Heat exchange device, air conditioning unit and control method of heat exchange device

Abstract

The application discloses a heat exchange device, an air conditioning unit and a control method of the heat exchange device. The heat exchange device comprises: a heat exchanger composed of multiple parallel heat exchange modules; multiple air baffle structures arranged on the windward side of the heat exchanger, wherein each air baffle structure comprises a limiting frame, at least two air guide fins arranged in the limiting frame, a rotating driving assembly for driving the air guide fins to rotate around an axis to adjust the air inlet angle, and an extension driving assembly for driving the air guide fins to move along the limiting frame to adjust the spacing between the air guide fins; and each heat exchange module is independently provided with a corresponding air baffle structure. The heat exchanger is divided into multiple parallel modules, and the air baffle structure with adjustable air guide fin angle and spacing is arranged, and the self-adaptive control is performed in combination with a detection assembly and a controller, so that the accurate matching of air volume of each module is realized, the heat exchange uniformity is effectively improved, the frost risk is significantly reduced, the system energy efficiency is improved, and the energy-saving effect is realized.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and in particular to heat exchange devices, air conditioning units, and control methods for heat exchange devices. Background Technology

[0002] In systems such as air source heat pumps, the heat exchanger, as a core heat exchange component, directly affects the system's energy efficiency. Taking a common finned tube heat exchanger as an example, it typically uses an axial flow fan for forced convection heat exchange. Due to the influence of fan layout and installation position, the wind speed on the windward side of the heat exchanger often exhibits a significant non-uniform distribution, specifically a gradient difference with high wind speed at the top and low wind speed at the bottom. This uneven wind speed distribution leads to excessive refrigerant superheat and a high proportion of gaseous refrigerant in high-wind-speed areas, thereby reducing heat exchange efficiency; while low-wind-speed areas are prone to insufficient superheat, which not only creates heat exchange dead zones but may also lead to the risk of liquid slugging caused by liquid refrigerant backflow. In addition, uneven wind speed also leads to uneven frost formation on the heat exchanger surface, shortening the continuous heating operation time and reducing the system's coefficient of performance and heating capacity.

[0003] To address the aforementioned issues, related technologies have proposed adding a wind-grate structure to the windward side of the heat exchanger. By adding a wind-grate to the fin surface and utilizing non-uniformly spaced guide vanes, the direction of airflow after entering the heat exchanger can be improved to some extent, thus making the air velocity distribution more uniform. However, in these existing wind-grate structures, the guide vanes are usually fixed or can only be adjusted in a single dimension, making it impossible to independently and precisely match the airflow to each module according to the heat exchange needs of different areas under actual operating conditions. Specifically, because the angle and spacing of the guide vanes cannot be flexibly adjusted, when the outdoor ambient temperature, compressor frequency, or water temperature changes, the air inlet angle and airflow distribution cannot be adaptively adjusted. This results in significant deviations in heat exchange between parallel heat exchange modules, underutilization of the effective heat exchange area, and difficulties in preventing premature frosting and significant drops in water temperature during defrosting in winter heating operation, thus failing to achieve efficient and stable operation under all conditions.

[0004] Therefore, how to design a heat exchange device that can independently adjust the airflow of each parallel module of the heat exchanger to adapt to different operating conditions is a technical problem that the industry urgently needs to solve. Summary of the Invention

[0005] To address the shortcomings of existing heat exchangers, such as the inability to independently adjust the airflow of each module and the uneven airflow distribution and frost formation caused by the fixed air grating structure, this invention proposes a control method for a heat exchange device, an air conditioning unit, and the heat exchange device. By dividing the heat exchanger into multiple parallel modules and setting an air grating structure with independently adjustable air guide vane angles and spacing, and combining detection components and a controller for adaptive control, this method not only achieves precise matching of airflow in each module but also effectively improves heat exchange uniformity, significantly reduces the risk of frost formation, and enhances system energy efficiency, thus achieving energy-saving effects.

[0006] The technical solution adopted in this invention is to design a heat exchange device, including:

[0007] The heat exchanger consists of multiple heat exchange modules connected in parallel;

[0008] Multiple air grating structures are arranged on the windward side of the heat exchanger. Each air grating structure includes a limiting frame, at least two air guide vanes arranged within the limiting frame, a rotary drive assembly for driving the air guide vanes to rotate around an axis to adjust the air inlet angle, and a telescopic drive assembly for driving the air guide vanes to move along the limiting frame to adjust the spacing between the air guide vanes.

[0009] Each heat exchange module has its own independent air grating structure.

[0010] This design divides the heat exchanger into multiple parallel heat exchange modules and sets up a corresponding air grating structure for each heat exchange module independently, so that the air volume of each module can be controlled individually. The air grating structure is equipped with both a rotary drive component and a telescopic drive component. The air guide vanes can rotate around the axis to adjust the air inlet angle and move along the limit frame to adjust the spacing. This allows for flexible matching of air volume according to the actual heat exchange requirements of each module, improving the problem of uneven air velocity distribution on the heat exchanger surface and enhancing the overall heat exchange efficiency.

[0011] Furthermore, each heat exchange module is equipped with a detection component for detecting temperature and pressure at the refrigerant flow path inlet and outlet. The detection component is connected to the controller of the heat exchange device. The controller controls the corresponding air grid structure to adjust the air inlet angle and / or spacing of the air guide vanes based on the detection data of the detection component.

[0012] This design incorporates temperature and pressure detection components at the inlet and outlet of the refrigerant flow path of each heat exchange module, connecting these components to a controller. This allows the controller to determine the heat exchange status based on the real-time inlet and outlet parameters of each module, thereby controlling the corresponding air grating structure to adjust the angle and / or spacing of the air guide vanes. This achieves automated and precise airflow regulation, helping to balance the heat exchange of each module.

[0013] Furthermore, each air guide vane is fixedly connected to a rotating shaft, and a guide groove is provided on the limiting frame. A slider is slidably mounted in the guide groove, and the rotating shaft is rotatably mounted on the slider. The rotation drive assembly is connected to the rotating shaft and is used to drive the rotating shaft to rotate relative to the slider, so as to drive the air guide vane to rotate around the axis to adjust the air inlet angle. The telescopic drive assembly is connected to the slider or air guide vane and is used to drive the slider to move along the guide groove, so as to drive the air guide vane to move and adjust the spacing.

[0014] This design fixes the air guide vane to a rotating shaft, which is rotatably mounted on a slider that can slide along a guide groove. When the rotary drive assembly drives the rotating shaft to rotate relative to the slider, the air guide vane rotates accordingly to adjust the air inlet angle. When the telescopic drive assembly drives the slider to move along the groove, the air guide vane moves accordingly to adjust the spacing. The rotational and translational motions do not interfere with each other, the mechanical structure is stable and reliable, and the dual independent adjustment of the air guide vane angle and spacing is achieved.

[0015] In some embodiments, the rotary drive assembly includes a rotary motor disposed on the slider, the output shaft of the rotary motor being drivenly connected to the rotating shaft to drive the rotating shaft to rotate; the telescopic drive assembly includes a telescopic motor and a drive rod, the drive rod being connected between two adjacent air guide vanes, the telescopic motor controlling the extension or retraction of the drive rod, and driving the slider to move along the guide groove by pushing and pulling the air guide vanes.

[0016] This design uses a rotary motor mounted on the slider and connected to the rotating shaft for transmission, so that the rotary motor moves along with the slider, ensuring the stability of the rotary drive. The telescopic drive assembly uses a drive rod to connect two adjacent air guide vanes. The telescopic motor controls the extension or retraction of the rod to push or pull the air guide vanes, thereby driving the slider to move along the guide groove. This structure is compact and has direct transmission, and can reliably achieve the adjustment of the air guide vane spacing.

[0017] In some embodiments, the number of air guide vanes in the air grating structure is two.

[0018] This design limits the number of air guide vanes in the air grating structure to two, resulting in a symmetrical structure and simple control. After being connected to the two ends of the drive rod respectively, the spacing can be easily increased or decreased, reducing the complexity of drive control while satisfying the basic adjustment function of the air grating structure.

[0019] In some embodiments, the heat exchanger is a finned tube heat exchanger.

[0020] This design specifically defines the heat exchanger as a finned tube heat exchanger, allowing the aforementioned air grid structure and control method to be directly applied to common air source heat pumps and other equipment. This helps to improve the problems of uneven airflow and localized frost formation on the surface of finned tube heat exchangers, thereby enhancing the applicability and practicality of this type of heat exchanger.

[0021] The present invention also proposes an air conditioning unit, including the aforementioned heat exchange device. Because the heat exchange device has the ability to independently adjust the airflow of each parallel module and adaptively control the angle and spacing of the air guide vanes based on detection data, it helps to improve the heat exchange uniformity, energy efficiency, and operational reliability of the air conditioning unit.

[0022] This invention also discloses a control method for a heat exchange device, the heat exchange device having multiple heat exchange modules arranged in parallel, each heat exchange module having an independently arranged air grating structure on its windward side, the air grating structure including at least two air guide vanes with adjustable angles and adjustable spacing; the control method includes an air grating structure adjustment step:

[0023] Obtain the inlet and outlet parameters of the refrigerant flow path for each heat exchange module;

[0024] Calculate the heat exchange capacity Q_i and the outlet superheat SH_i of the heat exchange module based on the inlet and outlet parameters of the heat exchange module.

[0025] Determine whether the heat transfer deviation |ΔQ| between the heat transfer capacity Q_i of each heat exchange module and the average heat transfer capacity Q_avg of all heat exchange modules is greater than the preset heat transfer deviation threshold.

[0026] If so, adjust the spacing between the air guide vanes of the heat exchange module;

[0027] If not, adjust the angle of the air guide vanes according to the outlet superheat SH_i of the heat exchange module.

[0028] This design calculates the heat exchange capacity Q_i and outlet superheat SH_i by acquiring the inlet and outlet parameters of each heat exchange module. It first determines the deviation between the heat exchange capacity Q_i and the average heat exchange capacity Q_avg to decide whether to adjust the spacing. Then, it adjusts the angle according to the superheat deviation ΔSH. This step-by-step adjustment strategy allows the system to first correct large heat exchange imbalances and then perform fine-tuning of the superheat, improving the rationality of the control process and the stability of system operation.

[0029] Furthermore, adjusting the spacing between the air guide vanes of the heat exchange module includes:

[0030] If the heat exchange capacity Q_i of the heat exchange module is greater than the average heat exchange capacity Q_avg, then reduce the spacing between the air guide vanes to reduce the air volume.

[0031] If the heat exchange capacity Q_i of the heat exchange module is less than the average heat exchange capacity Q_avg, then increase the spacing between the air guide vanes to increase the air volume.

[0032] This design reduces the airflow by decreasing the spacing between air guide vanes when the heat exchange capacity Q_i of a certain module is greater than the average heat exchange capacity Q_avg, and increases the spacing to increase the airflow when the heat exchange capacity Q_i of a certain module is less than the average heat exchange capacity Q_avg. This gradually makes the heat exchange capacity Q_i of each module more consistent, reducing the situation of individual modules being overloaded or underloaded, and improving the effective utilization rate of the overall heat exchanger area.

[0033] Furthermore, adjusting the angle of the air guide vanes according to the outlet superheat SH_i of the heat exchange module includes:

[0034] Calculate the superheat deviation ΔSH, where ΔSH = outlet superheat SH_i - target superheat SH_target;

[0035] If the superheat deviation ΔSH is greater than the preset upper limit of superheat deviation, the angle of the air guide vanes will be increased to reduce the air volume.

[0036] If the superheat deviation ΔSH is less than the preset lower limit of superheat deviation, the angle of the air guide vanes will be reduced to increase the air volume.

[0037] If the superheat deviation ΔSH is between the preset upper limit of superheat deviation and the preset lower limit of superheat deviation, the air guide vane will maintain its current angle.

[0038] This design increases the angle of the air guide vanes to reduce airflow when the superheat is too high, and decreases the angle of the air guide vanes to increase airflow when the superheat is too low. This achieves closed-loop regulation of superheat, keeping the outlet superheat SH_i of each module within a reasonable range, which helps reduce the risk of liquid slugging and improve the safe operation of the system.

[0039] Furthermore, the control method also includes: after adjusting the angle of the air guide vane, calculating the corresponding spacing compensation amount Δd based on the angle adjustment amount using a preset equivalent conversion coefficient. 补偿 The spacing between the air guide vanes is adjusted to compensate for the changes in heat exchange. The equivalent conversion factor is the ratio of the influence rate of angle change on heat exchange to the influence rate of spacing change on heat exchange.

[0040] This design, after adjusting the angle of the air guide vanes, uses an equivalent conversion factor to convert the angle adjustment amount into the corresponding spacing compensation amount, and then adjusts the spacing accordingly. This effectively reduces the mutual interference between angle adjustment and spacing adjustment, alleviates the system's back-and-forth oscillation between the two adjustment dimensions, and makes the control process more stable.

[0041] Furthermore, the control method also includes an adaptive initialization step:

[0042] The operating conditions of the air conditioning unit where the heat exchange device is located are divided into multiple operating condition zones;

[0043] Record the angle and spacing of the air guide vanes when the air conditioning unit reaches a stable state under various operating conditions, and establish a memory database;

[0044] When the air conditioning unit is turned on, the memory database is queried according to the current operating conditions. If a matching record is found, the air guide vane angle and spacing in the matching record are directly used as the initial adjustment position.

[0045] This design directly calls the matching initial adjustment position upon startup, shortening the optimization time for the system to reach the optimal adjustment state from startup and reducing frequent adjustment actions in the early stages of startup.

[0046] Furthermore, the control method also includes defrosting control steps:

[0047] After the wind grid adjustment cycle reaches a preset number of times, if the heat exchange capacity Q_i of the heat exchange module is less than the average heat exchange capacity Q_avg of all heat exchange modules, and the difference between the average heat exchange capacity and the heat exchange capacity Q_i is greater than the preset frosting judgment threshold, then the heat exchange module is marked as a frosting module, and the adjustment of the wind grid structure of the frosting module is stopped.

[0048] When the number of marked frosting modules reaches a preset threshold proportion of the total number of heat exchange modules, the air conditioning unit is controlled to enter defrosting mode.

[0049] This design marks the frosting modules based on the deviation between the heat exchange and the average heat exchange, and controls the air conditioning unit to enter defrosting mode when the proportion of frosting modules to the total number of modules reaches a preset threshold. This achieves auxiliary defrosting judgment based on actual heat exchange effect, which helps to start defrosting at the appropriate time, reduces unnecessary defrosting operations, and extends the continuous heating operation time.

[0050] Compared with the prior art, the present invention has at least one of the following beneficial effects:

[0051] 1. The heat exchanger is divided into multiple parallel heat exchange modules, and each module is independently equipped with an air grating structure. The air guide vanes can be rotated to adjust the air inlet angle and moved to adjust the spacing. Compared with traditional fixed air gratings or solutions that can only be adjusted in one dimension, this application can independently match the air volume according to the actual heat exchange requirements of each module, reducing heat exchange dead zones and local superheating abnormalities caused by uneven air velocity, improving the utilization rate of the effective area of ​​the heat exchanger and the overall energy efficiency of the system, and achieving energy-saving effects.

[0052] 2. Determine whether the spacing needs adjustment based on the deviation between the heat exchange of each module and the average heat exchange. After the deviation is small or the spacing adjustment is stable, fine-tune the angle of the air guide vanes according to the superheat deviation. This step-by-step control method of coarse adjustment followed by fine adjustment enables the system to quickly correct large heat exchange imbalances between modules, and then achieve fine airflow matching through superheat fine-tuning, improving the systematic nature of the control process and the stability of system operation.

[0053] 3. After adjusting the angle of the air guide vanes, the angle adjustment amount is converted into the corresponding spacing compensation amount using the equivalent conversion coefficient and then compensated. This effectively alleviates the coupling effect of angle change and spacing change on heat exchange, keeps the system coordinated between the two adjustment dimensions, reduces back-and-forth oscillations near the optimal operating point, and extends the service life of the drive components.

[0054] 4. After adjusting the air vents and stabilizing the system, if the heat exchange of a certain module is still less than the average heat exchange and the difference exceeds the preset frosting threshold, it is then marked as a frosting module. This judgment method, based on actual heat exchange performance and excluding airflow distribution interference, can more accurately distinguish between airflow distribution issues and heat exchange deterioration caused by frosting, avoiding misjudgments. Defrost mode is only activated when the proportion of frosting modules reaches the preset proportion threshold, reducing unnecessary defrosting cycles and extending the continuous heating operation time. Attached Figure Description

[0055] The present invention will now be described in detail with reference to the embodiments and accompanying drawings, wherein:

[0056] Figure 1 This is a schematic diagram of the heat exchange device of the present invention;

[0057] Figure 2 yes Figure 1 A schematic diagram of side A;

[0058] Figure 3 This is a schematic diagram of the angle adjustment of the air guide vane of the present invention;

[0059] Figure 4 This is a schematic diagram illustrating the adjustment of the spacing of the air guide vanes in this invention;

[0060] Figure 5 This is a schematic diagram of the wind grid structure adjustment steps in the control method of the present invention;

[0061] Figure 6 This is a schematic diagram of the spacing adjustment process of the present invention;

[0062] Figure 7 This is a schematic diagram of the angle adjustment process of the present invention;

[0063] Figure 8 This is a schematic diagram of the spacing compensation adjustment process of the present invention;

[0064] Figure 9 This is a schematic diagram illustrating the spacing, angle, and spacing compensation adjustment in an application example of the present invention.

[0065] Figure 10 This is a schematic diagram of the adaptive initialization steps of the control method of the present invention;

[0066] Figure 11 This is a schematic diagram of the standardized frost cycle heat transfer curve of the control method of the present invention;

[0067] Figure 12 This is a schematic diagram of the defrosting control steps of the control method of the present invention;

[0068] Figure 13 This is a schematic diagram of the control method according to a preferred embodiment of the present invention;

[0069] Explanation of reference numerals in the attached drawings: 1. Wind grid structure; 11. Air guide vane; 12. Limiting frame; 13. Rotating shaft; 2. Heat exchanger; 3. Axial flow fan. Detailed Implementation

[0070] To make the technical problems to be solved, the technical solutions, and the beneficial effects of the present invention clearer, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0071] like Figures 1 to 4 As shown, this invention proposes a heat exchange device, the core of which lies in reconstructing a traditional integral heat exchanger into multiple parallel independent modules, and configuring an adjustment mechanism in front of the windward side of each module that can simultaneously change the angle and spacing of the air guide vanes. Specifically, the heat exchange device includes a heat exchanger 2 composed of multiple parallel heat exchange modules, and multiple air grating structures 1 disposed on the windward side of the heat exchanger 2. Each air grating structure 1 is equipped with a limiting frame 12, at least two air guide vanes 11, a rotation drive assembly, and a telescopic drive assembly. The rotation drive assembly is responsible for driving the air guide vanes 11 to rotate around the axis to change the air inlet angle, and the telescopic drive assembly is responsible for driving the air guide vanes 11 to move along the limiting frame 12 to change the spacing between them, and each heat exchange module has its own dedicated air grating structure.

[0072] From the perspective of specific connections and working principles, multiple heat exchange modules are connected in parallel on the refrigerant pipeline. Each module contains several heat exchange tubes. The refrigerant flows from the main pipe into each module, and after heat exchange, it converges and flows out again. A fan grille structure covers the windward surface of the corresponding module. The guide vanes 11 are placed horizontally in the airflow path. By changing their angle and spacing, they directly change the air intake area and airflow direction of the module's windward surface, thereby adjusting the actual ventilation volume of the module. During operation, the system can independently control the drive components of each fan grille structure 1 according to the heat load requirements of different modules, achieving differentiated airflow distribution among modules.

[0073] In a feasible embodiment, the heat exchanger 2 can be divided into multiple modules arranged along its length, for example, i modules according to the number of tubes or loops, with each module corresponding to a set of air grating structures 1. In an air source heat pump system, since the axial fan 3 is usually located at the top of the heat exchanger 2, the top air velocity is high and the bottom air velocity is low. Through the independent air gratings of this design, the spacing of the guide vanes 11 at the bottom module can be increased or the angle adjusted to increase the air intake, while the spacing of the top module can be reduced to suppress excessive air intake, thereby making the heat exchange of each module more balanced and effectively avoiding the risk of excessive local overheating or liquid slugging.

[0074] This design divides the heat exchanger 2 into multiple parallel heat exchange modules and sets a corresponding air grating structure 1 for each heat exchange module independently, so that the air volume of each module can be controlled individually. The air guide vanes 11 can both rotate and translate, and the system can flexibly match the air volume to different modules according to the actual heat exchange requirements, thereby improving the problem of uneven air velocity distribution on the surface of the heat exchanger 2 and improving the overall heat exchange efficiency.

[0075] In a preferred embodiment of the present invention, each heat exchange module is equipped with a detection component, which is connected to the controller of the heat exchange device. The detection component specifically includes a temperature sensor and a pressure sensor respectively arranged at the inlet and outlet of the refrigerant flow path of each module. By collecting these data, the controller can calculate the outlet saturated evaporation temperature T_out of the module, and subtract T_out from the outlet temperature Ts to obtain the outlet superheat SH_i. At the same time, the unit heat exchange capacity Q_i of the module is calculated by the difference between the inlet and outlet enthalpy values, which provides an accurate data basis for subsequent air grid adjustment, so that the air volume adjustment is no longer a blind fixed action, but a precise response based on the real-time heat exchange status.

[0076] During operation, the detection component collects the refrigerant temperature and pressure at the inlet and outlet of each module in real time. These parameters are transmitted to the controller via signal lines. The controller has a built-in algorithm program that can calculate the saturation temperature and superheat of each module, as well as the heat exchange Q_i based on the inlet and outlet enthalpy difference, thus forming a closed-loop control. The controller is connected to the rotation drive component and telescopic drive component of the air grating structure 1 via electrical signals. Based on the calculation results, it issues control commands to drive the motor to automatically adjust the air inlet angle and / or spacing of the air guide vanes 11.

[0077] This design achieves automated and precise airflow regulation by setting temperature and pressure detection components at the inlet and outlet of the refrigerant flow path of each heat exchange module and connecting these components to the controller. This allows the controller to determine the heat exchange status based on the real-time inlet and outlet parameters of each module, and then control the corresponding air grating structure 1 to adjust the angle and / or spacing of the air guide vanes 11. This helps to make the heat exchange of each module more balanced.

[0078] See Figure 3 and Figure 4 As shown, each air guide vane 11 is fixedly connected to a rotating shaft 13. The rotating shaft 13 passes through the air guide vane 11 and is fixedly connected to it, so that when the rotating shaft 13 rotates, the air guide vane 11 rotates synchronously to change the windward angle. The limiting frame 12 is provided with a guide groove and a slider. The slider is embedded in the guide groove of the limiting frame and can only slide in a straight line along the groove and cannot rotate. The rotating shaft 13 is mounted on the slider through a bearing. Therefore, the rotating shaft 13 can both rotate relative to the slider and translate along with the slider in the groove. The rotary drive assembly is connected to the rotating shaft 13 and is used to drive the rotating shaft 13 to rotate relative to the slider, so as to drive the air guide vane 11 to rotate around the axis to adjust the air inlet angle. The telescopic drive assembly is connected to the slider or the air guide vane 11 and is used to drive the slider to move along the guide groove, so as to drive the air guide vane 11 to move and adjust the spacing.

[0079] This design fixes the air guide vane 11 to the rotating shaft 13, which is rotatably mounted on a slider that can slide along the guide groove. When the rotary drive assembly drives the rotating shaft 13 to rotate relative to the slider, the air guide vane 11 rotates accordingly to adjust the air inlet angle. When the telescopic drive assembly drives the slider to move along the groove, the air guide vane 11 moves accordingly to adjust the spacing. The rotational motion and translational motion do not interfere with each other, the mechanical structure is stable and reliable, and the dual independent adjustment of the angle and spacing of the air guide vane 11 is achieved.

[0080] In some embodiments, the rotary drive assembly includes a rotary motor mounted on the slider. The output shaft of the rotary motor is connected to the rotating shaft 13 for driving the rotating shaft 13 to rotate. In practical applications, the rotation angle can be adjusted from 0 to 90°. When the unit is turned off, the guide vane angle is 90°. At this time, the guide vanes 11 are parallel to the airflow direction and close to each other, which can play a dustproof role by shielding the fins and preventing dust from entering. The telescopic drive assembly includes a telescopic motor and a drive rod. The drive rod is connected between two adjacent guide vanes 11. The telescopic motor controls the extension or retraction of the drive rod. By pushing and pulling the guide vanes 11, the slider moves along the guide groove, thereby realizing the adjustment of the spacing between the guide vanes 11.

[0081] In the specific transmission process, the rotary motor is fixed on the slider and moves with the slider. Its output shaft is connected to the rotating shaft through a coupling or gear. When the motor receives a pulse signal from the controller and rotates, the rotating shaft 13 rotates on the slider, and the air guide vane 11 rotates accordingly to change its angle. Since the motor and the slider move as a whole, the position of the rotary motor always maintains the optimal transmission distance with the air guide vane 11. In the telescopic drive assembly, the two ends of the drive rod are respectively connected to two air guide vanes 11. When the telescopic motor controls the extension of the rod, the two air guide vanes 11 are pushed apart, and the rotating shaft 13 drives the slider to slide in the guide groove, increasing the distance between the air guide vanes 11; the opposite is true when the rod is shortened, making the structure very compact.

[0082] This design uses a rotary motor mounted on the slider and connected to the rotating shaft 13 for transmission, so that the rotary motor moves along with the slider, ensuring the stability of the rotary drive. The telescopic drive assembly uses a drive rod to connect two adjacent air guide vanes 11. The telescopic motor controls the extension or retraction of the rod to push or pull the air guide vanes 11, thereby driving the slider to move along the guide groove. This structure is compact and has direct transmission, which can reliably adjust the spacing of the air guide vanes 11.

[0083] To improve the reliability of the wind grating structure and simplify the control logic, the preferred solution is to set two air guide vanes 11 in the wind grating structure. The structure is symmetrical and easy to control. After being connected to the two ends of the drive rod respectively, the spacing can be easily enlarged or reduced, reducing the complexity of drive control, while satisfying the basic adjustment function of the wind grating structure.

[0084] The two air guide vanes 11 each have independent rotating shafts 13, but they move synchronously through a linkage mechanism and are connected by a drive rod, forming a simple linear push-pull mechanism. When the drive rod extends, the two air guide vanes 11 move outward simultaneously, increasing the distance between them and the ventilation area; when the drive rod shortens, the two vanes move closer together, decreasing the distance between them and the ventilation area. Since there are only two air guide vanes 11, only one telescopic drive assembly is needed, resulting in the simplest control logic and the fewest potential failure points.

[0085] Since each air grating structure 1 contains two extendable and rotatable air guide vanes 11, and a module can contain multiple air grating structures depending on its actual size, the total number of air guide vanes in a single module is equal to the number of air grating structures multiplied by 2. For example, in a heat exchange module, multiple such double-air guide vane air grating structures can be arranged side by side, with each air grating structure adjusted independently, thereby achieving precise airflow control on the windward side of the entire module. At the same time, each air grating structure contains only two air guide vanes 11, resulting in lower manufacturing and assembly costs.

[0086] In air source heat pump systems, finned tube heat exchangers are the core heat exchange components of the unit. In conventional air-cooled heat pump units, the fan is placed on top of the heat exchanger. Due to the axial fan layout, the wind speed on the heat exchanger's windward side exhibits a significantly non-uniform distribution, with high wind speeds at the top and low wind speeds at the bottom. The high-speed zone results in high refrigerant superheat, while the low-speed zone may pose a risk of liquid slugging and heat exchange dead zones. The air grating structure 1 of this invention specifically addresses this pain point of finned tube heat exchangers, demonstrating significant practical application effects. Therefore, in a preferred embodiment of this invention, the heat exchanger 2 is a finned tube heat exchanger, allowing the aforementioned air grating structure 1 and control method to be directly applied to common air source heat pumps and other equipment. This helps improve the uneven wind speed and localized frosting problems on the surface of the finned tube heat exchanger, enhancing the applicability and practicality of this type of heat exchanger.

[0087] Specifically, the finned tube heat exchanger consists of multiple rows of copper tubes and aluminum fins. Air flows through the gaps between the fins and exchanges heat with the refrigerant inside the tubes. Due to its structural characteristics, the wind speed distribution on the windward side is easily affected by the fan position and the duct structure. By installing the air grid structure 1 in front of the windward side of the finned tube heat exchanger, the angle and spacing of the air guide vanes 11 can be adjusted to directly change the airflow and velocity through different areas of the fin gaps, thereby specifically improving the wind speed distribution and reducing heat exchange dead zones.

[0088] The present invention also proposes an air conditioning unit, including the aforementioned heat exchange device. Because the heat exchange device has the ability to independently adjust the airflow of each parallel module and adaptively control the angle and spacing of the air guide vanes based on detection data, it helps to improve the heat exchange uniformity, energy efficiency, and operational reliability of the air conditioning unit.

[0089] The air conditioning unit may include a compressor, a four-way valve, a throttling element, a fan, and the aforementioned heat exchange device. The heat exchanger in the heat exchange device is connected in the refrigerant circulation loop and is used as an evaporator or condenser. The fan grille structure, detection components, and controller are integrated inside the unit, together forming a complete temperature control system that works collaboratively in various modes such as heating, cooling, and defrosting.

[0090] It should be understood that the air conditioning unit can be an air source heat pump unit. During winter heating operation, the heat exchanger 2 acts as an evaporator to absorb heat from the outside air. At this time, due to the low ambient temperature and high humidity, the surface of the heat exchanger 2 is prone to frost formation. This invention, by dividing the heat exchanger 2 into modules and setting independent air vent structures 1, can not only optimize the heat exchange uniformity of each module, but also accurately judge the frost formation situation according to the subsequent control method, realize assisted defrosting, and extend the continuous heating time in winter.

[0091] See Figure 5 As shown, the present invention also provides a control method based on the above-mentioned heat exchange device, including a wind grid structure adjustment step:

[0092] Obtain the inlet and outlet parameters of the refrigerant flow path for each heat exchange module. The inlet parameters include the refrigerant temperature measured by the inlet temperature sensor and the refrigerant pressure measured by the inlet pressure sensor. The outlet parameters include the refrigerant temperature (outlet temperature Ts_out) measured by the outlet temperature sensor and the refrigerant pressure (converted to outlet saturated evaporation temperature T_out) measured by the outlet pressure sensor.

[0093] Based on the inlet and outlet parameters of the heat exchange module, the heat exchange capacity Q_i and outlet superheat SH_i of the heat exchange module are calculated. Specifically, the outlet pressure is converted into the corresponding saturated evaporation temperature using the refrigerant thermodynamic property table. The outlet superheat SH_i is obtained by subtracting the saturated evaporation temperature from the measured outlet temperature. At the same time, the corresponding refrigerant specific enthalpy value is found based on the inlet and outlet temperatures and pressures. The heat exchange capacity Q_i of the module is obtained by subtracting the outlet enthalpy value from the approximate inlet saturated enthalpy value. Finally, the heat exchange capacity Q_i of all modules is summed to calculate the average heat exchange capacity Q_avg.

[0094] Determine whether the heat exchange deviation |ΔQ| between the heat exchange capacity Q_i of each heat exchange module and the average heat exchange capacity Q_avg of all heat exchange modules is greater than a preset heat exchange deviation threshold. This threshold can be set to the average heat exchange capacity Q_avg or a preset adjustment percentage of the rated heat exchange capacity (e.g., 15%) to define whether there is a serious imbalance in the air volume distribution between modules.

[0095] If so, it means that the heat exchange capacity Q_i of the heat exchange module is too different from the overall average level, and there is obvious uneven heat exchange. At this time, the spacing between the air guide vanes 11 of the heat exchange module should be adjusted first. The extension and retraction drive assembly drives the drive rod to extend or shorten, and the density between the air guide vanes 11 is changed to quickly increase or decrease the ventilation volume of the module. The large change in ventilation area is used to achieve coarse adjustment and correction.

[0096] If not, it means that the heat exchange capacity Q_i of each heat exchange module is relatively close and the overall air volume distribution is relatively balanced. At this time, the spacing is no longer changed significantly. Instead, the angle of the air guide vanes is adjusted according to the outlet superheat SH_i of the heat exchange module. The direction and resistance of the airflow entering the heat exchanger are changed by finely adjusting the tilt angle of the air guide vanes 11 by rotating the drive component. This allows for fine-tuning and optimization of the superheat to ensure stable system operation.

[0097] This design calculates the heat exchange capacity Q_i and outlet superheat SH_i by acquiring the inlet and outlet parameters of each heat exchange module. It first determines the heat exchange deviation |ΔQ| between the heat exchange capacity Q_i and the average heat exchange capacity Q_avg to decide whether to adjust the spacing. Then, it adjusts the angle according to the superheat deviation ΔSH. This step-by-step adjustment strategy allows the system to first correct large heat exchange imbalances and then perform fine-tuning of the superheat, improving the rationality of the control process and the stability of system operation.

[0098] The control method is executed periodically by the controller after the unit starts up. The controller first collects data from each module via sensors, converts the pressure to saturation temperature using the refrigerant thermodynamic property table, calculates the superheat based on temperature measurement points, and calculates the heat exchange rate Q_i using the inlet and outlet enthalpy difference. Then, it calculates the average heat exchange rate Q_avg of all modules and compares the relative deviation between each module's heat exchange rate Q_i and the average heat exchange rate Q_avg. If the deviation exceeds a preset heat exchange rate deviation threshold, it indicates severely uneven airflow distribution, and coarse adjustment is first performed by adjusting the spacing of the telescopic drive assembly; if the deviation is within the allowable range, it indicates that the airflow distribution is basically reasonable, and the superheat rate is then optimized by fine-tuning the angle of the rotary drive assembly. The entire adjustment process is logically clear and hierarchically structured.

[0099] To illustrate the application of this invention, after the air conditioning unit is turned on for heating operation, the air guide vanes first move to the initial angle and initial spacing. The initial angle is 30° after the first start-up and 90° when the unit is turned off to prevent dust. The preset target superheat SH_target can typically be set to 3°C or 5°C. The controller collects the inlet temperature / pressure and outlet temperature / pressure of heat exchange module i, calculates the outlet saturated evaporation temperature T_out and the outlet superheat SH_i, where the outlet superheat SH_i = outlet saturated evaporation temperature T_out - outlet temperature Ts_out, and calculates the heat exchange Q_i through the enthalpy value = outlet enthalpy h_out - inlet saturated enthalpy h_sat. The average heat exchange rate Q_avg is calculated by iterating through all heat exchange modules. The heat exchange deviation |ΔQ|=|Q_i-Q_avg| is calculated. When |ΔQ| / Q_ref>the preset adjustment ratio (15%), it indicates that the air guide vanes of the module are not in the optimal position and the spacing needs to be adjusted. This completes the closed loop from data acquisition to judgment and execution.

[0100] It should be noted that Q_ref is a preset reference heat exchange rate, preferably the average heat exchange rate Q_avg of all heat exchange modules or the rated heat exchange rate of the unit.

[0101] See Figure 6 As shown, to improve the accuracy of the air guide vane spacing adjustment, the preferred solution is to adjust the spacing between the air guide vanes of the heat exchange module according to the following control logic:

[0102] If the heat exchange capacity Q_i of the heat exchange module is greater than the average heat exchange capacity Q_avg, it indicates that the current air intake of the module is too large, resulting in excessive heat absorption by the refrigerant. Long-term operation may cause the temperature in this area to be too low and frost to form prematurely. It also means that there is a significant skew in the air volume distribution. At this time, the controller controls the telescopic drive component to reduce the distance between the air guide vanes 11 to reduce the air volume and increase the airflow resistance, so that the heat exchange capacity of the module falls back to a reasonable range.

[0103] If the heat exchange capacity Q_i of the heat exchange module is less than the average heat exchange capacity Q_avg, it indicates that the current air intake of the module is insufficient, resulting in low heat exchange efficiency, underutilized heat exchange dead zones and wasted area. It may also be accompanied by the risk of liquid slugging due to low superheat. At this time, the controller controls the telescopic drive component to increase the spacing between the air guide vanes 11 to increase the air volume, reduce airflow resistance, enhance the heat exchange effect at this point, and make the heat exchange capacity Q_i of each module tend to be consistent.

[0104] This design adjusts the spacing of the air guide vanes 11 to gradually make the heat exchange of each module more consistent, reducing the situation where individual modules are overloaded or underloaded, and improving the effective utilization rate of the overall area of ​​the heat exchanger.

[0105] When adjusting the spacing, the controller sends a command to the telescopic drive assembly. If the heat exchange capacity Q_i of a certain heat exchange module is too high, it indicates that the air intake is too large. The controller then controls the drive rod to shorten, reducing the spacing between the air guide vanes 11, increasing airflow resistance, and reducing the air intake of that heat exchange module, thus lowering its heat exchange capacity Q_i. Conversely, if the heat exchange capacity Q_i of a certain heat exchange module is too low, the controller controls the drive rod to extend, increasing the spacing between the air guide vanes 11, reducing resistance, and introducing more airflow to improve heat exchange. Through this negative feedback adjustment, the difference in heat exchange capacity Q_i between the modules gradually narrows.

[0106] In an application example of this invention, the process of adjusting the spacing between the air guide vanes 11 of the heat exchange module is as follows: If ΔQ > 0, the heat exchange capacity Q_i is too large, and long-term heating operation may cause premature frosting at this location; therefore, the spacing is reduced to decrease the airflow at that location. If ΔQ < 0, the heat exchange capacity Q_i is too low, and the heat exchanger efficiency is low; therefore, the spacing is increased to increase the airflow and improve the heat exchange capacity. The adjustment range of the spacing each time can be a fixed value X. The minimum spacing should meet the space requirements without affecting the angle adjustment, thereby achieving the most effective airflow correction while ensuring mechanical safety.

[0107] See Figure 7 As shown, to improve the accuracy of the air guide vane angle adjustment, the preferred solution is to adjust the air guide vane angle of the heat exchange module according to the following control logic:

[0108] Calculate the superheat deviation ΔSH, where ΔSH = outlet superheat SH_i - target superheat SH_target;

[0109] If the superheat deviation ΔSH is greater than the preset superheat deviation upper limit, it means that the outlet superheat SH_i of the module is too high, the evaporation process is too full and the heat exchange is excessive. At this time, it is necessary to reduce the heat exchange intensity at this point. Therefore, the angle of the air guide vanes is increased to reduce the air volume, so that the airflow sweeps across the heat exchanger surface more obliquely, thereby reducing the heat exchange efficiency between air and refrigerant.

[0110] If the superheat deviation ΔSH is less than the preset superheat deviation lower limit, it indicates that the outlet superheat SH_i of the module is too low, and there may be a risk of incomplete evaporation of the refrigerant. At this time, it is necessary to enhance the heat exchange effect at this point. Therefore, the angle of the air guide vanes is reduced to increase the air volume, so that the airflow can more vertically scour the surface of the heat exchanger and improve the heat exchange efficiency between the air and the refrigerant.

[0111] If the superheat deviation ΔSH is between the preset upper limit and the preset lower limit of the superheat deviation, the air guide vane will maintain its current angle to avoid frequent adjustments due to small fluctuations that could cause system oscillations and maintain stable system operation.

[0112] This design increases the angle of the air guide vanes to reduce airflow when the outlet superheat SH_i is too high, and decreases the angle of the air guide vanes to increase airflow when the outlet superheat SH_i is too low. This achieves closed-loop regulation of superheat, keeping the outlet superheat SH_i of each module within a reasonable range, which helps reduce the risk of liquid slugging and improve the safe operation of the system.

[0113] Superheat reflects the dryness of the refrigerant at the evaporator outlet. Excessive superheat indicates over-evaporation or even overheating, requiring a reduction in airflow to allow the refrigerant to absorb more heat. Insufficient superheat suggests incomplete evaporation of liquid refrigerant, posing a risk of liquid slugging, necessitating increased airflow to enhance heat exchange and ensure complete evaporation. By setting upper and lower limits to create hysteresis control, frequent small adjustments near the critical point prevent system oscillations. When the superheat is within a reasonable range, the angle remains constant, maintaining stable system operation.

[0114] In an application example of this invention, the process of adjusting the angle of the air guide vanes in the heat exchange module is as follows: if ΔSH > 1℃, the superheat is too high, so the angle of the air guide vanes is increased (+3°), making the airflow more inclined and reducing the air volume at this point, thus weakening heat exchange; if ΔSH < -1℃, the superheat is too low, so the angle of the air guide vanes is decreased (-3°), making the airflow more vertical and increasing the air volume at this point, thus enhancing heat exchange; if -1℃ < ΔSH < 1℃, then the adjustment is stopped. This fine-tuning method can accurately control the superheat near the target value, while the angle increment for each adjustment is fixed at 3°, making the control action simple.

[0115] See Figure 8 and Figure 9 As shown, to improve the accuracy of wind grating structure adjustment, the control method also includes: after adjusting the angle of the air guide vanes, calculating the corresponding spacing compensation amount Δd based on the angle adjustment amount using a preset equivalent conversion coefficient. 补偿 The spacing between the air guide vanes is adjusted to compensate for the changes in heat exchange. The equivalent conversion factor is the ratio of the influence rate of angle change on heat exchange to the influence rate of spacing change on heat exchange.

[0116] This design, after adjusting the angle of the air guide vanes, uses an equivalent conversion factor to convert the angle adjustment amount into the corresponding spacing compensation amount, and then adjusts the spacing accordingly. This effectively reduces the mutual interference between angle adjustment and spacing adjustment, alleviates the system's back-and-forth oscillation between the two adjustment dimensions, and makes the control process more stable.

[0117] Because adjusting the angle changes the tilt of the air guide vanes, it affects the local ventilation area and airflow resistance, which in turn affects the total airflow through the module. This change in airflow, in turn, affects the heat exchange, effectively altering the previously adjusted spacing. Therefore, after each fine-tuning of the angle, the spacing needs to be compensated using an equivalent conversion factor to offset the coupling effect of the angle change and ensure that the system always operates near the optimal balance point.

[0118] The specific compensation formula is: Δd 补偿= k × ((∂Q / ∂α) / (∂Q / ∂d)) × Δα, where k is the weighting coefficient, initially set to 0.8 and adaptively adjusted according to actual results; (∂Q / ∂α) / (∂Q / ∂d) is the equivalent conversion coefficient, (∂Q / ∂α) represents the influence rate of angle change on heat exchange, (∂Q / ∂d) represents the influence rate of spacing change on heat exchange, and the equivalent heat exchange coefficient represents how many mm the spacing d changes in equivalent to the effect of a 1° change in angle α on heat exchange. This coefficient needs to be calibrated after calculating the influence of angle and spacing on heat exchange through individual heat exchanger experiments. The equivalent conversion coefficient is a preset value; Δα is the target value for this angle adjustment (e.g., +3° or -3°). Through this compensation mechanism, the system can find the optimal balance point between the two degrees of freedom, avoiding back-and-forth oscillations.

[0119] See Figure 10 As shown, to improve the efficiency of the control scheme, the control method also includes an adaptive initialization step:

[0120] The operating conditions of the air conditioning unit where the heat exchange device is located are divided into multiple operating condition intervals. Specifically, according to key parameters such as ambient temperature, inlet water temperature and compressor operating frequency, the unit can be divided into several independent operating condition intervals with a certain temperature interval or frequency range, so that the unit can find the corresponding classification under various actual use conditions.

[0121] Record the angle and spacing of the air guide vanes when the air conditioning unit reaches a steady state under various operating conditions, and establish a memory database. The steady state refers to the state in which the heat exchange deviation |ΔQ| and superheat deviation ΔSH of each module are maintained within a small range and continue for a certain period of time after the system is adjusted by the air grates. At this time, the controller stores the current operating condition characteristics information together with the corresponding average angle and spacing of the air grates. As the running time accumulates, a memory database covering multiple usage scenarios is gradually formed.

[0122] When the air conditioning unit is turned on, the memory database is queried according to the current operating conditions. If a matching record is found, the air guide vane angle and spacing in the matching record are directly used as the initial adjustment position.

[0123] This design directly calls the matching initial adjustment position upon startup, shortening the optimization time for the system to reach the optimal adjustment state from startup and reducing frequent adjustment actions in the early stages of startup.

[0124] The optimal combination of fan grille angle and spacing varies depending on ambient temperature, water temperature, and compressor frequency. By partitioning operating conditions and establishing a memory database, the system can directly jump to the previously determined optimal position when encountering the same operating conditions upon startup, without having to slowly trial and error from the initial angle. After each adjustment reaches a stable state, the controller stores the operating condition parameters and fan grille parameters as a record in the database. As operating time accumulates, the database covers more and more comprehensive operating conditions, and the system's adaptive capability becomes stronger.

[0125] In an application example of this invention, the adaptive initialization process is as follows: the unit ambient temperature T_amb is partitioned in 5°C intervals (e.g., -15°C to -10°C, -10°C to -5°C, etc.), the unit inlet water temperature T_in is partitioned in 5°C intervals (e.g., 25°C to 30°C, 30°C to 35°C, etc.), and the compressor frequency is set to three intervals: low, medium, and high, according to the operating frequency range. After each adjustment of the unit stabilizes (the spacing adjustment cycle is 5 seconds, the angle adjustment cycle is 15 seconds; if ΔQ / Q_avg between modules < 5% and |ΔSH| < 0.5°C for 5 consecutive minutes, it is determined to be a stable state), the current operating condition information and the average angle and spacing are recorded in the memory database. After running for a period of time, the unit will generate a standardized defrost cycle heat exchange curve covering all user operating conditions (see...). Figure 11 As shown in the figure, by integrating the heat transfer curves generated with different angles and spacings, the maximum heat transfer during the defrosting cycle is obtained. This data is then used to create a data table in the unit controller to store the optimal combination of guide vane adjustment data under different operating conditions. Upon startup, T_amb and the initial frequency are read, and the memory is queried. If a match is found, it is directly called; otherwise, the initial angle of 30° and spacing for the first run are executed, significantly shortening the optimization time.

[0126] See Figure 12 and Figure 13 As shown, in a preferred embodiment of the present invention, the control method further includes a defrosting control step:

[0127] After the louver adjustment cycle reaches a preset number of iterations, if the heat exchange capacity Q_i of a certain heat exchange module is less than the average heat exchange capacity Q_avg of all heat exchange modules, and the difference between the average heat exchange capacity and the heat exchange capacity Q_i is greater than the preset frosting threshold, then the heat exchange module is marked as a frosting module. Specifically, when the louver adjustment cycle is completed, the cycle number n is recorded (this cycle number n is reset to zero when the unit is restarted or shut down). After multiple adjustments to the spacing and angle of the louver structure, if the heat exchange capacity Q_i of a certain heat exchange module is still significantly lower than the average heat exchange capacity Q_avg, then the louver adjustment cycle continues. If the average heat exchange rate Q_avg is greater than the absolute value of the difference between the two values, it indicates that the deterioration of the heat exchange capacity at this point is not due to uneven airflow distribution, but rather because the frost on the surface of the heat exchanger increases the thermal resistance and hinders heat transfer. In this case, the heat exchange module is marked as a frosting module, and the adjustment of the air grid structure of the frosting module is stopped. The frosting threshold can be set to the average heat exchange rate Q_avg or the preset frosting percentage of the rated heat exchange rate (e.g., 30%) to determine whether the heat exchange capacity of the heat exchange module has been severely deteriorated.

[0128] When the number of marked frosted modules reaches a preset threshold (e.g., 70%), it indicates that a considerable number of modules in the unit are unable to exchange heat normally due to frosting, and the overall heat exchange efficiency has been severely affected. The air conditioning unit then enters defrosting mode to centrally remove the frost layer and restore the normal heat absorption capacity of each module.

[0129] This design marks the frosting modules based on the deviation between the heat exchange rate Q_i and the average heat exchange rate Q_avg, and controls the air conditioning unit to enter defrosting mode when the proportion of the number of frosting modules to the total number of modules reaches a preset threshold. This achieves auxiliary defrosting judgment based on actual heat exchange effect, which helps to start defrosting at the appropriate time, reduces unnecessary defrosting operations, and extends the continuous heating operation time.

[0130] The design principle is that after the airflow distribution is adjusted and the system reaches a stable state, if the heat exchange rate (Q_i) of a certain module is still significantly lower than the average level, it indicates that the problem is not with airflow distribution, but rather with a change in the state of the heat exchange surface, such as frost formation leading to increased thermal resistance. This module is then marked as frosted. When this occurs in most modules, it indicates severe frost formation throughout the entire unit, requiring unified defrosting. This judgment method, based on heat exchange performance rather than simply relying on time or temperature thresholds, is more accurate and timely.

[0131] See Figure 13 As shown, in the application example of the present invention, the defrosting control step is as follows: the angle adjustment and spacing adjustment are judged by the heat exchange cycle, and when the difference between the average heat exchange Q_avg is large, the module is marked as having frost. When the number of marked modules m ≥ the total number of modules × 70%, it is judged that the unit is severely frosted and defrosting can be performed.

[0132] It should be noted that the terminology used above is for describing specific embodiments only and is not intended to limit the exemplary embodiments of the present invention. When the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof. The order of execution of actions, steps, etc., in the apparatus and methods shown in the specification and drawings may be implemented in any order unless a specific express order is specified, and as long as the output of a previous process is not used in a subsequent process. Similar sequential terms used for ease of description do not imply that such an order must be followed.

[0133] Techniques, methods, and apparatus known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and apparatus should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as constraints. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0134] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A heat exchange device, characterized in that, include: The heat exchanger consists of multiple heat exchange modules connected in parallel; Multiple air grating structures are disposed on the windward side of the heat exchanger. Each air grating structure includes a limiting frame, at least two air guide vanes disposed within the limiting frame, a rotary drive assembly for driving the air guide vanes to rotate around an axis to adjust the air inlet angle, and a telescopic drive assembly for driving the air guide vanes to move along the limiting frame to adjust the spacing between the air guide vanes. Each heat exchange module is independently equipped with a corresponding air grating structure.

2. The heat exchange device according to claim 1, characterized in that, Each heat exchange module is equipped with a detection component for detecting temperature and pressure at its refrigerant flow path inlet and outlet. The detection component is connected to the controller of the heat exchange device. The controller controls the corresponding air grating structure to adjust the air inlet angle and / or spacing of the air guide vanes based on the detection data of the detection component.

3. The heat exchange device according to claim 1, characterized in that, Each of the air guide vanes is fixedly connected to a rotating shaft, the limiting frame is provided with a guide groove, a slider is slidably mounted in the guide groove, and the rotating shaft is rotatably mounted on the slider; The rotary drive assembly is connected to the rotating shaft and is used to drive the rotating shaft to rotate relative to the slider, so as to drive the air guide vane to rotate around the axis to adjust the air inlet angle. The telescopic drive assembly is connected to the slider or the air guide plate and is used to drive the slider to move along the guide groove, thereby moving the air guide plate to adjust the spacing.

4. The heat exchange device according to claim 3, characterized in that, The rotary drive assembly includes a rotary motor, which is mounted on the slider. The output shaft of the rotary motor is connected to the rotating shaft to drive the rotating shaft to rotate. The telescopic drive assembly includes a telescopic motor and a drive rod. The drive rod is connected between two adjacent air guide vanes. The telescopic motor controls the extension or retraction of the drive rod, and drives the slider to move along the guide groove by pushing and pulling the air guide vanes.

5. The heat exchange device according to claim 1, characterized in that, The number of air guide vanes in the wind grating structure is two.

6. The heat exchange device according to any one of claims 1 to 5, characterized in that, The heat exchanger is a finned tube heat exchanger.

7. An air conditioning unit, characterized in that, Includes the heat exchange device as described in any one of claims 1 to 6.

8. A control method for a heat exchange device, characterized in that, The heat exchange device has multiple heat exchange modules arranged in parallel. Each heat exchange module has an independently provided wind grid structure on its windward side. The wind grid structure includes at least two air guides with adjustable angle and adjustable spacing. The control method includes a wind grid structure adjustment step: Obtain the inlet and outlet parameters of the refrigerant flow path for each heat exchange module; Based on the inlet and outlet parameters of the heat exchange module, calculate the heat exchange capacity Q_i and the outlet superheat SH_i of the heat exchange module; Determine whether the heat exchange deviation |ΔQ| between the heat exchange capacity Q_i of each heat exchange module and the average heat exchange capacity Q_avg of all heat exchange modules is greater than a preset heat exchange deviation threshold. If so, adjust the spacing between the air guide vanes of the heat exchange module; If not, adjust the angle of the air guide vanes according to the outlet superheat SH_i of the heat exchange module.

9. The control method according to claim 8, characterized in that, Adjusting the spacing between the air guide vanes of the heat exchange module includes: If the heat exchange capacity Q_i of the heat exchange module is greater than the average heat exchange capacity Q_avg, then the spacing between the air guide vanes is reduced to reduce the air volume. If the heat exchange capacity Q_i of the heat exchange module is less than the average heat exchange capacity Q_avg, then the spacing between the air guide vanes is increased to increase the air volume.

10. The control method according to claim 8, characterized in that, Adjusting the angle of the air guide vanes according to the outlet superheat SH_i of the heat exchange module includes: Calculate the superheat deviation ΔSH, where ΔSH = outlet superheat SH_i - target superheat SH_target; If the superheat deviation ΔSH is greater than the preset upper limit of superheat deviation, then the angle of the air guide vane is increased to reduce the air volume; If the superheat deviation ΔSH is less than the preset lower limit of superheat deviation, then the angle of the air guide vane is reduced to increase the air volume; If the superheat deviation ΔSH is between the preset upper limit of superheat deviation and the preset lower limit of superheat deviation, the air guide vane maintains its current angle.

11. The control method according to claim 8, characterized in that, Also includes: After adjusting the angle of the air guide vane, the corresponding spacing compensation amount Δd is calculated based on the angle adjustment amount using a preset equivalent conversion coefficient. 补偿 And the spacing between the air guide vanes is compensated and adjusted; The equivalent conversion factor is the ratio of the influence rate of angle change on heat exchange to the influence rate of spacing change on heat exchange.

12. The control method according to claim 8, characterized in that, It also includes an adaptive initialization step: The operating conditions of the air conditioning unit where the heat exchange device is located are divided into multiple operating condition intervals; Record the angle and spacing of the air guide vanes when the air conditioning unit reaches a stable state under various operating conditions, and establish a memory database; When the air conditioning unit is turned on, it queries the memory database according to the current operating conditions. If a matching record is found, the air guide vane angle and spacing in the matching record are directly used as the initial adjustment position.

13. The control method according to claim 8, characterized in that, It also includes defrosting control steps: After the wind grid adjustment step has been cycled for a preset number of times, if the heat exchange capacity Q_i of the heat exchange module is less than the average heat exchange capacity Q_avg of all heat exchange modules, and the difference between the average heat exchange capacity and the heat exchange capacity Q_i is greater than the preset frosting judgment threshold, then the heat exchange module is marked as a frosting module, and the adjustment of the wind grid structure of the frosting module is stopped. When the number of marked frost modules reaches a preset threshold proportion of the total number of heat exchange modules, the air conditioning unit is controlled to enter defrosting mode.

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