Control method and device of air source heat pump system and air source heat pump system

Abstract

The invention relates to the technical field of heat pump operation control, and discloses a control method and device of an air source heat pump system and the air source heat pump system.The method comprises the steps that a three-parameter linkage model with the frequency of a compressor, the number of revolutions of a draught fan and the speed regulation of a water pump as regulation and control objects is established with the heating capacity / refrigerating capacity of the heat pump system matched with a tail end load as the core; according to a preset temperature threshold value, the environment temperature is divided into different temperature zones, and according to the user side supply and return water temperature difference, the three parameter intervals of the different temperature zones and the priority adjusting strategy are determined; and operating parameters of the system are collected, and the three parameters are subjected to collaborative linkage adjustment according to an adjustment priority strategy, so that the heat exchange performance of the system is ensured, and meanwhile, the conveying energy consumption is optimized. According to the method, through three-parameter accurate cooperation and temperature zone adaptive regulation and control, the heat exchange performance and the tail end requirement are guaranteed, meanwhile, the conveying energy consumption of the draught fan and the water pump is optimized, the running stability and adaptability of the system under all working conditions are improved, and the method is suitable for air source heat pump application scenes in various climatic environments.

Description

Technical Field

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

[0002] Air source heat pump systems are widely used in building heating and cooling due to their advantages such as energy saving, environmental protection, and convenient installation. However, traditional air source heat pump systems generally adopt a "high flow rate and small temperature difference" operating mode, which has many technical pain points and seriously restricts the system's energy efficiency and operational stability.

[0003] First, the energy consumption of traditional systems remains high. In the "high flow rate and small temperature difference" mode, distribution equipment such as fans and pumps need to maintain high load operation to ensure fluid delivery, resulting in their energy consumption accounting for 30%-40% of the total system energy consumption, highlighting the problem of energy waste. At the same time, the system lacks a precise matching mechanism between compressor frequency, fan speed, and pump flow rate. The core power output is disconnected from the distribution capacity and heat exchange requirements, often resulting in parameter mismatches such as "increased compressor frequency but insufficient fan heat exchange" and "excessive pump flow rate but low terminal load," further aggravating energy waste.

[0004] Secondly, heat exchange efficiency is not fully utilized. Traditional systems often control the compressor, fan, and water pump independently, without establishing a coordinated linkage logic among them. This results in the fluid parameters (temperature and flow rate) on both sides of the heat exchanger not being able to match the optimal heat exchange range. For example, after adjusting the compressor output power, the fan speed is not optimized synchronously, causing the evaporator / condenser heat exchange temperature difference to deviate from the ideal range; the water pump flow rate is mismatched with the terminal load, causing excessive fluctuations in the supply and return water temperature difference on the user side, ultimately leading to a decrease in heat exchange efficiency and affecting the terminal heating / cooling effect.

[0005] Furthermore, traditional control algorithms often employ single-parameter adjustment logic, independently controlling only a single parameter such as compressor frequency or water pump flow rate, making it difficult to simultaneously achieve the dual goals of "energy consumption optimization" and "performance assurance." These algorithms fail to consider the coupled effects of multiple parameters such as ambient temperature, heat exchange status, and terminal load, resulting in delayed adjustment responses, which can easily lead to system fluctuations and further reduce the overall operational efficiency of the system. Summary of the Invention

[0006] To address the technical problems of parameter mismatch, high energy consumption, low heat exchange efficiency, and poor adaptability in traditional air source heat pump systems, this invention provides a control method, device, and system for an air source heat pump system, which optimizes system energy consumption while ensuring the heating / cooling needs and heat exchange performance at the terminal.

[0007] In a first aspect, the present invention provides a control method for an air source heat pump system, comprising: With the matching of the heating / cooling capacity of the heat pump system with the terminal load as the core, a three-parameter linkage model is established with compressor frequency, fan speed and water pump speed as the control objects. The ambient temperature is divided into different temperature zones based on the preset temperature threshold, and the parameter range and adjustment priority strategy for compressor frequency, fan speed and water pump speed in different temperature zones are determined based on the temperature difference between the supply and return water on the user side. The system collects operating parameters and adjusts the compressor frequency, fan speed, and water pump speed in a coordinated manner according to the adjustment priority strategy, so as to optimize the energy consumption of the system while ensuring heat exchange performance.

[0008] The control method for an air source heat pump system provided in this invention constructs a three-parameter linkage model with terminal load matching as the core, and combines temperature zone division to formulate differentiated parameter ranges and adjustment priorities to achieve coordinated linkage of the three parameters. This effectively solves the core pain points of traditional systems, such as parameter mismatch, high proportion of energy consumption in transmission, and insufficient heat exchange efficiency. While accurately ensuring heat exchange performance and terminal heating / cooling needs, it significantly optimizes the energy consumption of fans and water pumps, significantly improves the system's adaptability and operational stability under different ambient temperatures, and is suitable for all actual application scenarios.

[0009] In one optional implementation, the basic matching relationship of the three-parameter linkage model is: Q = k1 × f = k2 × n = k3 × v Where Q is the heating / cooling capacity, k1, k2, and k3 are equipment characteristic coefficients derived from the core principle of the equipment, f is the compressor frequency, n is the fan speed, and v is the water pump flow rate.

[0010] This invention establishes a clear quantitative relationship between heating / cooling capacity and three parameters, and the equipment characteristic coefficients are derived based on the core principles of the equipment, closely matching actual operating characteristics. This provides precise mathematical support for the coordinated operation of the three parameters, avoiding parameter disconnection caused by blind adjustments, ensuring dynamic balance in heat exchange and distribution, significantly improving the accuracy and reliability of control, while simplifying control logic design and reducing the difficulty and cost of commissioning during engineering implementation.

[0011] In one optional implementation, the step of dividing the ambient temperature into different temperature zones according to a preset temperature threshold includes: a high-temperature zone, a normal-temperature zone, a low-temperature zone, and an extremely cold zone, wherein the priority adjustment strategy includes: High-temperature zone: Prioritize adjusting water pump speed and fan speed, then optimize compressor frequency; Normal temperature range: Balance the compressor frequency, fan speed and water pump speed; Low temperature zone: Prioritize adjusting the compressor frequency and fan speed, then adjust the water pump speed; In extremely cold regions: prioritize ensuring compressor frequency, then adjust fan speed, and finally adjust water pump speed.

[0012] This invention divides ambient temperature into four temperature zones and assigns corresponding differentiated adjustment priorities. In high-temperature zones, priority is given to optimizing energy consumption for transmission and distribution; in low-temperature / extremely cold zones, priority is given to ensuring energy supply and frost prevention; and in normal-temperature zones, balanced adjustment is implemented. This precisely adapts to the core needs of different temperature zones, completely resolving problems such as energy waste at high temperatures, frequent frost formation at low temperatures, and insufficient energy supply in extreme cold caused by traditional "one-size-fits-all" adjustments. This significantly improves the system's operational reliability, adaptability, and user experience across all temperature zones.

[0013] In one optional implementation, the coordinated adjustment is based on a preset proportional relationship between the compressor frequency, fan speed and water pump speed, wherein the proportional relationship is: for every 10% change in compressor frequency, the fan speed changes synchronously by 8%-10% and the water pump flow rate changes synchronously by 8%-10%.

[0014] This invention achieves coordinated regulation based on a fixed proportional relationship: "for every 10% change in compressor frequency, the fan speed and water pump flow rate change synchronously by 8%-10%." This ensures precise matching of the adjustment ranges of the three parameters. It effectively avoids problems such as heat exchange imbalance and system fluctuations caused by fluctuations in a single parameter, ensuring a stable and controllable adjustment process. This further consolidates the balance between heat exchange performance and energy consumption optimization, improves the predictability of control actions and the stability of system operation, and reduces performance fluctuations during operating condition switching.

[0015] In one optional implementation, the coordinated adjustment is achieved through an adaptive control algorithm with parameter coupling weight factors. The weight factors are dynamically configured according to different temperature zones. The higher the temperature zone, the greater the weight of the water pump speed regulation. The lower the temperature zone, the greater the weight of the compressor frequency. The input parameters of the adaptive control algorithm include ambient temperature and humidity, evaporator / condenser temperature, user-side supply and return water temperature difference, and real-time values ​​of the three parameters. The output parameters include compressor frequency regulation, fan speed regulation, and water pump speed regulation.

[0016] This invention achieves regulation through an adaptive control algorithm that dynamically configures parameters coupled with weighting factors. Higher temperature zones have a greater weighting on pump speed regulation, while lower temperature zones have a greater weighting on compressor frequency. Furthermore, it incorporates multi-dimensional operating parameters. This enhances the targetedness and accuracy of the three-parameter linkage, enabling rapid response to dynamic changes in the environment, heat exchange, and terminal load. It avoids ineffective regulation and energy waste, maximizing energy savings while ensuring system performance meets standards, and improving the system's automation level and adaptability to complex operating conditions.

[0017] In an optional implementation, when the temperature zone is the low-temperature zone or the extremely cold zone, a frost prevention control strategy is also included: When the preset frosting conditions are detected, the compressor frequency and the fan speed are increased first, and the change in the water pump speed is maintained or limited during defrosting.

[0018] This invention incorporates a frost prevention control strategy for low-temperature / extremely cold regions. When frost forms, it prioritizes frequency and speed increases for defrosting and stabilizes the water pump speed. This precisely addresses issues such as heat exchange attenuation and power supply interruption caused by evaporator frost in low-temperature environments, shortens defrosting time, reduces energy loss during defrosting, ensures the continuity and stability of heating in low-temperature / extremely cold regions, and significantly improves the system's operational reliability and practical value in cold areas.

[0019] In one optional implementation, the method further includes an exception handling process: When the compressor discharge temperature is higher than the preset temperature or the compressor frequency is higher than the preset frequency threshold, the frequency is reduced first. If the problem is not resolved, the fan speed and water pump speed are increased to the preset range. If the problem is still abnormal, an alarm is triggered. When the fan speed is lower than the preset speed threshold, the compressor frequency is increased and the electric auxiliary heating is started; When the water pump flow rate is zero, the compressor frequency and fan speed are reduced within a first preset time, and a shutdown alarm is triggered after a second preset time.

[0020] This invention provides a tiered and progressive fault handling process covering key abnormal scenarios for three core equipment types: compressors, fans, and water pumps. It can quickly respond to faults such as exhaust overheating, abnormal frequency, excessively low RPM, and water pump interruption, promptly curbing the escalation of faults through targeted adjustments, effectively protecting equipment safety, reducing unplanned downtime losses, and maximizing the protection of end-point power supply, thereby significantly improving the system's operational safety, fault tolerance, and service life. In a second aspect, the present invention provides a control device for an air source heat pump system, the device comprising: The three-parameter linkage model construction module is used to establish a three-parameter linkage model with compressor frequency, fan speed and water pump speed as the control objects, with the matching of the heating / cooling capacity of the heat pump system with the terminal load as the core. The temperature zone division and configuration module is used to divide the ambient temperature into different temperature zones according to the preset temperature threshold, and to determine the parameter range and adjustment priority strategy of compressor frequency, fan speed and water pump speed for different temperature zones according to the temperature difference between the supply and return water on the user side. The three-parameter linkage control module is used to collect system operating parameters and, based on the adjustment priority strategy, coordinate and adjust the compressor frequency, the fan speed, and the water pump speed to optimize energy consumption while ensuring heat exchange performance.

[0021] Thirdly, the present invention provides an air source heat pump system, comprising: a memory and a processor, wherein the memory and the processor are communicatively connected to each other, the memory stores computer instructions, and the processor executes the computer instructions to perform the control method of the air source heat pump system of the first aspect or any corresponding embodiment described above.

[0022] Fourthly, the present invention provides a computer-readable storage medium storing computer instructions for causing a computer to execute the control method of the air source heat pump system of the first aspect or any corresponding embodiment described above.

[0023] Fifthly, the present invention provides a computer program product, including computer instructions for causing a computer to execute the control method of the air source heat pump system of the first aspect or any corresponding embodiment described above. Attached Figure Description

[0024] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific 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 from these drawings without creative effort.

[0025] Figure 1 This is a schematic flowchart of a control method for an air source heat pump system according to an embodiment of the present invention; Figure 2 This is a structural block diagram of the control device of an air source heat pump device according to an embodiment of the present invention; Figure 3 This is a schematic diagram of the hardware structure of an air source heat pump system according to an embodiment of the present invention. Detailed Implementation

[0026] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0027] It is understood that before using the technical solutions disclosed in the various embodiments of the present invention, users should be informed of the types, scope of use, and usage scenarios of the personal information involved in the present invention and their authorization should be obtained in accordance with relevant laws and regulations through appropriate means.

[0028] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0029] Traditional control algorithms often employ single-parameter adjustment logic, independently controlling only a single parameter such as compressor frequency or water pump flow rate. This makes it difficult to simultaneously achieve the dual goals of "energy consumption optimization" and "performance assurance." Furthermore, these algorithms fail to consider the coupled effects of multiple parameters, such as ambient temperature, heat exchange status, and terminal load, resulting in delayed adjustment responses, which can easily lead to system fluctuations and further reduce the overall operational efficiency of the system.

[0030] This invention provides an embodiment of a control method for an air source heat pump system, which can achieve coordinated linkage of three parameters: compressor frequency, fan speed, and water pump speed regulation, and adapt to the differentiated needs of different temperature zones. This method solves the technical problems of traditional air source heat pump systems, such as parameter mismatch, high energy consumption, low heat exchange efficiency, and poor adaptability to operating conditions. It optimizes system energy consumption while ensuring the heating / cooling needs and heat exchange performance at the terminal.

[0031] It should be noted that the steps shown in the flowchart in the accompanying drawings can be executed in a computer system such as a set of computer-executable instructions, and although a logical order is shown in the flowchart, in some cases the steps shown or described may be executed in a different order than that shown here. Figure 1 This is a flowchart of a control method for an air source heat pump system according to an embodiment of the present invention, such as... Figure 1 As shown, the process includes the following steps: Step S1: With the matching of the heating / cooling capacity of the heat pump system with the terminal load as the core, establish a three-parameter linkage model with compressor frequency, fan speed and water pump speed as the control objects.

[0032] Specifically, the basic matching relationship of the three-parameter linkage model provided in this embodiment of the invention is as follows: Q = k1 × f = k2 × n = k3 × v Where Q represents heating / cooling capacity, k1, k2, and k3 are equipment characteristic coefficients derived from the core principles of the equipment, f is the compressor frequency, n is the fan speed, and v is the water pump flow rate. In one example, compressor k1 can be estimated by combining compressor displacement, intake / exhaust parameters, and energy efficiency formulas; fan k2 is calculated based on the similarity law of fluid mechanics (airflow is proportional to speed), combined with the fan's rated airflow and speed; and water pump k3 is derived from the similarity law of water pumps (flow rate is proportional to speed), based on rated flow rate and rated speed.

[0033] Traditional air source heat pump systems often suffer from problems such as insufficient heat exchange, frequent frosting, and system fluctuations due to the lack of clear quantitative correlation between the three parameters: compressor frequency increases but fan speed and water pump flow do not keep up, or distribution parameter adjustments are disconnected from core power output. This results in the aforementioned equation constraint, forcing the operating parameters of the compressor, fan, and water pump to change in synergy around the core objective of "matching heating / cooling capacity with terminal load," fundamentally avoiding the energy waste caused by the "large flow rate and small temperature difference" of traditional systems. Furthermore, k1, k2, and k3 are derived based on the core principles of the equipment (compressor displacement and energy efficiency formulas, fluid mechanics / pump similarity laws), ensuring that the quantitative relationship closely matches the actual operating characteristics of the equipment, rather than being empirically adapted, further improving the stability and reliability of system operation.

[0034] Step S2: Divide the ambient temperature into different temperature zones according to the preset temperature threshold, and determine the parameter range and adjustment priority strategy for compressor frequency, fan speed and water pump speed for different temperature zones according to the temperature difference between the supply and return water on the user side.

[0035] Specifically, this invention comprehensively covers the core requirements of different climate scenarios by dividing the temperature zone into multiple zones and matching them with dedicated parameter ranges and adjustment priorities. It clearly defines the parameter control boundaries and priority order for each temperature zone, ensuring that the three parameters work in a structured manner and preventing parameter mismatches caused by traditional "one-size-fits-all" adjustments. For example, in high-temperature zones, there is no need to excessively adjust the compressor, while in low-temperature zones, the core requirement of anti-frost is not ignored, ensuring heat exchange efficiency and terminal supply-demand balance, reducing system fluctuations during operating condition switching, and improving operational reliability.

[0036] In one embodiment, different ambient temperatures are divided into different temperature zones based on preset temperature thresholds, including: a high-temperature zone (>15℃), a normal-temperature zone (5℃~15℃), a low-temperature zone (-15℃~5℃), and an extremely cold zone (<-15℃). Statistical analysis shows that the supply and return water temperature difference at the user side is 10-12℃ for cooling and 13-15℃ for heating in the high-temperature zone, 9-10℃ for cooling and 12-13℃ for heating in the normal-temperature zone, 12-14℃ for heating in the low-temperature zone, and 10-12℃ for heating in the extremely cold zone. The specific parameter ranges for each temperature zone are as follows: 1. High-temperature zone: The temperature difference between the supply and return water on the user side is 10-12℃ for cooling and 13-15℃ for heating. The compressor frequency is 40%-60% of the rated frequency (variable frequency range 15-60Hz), the fan speed is 30%-60% of the rated speed (corresponding to 30%-60% of the air volume), and the water pump speed is 40%-30% of the rated flow rate (permanent magnet synchronous variable frequency speed control, 20-30Hz). 2. Normal temperature zone: The temperature difference between the supply and return water on the user side is 9-10℃ for cooling and 12-13℃ for heating. The compressor frequency is 30%-70% of the rated frequency (variable frequency range 25-70Hz), the fan speed is 60%-70% of the rated speed (corresponding to 60%-70% of the air volume), and the water pump speed is 30%-60% of the rated flow rate (permanent magnet synchronous variable frequency speed control, 25-35Hz). 3. Low temperature zone: The temperature difference between the supply and return water on the user side is 12-14℃ for heating. The compressor frequency is 60%-80% of the rated frequency (vapor injection enthalpy enhancement mode, 30-80Hz), the fan speed is 60%-80% of the rated frequency (dynamic adjustment, increased to 80% when frosting), and the water pump speed is 30%-60% of the rated flow rate (increase the flow rate by 5% when using vapor injection enthalpy enhancement, permanent magnet synchronous frequency conversion speed regulation, 25-35Hz). 4. Extremely cold regions: The temperature difference between the supply and return water on the user side is 10-12℃ for heating, the compressor frequency is 80%-90% of the rated frequency (two-stage compression mode, 40-90Hz), the fan speed is 80%-90% of the rated frequency (corresponding to 80%-90% of the air volume), and the water pump speed is 60%-70% of the rated flow rate (permanent magnet synchronous frequency conversion speed regulation, 30-40Hz).

[0037] In this embodiment of the invention, the priority strategy corresponding to each temperature zone includes: High-temperature zone: Prioritize adjusting water pump speed and fan speed, then optimize compressor frequency; Normal temperature range: Balance the compressor frequency, fan speed and water pump speed; Low temperature zone: Prioritize adjusting the compressor frequency and fan speed, then adjust the water pump speed; In extremely cold regions: prioritize ensuring compressor frequency, then adjust fan speed, and finally adjust water pump speed.

[0038] This invention prioritizes the adjustment of water pumps and fans (transmission and distribution equipment) in high-temperature zones to minimize transmission energy consumption, meeting core energy-saving requirements. In low-temperature zones, it prioritizes the compressor and fans, specifically addressing heat exchange attenuation caused by frost and ensuring stable heating capacity. In extremely cold zones, it focuses on ensuring compressor frequency, coordinating with fan adjustment to avoid single-stage compressor overload and meet the essential energy supply needs under extreme low temperatures. In normal-temperature zones, it achieves a dynamic balance between performance and energy consumption, covering everyday usage scenarios. This priority strategy abandons the traditional fixed priority mode, dynamically adjusting the control focus based on ambient temperature, avoiding energy waste caused by excessive compressor adjustment in high-temperature zones or system fluctuations caused by neglecting anti-frost requirements in low-temperature zones. By clarifying the control logic through priority ranking, it ensures seamless linkage of the three parameters, guarantees heat exchanger efficiency and end-point supply-demand balance, and reduces performance fluctuations during operating condition switching.

[0039] Step S3: Collect system operating parameters and, based on the adjustment priority strategy, coordinate and adjust the compressor frequency, the fan speed, and the water pump speed to optimize energy consumption while ensuring heat exchange performance.

[0040] In one embodiment, the coordinated adjustment in this invention is based on a preset proportional relationship between compressor frequency, fan speed, and water pump speed. The proportional relationship is as follows: for every 10% change in compressor frequency, fan speed changes synchronously by 8%-10%, and water pump flow rate changes synchronously by 8%-10%. This quantified ratio provides a clear execution standard for the three-parameter linkage, making the adjustment actions predictable and controllable, avoiding system oscillations caused by sudden changes in a single parameter. For example, when the compressor frequency is increased, the fan and water pump synchronously follow suit, improving heat exchange and distribution capabilities, reducing performance fluctuations during operating condition switching, ensuring stable supply and return water temperature differences at the terminal, and improving the user experience.

[0041] Taking the high-temperature zone (energy saving priority) as an example, maintain 40%-60% of the rated frequency (15-60Hz). The linkage logic is: for every 10Hz decrease in frequency, the water pump speed decreases by 5Hz (flow rate decreases by 8%) and the fan speed decreases by 8% (air volume decreases by 8%), ensuring that the coefficient of performance (COP) is ≥3.6.

[0042] When the temperature zone is a low temperature zone or an extremely cold zone, it also includes a frost prevention control strategy: when the preset frost conditions are detected, the compressor frequency and the fan speed are increased first, and the water pump speed is maintained or limited during defrosting.

[0043] Taking the low-temperature zone (frost prevention and power supply) as an example: activate jet enthalpy enhancement, frequency 60%-80% (30-80Hz). When the evaporator temperature is <-5℃, temporarily increase the frequency by 10Hz (about 15%) and the fan speed by 20% (rapid defrosting). Within 30 seconds after defrosting, return to the target value synchronously, and the water pump speed remains unchanged. The frost judgment condition is: when the evaporator temperature is <-5℃, defrosting is terminated by switching the four-way valve to switch to heating, 30 seconds after defrosting.

[0044] Taking extremely cold regions (supply priority) as an example: dual-stage compression mode at 80%-90% frequency (40-90Hz), linked fan speed at 80%-90%, water pump speed at 30-40Hz, and electric auxiliary heating at 15% of total heating capacity to avoid single-stage compression overload.

[0045] In another embodiment, the coordinated adjustment is achieved through an adaptive control algorithm (e.g., a PID algorithm) with parameter coupling weight factors. The weight factors are dynamically configured according to the temperature zone. The higher the temperature zone, the greater the weight of the water pump speed regulation, and the lower the temperature zone, the greater the weight factor of the compressor frequency. The input parameters of the adaptive control algorithm include ambient temperature and humidity, evaporator / condenser temperature, user-side supply and return water temperature, and real-time values ​​of the three parameters. The output parameters include compressor frequency regulation, fan speed regulation, and water pump speed regulation.

[0046] In one example, the percentage of parameter adjustment weighting factors for each temperature zone is: High-temperature zone: water pump speed adjusted to 40%, fan speed to 35%, compressor frequency to 25%; Low temperature zone: compressor frequency 40%, fan speed 35%, water pump speed 25%; Extremely cold regions: compressor frequency 30%, fan speed 30%, water pump speed 20%.

[0047] In this embodiment of the invention, the weighting factor is dynamically configured according to the temperature zone. In the high temperature zone, the focus is on water pump speed regulation (enhancing energy saving in transmission and distribution), while in the low temperature / extreme cold zone, the focus is on compressor frequency (ensuring power supply and preventing frost). This accurately matches the core requirements of different temperature zones, maximizing the reduction of transmission energy consumption in the high temperature zone and effectively preventing frost formation and heat output attenuation in the low temperature zone, thus achieving the optimal balance between performance and energy consumption under all operating conditions.

[0048] Example of a cooling scenario in a high-temperature area during summer (ambient temperature 35℃): 1. Temperature zone determination and weight configuration: The system detects an ambient temperature of 35℃ and determines it as a high temperature zone. The weight factors are dynamically configured as follows: water pump speed regulation 40%, fan speed 35%, compressor frequency 25% (energy saving priority). 2. Parameter Acquisition: The algorithm collects input parameters in real time: ambient temperature and humidity (35℃, 30% RH), evaporator temperature (12℃), condenser temperature (45℃), supply and return water temperature difference on the user side (11℃), and real-time values ​​of three parameters (compressor frequency 55Hz, fan speed 60% of rated speed, water pump speed regulation 28Hz); 3. Deviation assessment: The temperature difference between the supply and return water on the user side is 11℃, which is close to the upper limit of the cooling target (10-12℃), and energy consumption needs to be further optimized. 4. Calculation and output of adjustment: Based on the weight of the high temperature zone, the adjustment of water pump and fan is calculated first: water pump speed adjustment -2Hz (reduced to 26Hz), fan speed adjustment -5% (reduced to 55% of the rated ratio), compressor frequency adjustment -3Hz (reduced to 52Hz). 5. Execution and Feedback: After the equipment adjusts according to the instructions, the temperature difference on the user side is maintained at 11℃, and the total energy consumption of the system is reduced by 8%, achieving a balance between energy saving and performance.

[0049] The method provided in this embodiment of the invention also includes an exception handling process: 1. When the compressor exhaust temperature is higher than the preset temperature or the compressor frequency is higher than the preset frequency threshold, the frequency is reduced first. If the problem is not resolved, the fan speed and water pump speed are increased to the preset range. If the problem is still abnormal, an alarm is triggered. For example, if the compressor frequency is abnormal (exceeding 90Hz), the frequency is reduced to 80Hz, the fan speed is increased by 10%, and the water pump speed is increased by 5Hz. If the problem is still abnormal, an alarm is triggered.

[0050] 2. When the fan speed is lower than the preset value, increase the compressor frequency and start the electric auxiliary heating; for example, if the fan speed is out of control (below 300r / min), immediately increase the compressor frequency to 80Hz and start the electric auxiliary heating (10% power) to continuously ensure the heating output and avoid a sudden drop in indoor temperature until the fan speed returns to normal.

[0051] 3. When the water pump flow rate is zero, the compressor frequency and fan speed will be reduced within the first preset time, and a shutdown alarm will be triggered after the second preset time. Within 1 second, the compressor frequency will be reduced to 30Hz and the fan speed to 30%, and the machine will be stopped after 3 seconds, triggering an emergency stop alarm to prevent damage to the machine due to an emergency stop, as stopping the machine immediately when the speed is very high will cause damage.

[0052] This invention employs a tiered handling process for different abnormal scenarios. First, it attempts to restore normal operation by adjusting parameters, avoiding indiscriminate shutdowns or alarms, and maximizing end-point energy supply (e.g., starting electric auxiliary heating in case of fan failure). In extreme cases (water pump interruption), a "speed reduction + shutdown" mode is used to prevent mechanical damage to equipment from sudden high-speed stops and extend equipment lifespan. This abnormal handling process, tailored to the operating characteristics of heat pumps, addresses issues such as reduced heating capacity due to fan failure and soaring energy consumption caused by compressor overclocking. Furthermore, by defining specific parameter thresholds and time points, it ensures predictable and implementable abnormal handling, enhancing the system's reliability and stability under complex operating conditions.

[0053] This embodiment also provides a control device for an air source heat pump system, which is used to implement the above embodiments and preferred embodiments; details already described will not be repeated. As used below, the term "module" can refer to a combination of software and / or hardware that performs a predetermined function. Although the device described in the following embodiments is preferably implemented in software, hardware implementation, or a combination of software and hardware, is also possible and contemplated.

[0054] This embodiment provides a control device for an air source heat pump system, such as... Figure 2 As shown, it includes: The three-parameter linkage model construction module 21 is used to establish a three-parameter linkage model with compressor frequency, fan speed and water pump speed as the control objects, with the heat pump system's heating / cooling capacity matching the terminal load as the core. The temperature zone division and configuration module 22 is used to divide the ambient temperature into different temperature zones according to the preset temperature threshold, and to determine the parameter range and adjustment priority strategy of compressor frequency, fan speed and water pump speed for different temperature zones according to the temperature difference between the supply and return water on the user side. The three-parameter linkage control module 23 is used to collect system operating parameters and, based on the adjustment priority strategy, coordinate and adjust the compressor frequency, the fan speed and the water pump speed to optimize the energy consumption of the system while ensuring heat exchange performance.

[0055] In some optional implementations, the basic matching relationship of the three-parameter linkage model is as follows: Q = k1 × f = k2 × n = k3 × v Where Q is the heating / cooling capacity, k1, k2, and k3 are equipment characteristic coefficients derived from the core principle of the equipment, f is the compressor frequency, n is the fan speed, and v is the water pump flow rate.

[0056] In some optional implementations, the division of the ambient temperature into different temperature zones based on a preset temperature threshold includes: a high-temperature zone, a normal-temperature zone, a low-temperature zone, and an extremely cold zone, wherein the priority adjustment strategy includes: High-temperature zone: Prioritize adjusting water pump speed and fan speed, then optimize compressor frequency; Normal temperature range: Balance the compressor frequency, fan speed and water pump speed; Low temperature zone: Prioritize adjusting the compressor frequency and fan speed, then adjust the water pump speed; In extremely cold regions: prioritize ensuring compressor frequency, then adjust fan speed, and finally adjust water pump speed.

[0057] In some optional implementations, the coordinated linkage adjustment in the three-parameter linkage control module 23 is based on a preset proportional relationship between the compressor frequency, fan speed and water pump speed, wherein the proportional relationship is: for every 10% change in compressor frequency, the fan speed changes synchronously by 8%-10% and the water pump flow rate changes synchronously by 8%-10%.

[0058] In some optional implementations, the coordinated linkage adjustment of the three-parameter linkage control module 23 is achieved through an adaptive control algorithm with parameter coupling weight factors. The weight factors are dynamically configured according to different temperature zones. The higher the temperature zone, the greater the weight of the water pump speed regulation. The lower the temperature zone, the greater the weight of the compressor frequency. The input parameters of the adaptive control algorithm include ambient temperature and humidity, evaporator / condenser temperature, user-side supply and return water temperature difference, and real-time values ​​of the three parameters. The output parameters include compressor frequency adjustment, fan speed adjustment, and water pump speed regulation.

[0059] In some optional implementations, when the temperature zone is the low-temperature zone or the extremely cold zone, a frost prevention control strategy is also included: When the preset frosting conditions are detected, the compressor frequency and the fan speed are increased first, and the change in the water pump speed is maintained or limited during defrosting.

[0060] In some optional implementations, an exception handling module is also included, comprising: The compressor abnormality handling unit is used to first reduce the frequency when the compressor discharge temperature is higher than the preset temperature or the compressor frequency is higher than the preset frequency threshold. If the problem is not resolved, the fan speed and water pump speed are increased to the preset range. If the problem is still abnormal, an alarm is triggered. The fan malfunction handling unit is used to increase the compressor frequency and start the electric auxiliary heater when the fan speed is lower than the preset speed threshold. The water pump abnormality handling unit is used to reduce the compressor frequency and fan speed within a first preset time when the water pump flow is zero, and to trigger a shutdown alarm after a second preset time.

[0061] The control device for the air source heat pump system provided in this embodiment of the invention can execute the control method for the air source heat pump system provided in any embodiment of the invention, and has the corresponding functional modules and beneficial effects for executing the method. Further functional descriptions of the various modules and units described above are the same as in the corresponding embodiments described above, and will not be repeated here.

[0062] Figure 3 This is a schematic diagram of an air source heat pump system provided in an embodiment of the present invention.

[0063] The following is a detailed reference. Figure 3 This diagram illustrates a structural schematic suitable for implementing an air-source heat pump system according to an embodiment of the present invention. The air-source heat pump system may include a processor (e.g., a central processing unit, graphics processor, etc.) 301, which can perform various appropriate actions and processes based on a program stored in a read-only memory (ROM) 302 or a program loaded from memory 308 into random access memory (RAM) 303. The RAM 303 also stores various programs and data required for the operation of the air-source heat pump system. The processor 301, ROM 302, and RAM 303 are interconnected via a bus 304. An input / output (I / O) interface 305 is also connected to the bus 304.

[0064] Typically, the following devices can be connected to I / O interface 305: input devices 306 including, for example, touchscreens, touchpads, keyboards, mice, cameras, microphones, etc.; output devices 307 including, for example, liquid crystal displays (LCDs), speakers, etc.; memory devices 308 including, for example, magnetic tapes, hard disks, etc.; and communication devices 309. Communication device 309 allows the air source heat pump system to communicate wirelessly or wiredly with other devices to exchange data. Although Figure 3 An air source heat pump system with various devices is shown, but it should be understood that it is not required to implement or have all of the devices shown, and more or fewer devices may be implemented or have instead.

[0065] In particular, according to embodiments of the present invention, the processes described above with reference to the flowcharts can be implemented as computer software programs. For example, embodiments of the present invention include a computer program product comprising a computer program carried on a non-transitory computer-readable medium, the computer program containing program code for performing the methods shown in the flowcharts. In such embodiments, the computer program can be downloaded and installed from a network via a communication device 309, or installed from a memory 308, or installed from a ROM 302. When the computer program is executed by the processor 301, it performs the functions defined in the control method of the air source heat pump system of the embodiments of the present invention.

[0066] Figure 3The air source heat pump system shown is merely an example and should not be construed as limiting the functionality and scope of the embodiments of the present invention.

[0067] This invention also provides a computer-readable storage medium. The methods described above according to embodiments of the invention can be implemented in hardware or firmware, or implemented as computer code that can be recorded on a storage medium, or implemented as computer code downloaded via a network and originally stored on a remote storage medium or a non-transitory machine-readable storage medium and then stored on a local storage medium. Thus, the methods described herein can be processed by software stored on a storage medium using a general-purpose computer, a dedicated processor, or programmable or dedicated hardware. The storage medium can be a magnetic disk, optical disk, read-only memory, random access memory, flash memory, hard disk, or solid-state drive, etc.; further, the storage medium can also include combinations of the above types of memory. It is understood that computers, processors, microprocessor controllers, or programmable hardware include storage components capable of storing or receiving software or computer code. When the software or computer code is accessed and executed by the computer, processor, or hardware, the control method of the air source heat pump system shown in the above embodiments is implemented.

[0068] A portion of this invention can be applied as a computer program product, such as computer program instructions, which, when executed by a computer, can invoke or provide the methods and / or technical solutions according to the invention through the operation of the computer. Those skilled in the art will understand that the forms in which computer program instructions exist in a computer-readable medium include, but are not limited to, source files, executable files, installation package files, etc. Correspondingly, the ways in which computer program instructions are executed by a computer include, but are not limited to: the computer directly executing the instructions, or the computer compiling the instructions and then executing the corresponding compiled program, or the computer reading and executing the instructions, or the computer reading and installing the instructions and then executing the corresponding installed program. Here, the computer-readable medium can be any available computer-readable storage medium or communication medium accessible to a computer.

[0069] Although embodiments of the invention have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of the invention, and such modifications and variations all fall within the scope defined by the appended claims.

Claims

1. A control method for an air source heat pump system, characterized in that, include: With the matching of the heating / cooling capacity of the heat pump system with the terminal load as the core, a three-parameter linkage model is established with compressor frequency, fan speed and water pump speed as the control objects. The ambient temperature is divided into different temperature zones based on the preset temperature threshold, and the parameter range and adjustment priority strategy for compressor frequency, fan speed and water pump speed in different temperature zones are determined based on the temperature difference between the supply and return water on the user side. The system collects operating parameters and adjusts the compressor frequency, fan speed, and water pump speed in a coordinated manner according to the adjustment priority strategy, so as to optimize the energy consumption of the system while ensuring heat exchange performance.

2. The method according to claim 1, characterized in that, The basic matching relationship of the three-parameter linkage model is as follows: Q = k1 × f = k2 × n = k3 × v Where Q is the heating / cooling capacity, k1, k2, and k3 are equipment characteristic coefficients derived from the core principle of the equipment, f is the compressor frequency, n is the fan speed, and v is the water pump flow rate.

3. The method according to claim 1, characterized in that, The process of dividing the ambient temperature into different temperature zones based on a preset temperature threshold includes: a high-temperature zone, a normal-temperature zone, a low-temperature zone, and an extremely cold zone, wherein the priority adjustment strategy includes: High-temperature zone: Prioritize adjusting water pump speed and fan speed, then optimize compressor frequency; Normal temperature range: Balance the compressor frequency, fan speed and water pump speed; Low temperature zone: Prioritize adjusting the compressor frequency and fan speed, then adjust the water pump speed; In extremely cold regions: prioritize ensuring compressor frequency, then adjust fan speed, and finally adjust water pump speed.

4. The method according to any one of claims 1-3, characterized in that, The coordinated adjustment is based on a preset proportional relationship between the compressor frequency, fan speed, and water pump speed. The proportional relationship is as follows: for every 10% change in compressor frequency, the fan speed changes by 8%-10% and the water pump flow rate changes by 8%-10%.

5. The method according to any one of claims 1-3, characterized in that, The coordinated adjustment is achieved through an adaptive control algorithm with parameter coupling weight factors. The weight factors are dynamically configured according to different temperature zones. The higher the temperature zone, the greater the weight of the water pump speed regulation. The lower the temperature zone, the greater the weight of the compressor frequency. The input parameters of the adaptive control algorithm include ambient temperature and humidity, evaporator / condenser temperature, user-side supply and return water temperature difference, and real-time values ​​of the three parameters. The output parameters include compressor frequency regulation, fan speed regulation, and water pump speed regulation.

6. The method according to claim 3, characterized in that, When the temperature zone is the low temperature zone or the extremely cold zone, a frost prevention control strategy is also included: When the preset frosting conditions are detected, the compressor frequency and the fan speed are increased first, and the change in the water pump speed is maintained or limited during defrosting.

7. The method according to claim 1, characterized in that, It also includes exception handling procedures: When the compressor discharge temperature is higher than the preset temperature or the compressor frequency is higher than the preset frequency threshold, the frequency is reduced first. If the problem is not resolved, the fan speed and water pump speed are increased to the preset range. If the problem is still abnormal, an alarm is triggered. When the fan speed is lower than the preset speed threshold, the compressor frequency is increased and the electric auxiliary heating is started; When the water pump flow rate is zero, the compressor frequency and fan speed are reduced within a first preset time, and a shutdown alarm is triggered after a second preset time.

8. A control device for an air source heat pump system, characterized in that, include: The three-parameter linkage model construction module is used to establish a three-parameter linkage model with compressor frequency, fan speed and water pump speed as the control objects, with the matching of the heating / cooling capacity of the heat pump system with the terminal load as the core. The temperature zone division and configuration module is used to divide the ambient temperature into different temperature zones according to the preset temperature threshold, and to determine the parameter range and adjustment priority strategy of compressor frequency, fan speed and water pump speed for different temperature zones according to the temperature difference between the supply and return water on the user side. The three-parameter linkage control module is used to collect system operating parameters and, based on the adjustment priority strategy, coordinate and adjust the compressor frequency, the fan speed, and the water pump speed to optimize energy consumption while ensuring heat exchange performance.

9. An air source heat pump system, characterized in that, include: A memory and a processor are communicatively connected, the memory stores computer instructions, and the processor executes the computer instructions to perform the control method of the air source heat pump system according to any one of claims 1 to 6.

10. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores computer instructions for causing a computer to execute the control method of the air source heat pump system according to any one of claims 1 to 6.

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