice with the goal of eliminating the difference and minimizing the adjustment amount of the first refrigerant flow; The second control strategy includes: calling pre-stored historical data; the historical data includes the refrigerant flow corresponding to each set temperature adjusted to each ambient temperature when the hot water switch is turned on; determining the second refrigerant flow currently required based on the current ambient temperature, the set temperature and the historical data; and adjusting the expansion valve three times according to the second refrigerant flow.

2. The system according to claim 1, characterized in that The heat recovery component is a double-effect heat recovery component including a first heat recovery device and a second heat recovery device; the first heat recovery device is connected to the exhaust port of the compressor; and the second heat recovery device is connected to the condenser.

3. The system according to claim 1, characterized in that The compressor is a variable frequency compressor, and the expansion valve is a variable frequency controlled expansion valve; the frequency control of the expansion valve corresponds to the frequency of the variable frequency compressor.

4. A heat recovery air conditioning system control method, characterized in that: The method comprises: Controlling the expansion valve to operate according to the first control strategy, and when the hot water switch is turned on, operating according to the second control strategy; The first control strategy includes: based on the current ambient temperature and the set temperature, calculating the first refrigerant flow required to adjust the current ambient temperature to the set temperature in a preset time; adjusting the expansion valve once according to the first refrigerant flow, and monitoring the actual superheat at the evaporator outlet; in response to a difference between the actual superheat and the preset superheat interval, adjusting the expansion valve twice with the goal of eliminating the difference and minimizing the adjustment amount of the first refrigerant flow; The second control strategy includes: calling pre-stored historical data; the historical data includes the refrigerant flow corresponding to each set temperature adjusted to each ambient temperature when the hot water switch is turned on; determining the second refrigerant flow currently required based on the current ambient temperature, the set temperature and the historical data; and adjusting the expansion valve three times according to the second refrigerant flow.

5. The method according to claim 4, characterized in that The method further comprises: Controlling the operation of the compressor based on the first refrigerant flow required, and determining a plurality of operating states during the operation of the compressor; the operating states include a start-stop process state and a load state; The corresponding control of the expansion valve opening according to the operating state includes: in response to the compressor being in the start-stop process, controlling the expansion valve to enter a first opening; in response to the compressor being in a load state, controlling the expansion valve to enter a second opening; the second opening includes the openings of multiple valve steps corresponding to the primary adjustment, the secondary adjustment and the tertiary adjustment of the expansion valve; the opening of each valve step is valve step controlled based on a PID control algorithm; the first opening is smaller than the second opening.

6. The method according to claim 4, characterized in that The method further comprises: In response to the current ambient temperature changing, the target temperature is calculated based on the following formula: Target temperature = set temperature + (starting ambient temperature - current ambient temperature) × preset compensation coefficient.

7. The method according to claim 6, characterized in that The method further comprises: Acquire the working environment and user needs, and set the preset temperature compensation coefficients of multiple coefficient levels; the working environment includes an extreme environment with a temperature difference greater than a preset temperature difference, and a normal environment with a temperature difference less than the preset temperature difference; the user needs include a control mode of rapid control with a control rate greater than a first preset rate, and a control mode of comfortable control with a control rate less than the first preset rate; Establishing correlations between each control mode of the comfortable control in the extreme environment, the comfortable control in the normal environment, the rapid control in the extreme environment and the rapid control in the normal environment and each coefficient level; In response to a change in the current ambient temperature, the temperature compensation coefficient of the corresponding level of the control mode is determined according to the current working environment and the user demand.

8. The method according to claim 7, characterized in that The method further comprises: Divide the compressor load into multiple load levels from high to low, and set multiple temperature difference intervals; Establishing a mapping relationship between the temperature difference interval and each of the load levels in order from high to low according to the temperature difference in the temperature difference interval; Based on the temperature adjustment difference between the current ambient temperature and the set temperature, determining the temperature difference interval satisfied by the temperature adjustment difference, and selecting the load level of the compressor based on the mapping relationship; The compressor operation is controlled based on the selected load level.

9. The method according to claim 8, characterized in that The system further includes an oil separator; the compressor further includes an oil return control valve; the load level includes a load level of 25%, a load level of 50%, a load level of 75% and a load level of 100%; the method further includes: When the compressor is started for a first preset time, the load level of the compressor is below 50% and the refrigerant flow rate is less than a first preset flow rate, the compressor is controlled to enter an oil return mode; the oil return mode includes: controlling the oil return control valve to open, and controlling the expansion valve opening based on the refrigerant flow rate.

10. The method according to claim 4, characterized in that The system further comprises a water pump; and the method further comprises: In response to the current ambient temperature being less than a preset temperature, the water pump is controlled to run for a second preset time and a prompt to enter an antifreeze mode is output, wherein the antifreeze mode prompt is used to instruct a user to check whether a pipe connected to the water pump is frozen.

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