Air conditioner outdoor unit

Abstract

The application relates to an air conditioner outdoor unit, belonging to the air conditioner technical field; the air conditioner outdoor unit comprises a machine shell, a condenser, a compressor, an axial flow fan, a driving motor and a wind guide ring arranged in the machine shell; the wind guide ring comprises an assembling part, an inlet part, a throat part and an outlet part; the assembling part is provided with a wind guide hole in the center; one side of the inlet part is connected with the outer edge of the wind guide hole in a smooth mode, the inner side wall of the inlet part is projected to the plane where the wind guide ring axis is located in an arc mode, and the center of the arc is outside the wind guide ring; one side of the throat part is connected with the side of the inlet part far from the assembling part in a smooth mode; one side of the outlet part is connected with the side of the throat part far from the inlet part in a smooth mode, and the inner side wall of the outlet part is also projected in an arc mode, and the center of the arc is outside the wind guide ring. The application solves the problems of large noise, high power consumption and insufficient air volume output caused by unreasonable matching of the wind guide ring and the fan in the prior art, and improves the overall performance of the air conditioner outdoor unit.

Description

Technical Field

[0001] This application relates to the field of air conditioning technology, and more particularly to an outdoor unit for an air conditioner. Background Technology

[0002] The outdoor unit of an air conditioner is the core equipment of the air conditioning system, responsible for heat exchange and refrigerant circulation. It integrates key components such as a compressor, condenser, cooling fan, refrigerant piping, gas-liquid separator, and four-way valve. The compressor provides power for the refrigerant circulation, compressing the low-pressure, low-temperature refrigerant into a high-pressure, high-temperature state. The condenser cools and condenses the high-pressure gaseous refrigerant by exchanging heat with the outdoor air. The cooling fan drives airflow to enhance the condenser's heat exchange efficiency. The refrigerant piping connects all components to form a closed loop, working together to achieve the cooling or heating function.

[0003] In the outdoor unit of an air conditioner, the fan and air guide ring constitute the core structural combination affecting airflow efficiency. The fan, mounted in the corresponding area of ​​the outdoor unit, drives air to flow axially through high-speed rotation, forming a forced airflow circulation that forces outside air to flow quickly across the condenser surface, accelerating the heat exchange process. The air guide ring, arranged in a surrounding pattern around the fan, directly determines the airflow guidance accuracy and rectification effect. By streamlining the airflow driven by the fan, it effectively regulates turbulent airflow, reduces local eddies, and lowers energy loss in the flow path, thereby improving overall airflow efficiency and providing crucial support for maintaining the condenser's high-efficiency heat exchange performance.

[0004] In existing technologies, the overall profile design of the air guide ring is poorly adapted to the airflow characteristics of the fan, exhibiting significant structural design flaws. Its surface curve fails to properly match the streamlines of the airflow driven by the fan, resulting in frequent turbulence such as impacts and separations throughout the airflow's passage through the air guide ring. This not only significantly increases airflow resistance and pressure loss, causing substantial energy waste, but also generates noticeable aerodynamic noise due to the intense airflow disturbances. This unreasonable structural design prevents the air guide ring from effectively performing its rectifying and guiding function, reducing the fan's air delivery efficiency and stability, thereby affecting the overall operating performance of the outdoor unit of the air conditioner and providing a poor user experience. Utility Model Content

[0005] This application provides an outdoor unit for an air conditioner, which aims to optimize the compatibility between the air guide ring and the axial fan to achieve smooth airflow guidance and reduce airflow separation and turbulence during the circulation process. This specifically solves the problems in the prior art caused by unreasonable matching between the air guide ring and the fan, such as high operating noise, excessive fan power consumption, and insufficient or unstable airflow output, thereby improving the overall performance and user experience of the outdoor unit for the air conditioner.

[0006] To achieve the above objectives, this application adopts the following technical solution: This application provides an outdoor unit for an air conditioner, including a housing, wherein the housing contains: Axial fan; A drive motor, used to drive the axial fan to rotate; An air guide ring is fitted around the outer periphery of the axial flow fan; wherein the air guide ring includes: The assembly section has an air guide hole at its center; The inlet is connected to the outer edge of the air guide hole of the assembly part on one side; when projected onto the plane where the axis of the air guide ring is located, the projection of the inner wall of the inlet is an arc shape, the center of the arc formed by the projection of the inner wall of the inlet is located outside the air guide ring, and the central angle corresponding to the arc formed by the projection of the inner wall of the inlet is in the range of 75°~90°. The throat, one side of which is connected to the side of the inlet portion away from the assembly portion; The outlet section has one side connected to the throat section away from the inlet section; when projected onto the plane containing the axis of the air guide ring, the projection of the inner wall of the outlet section is an arc shape, the center of the arc formed by the projection of the inner wall of the outlet section is located outside the air guide ring, and the central angle corresponding to the arc formed by the projection of the inner wall of the outlet section is in the range of 21°~27°. Specifically, when projecting onto the plane containing the axis of the air guide ring, the ratio between the radius of the arc formed by the projection of the inner wall of the outlet and the radius of the arc formed by the projection of the inner wall of the inlet is 1.6 to 2; the ratio between the radius of the arc formed by the projection of the inner wall of the outlet and the radius of the inner wall of the outlet on the side away from the throat is 0.16 to 0.17.

[0007] In this application, the inner walls of both the inlet and outlet sections of the air guide ring are arc-shaped on the projected plane, with the center of the arc located outside the air guide ring, thus matching the airflow characteristics of the axial fan. The airflow contracts along the inner wall of the inlet section and smoothly enters the throat, where it is then guided and diffused out along the inner wall of the outlet section. This reduces airflow impact, separation, and turbulence, lowering energy loss. It solves the problems of high noise, high power consumption, and insufficient airflow caused by improper matching between the air guide ring and the fan in existing technologies, thereby improving the overall performance of the outdoor unit of the air conditioner. Secondly, the central angle of the arc on the inner wall of the inlet is limited to 75°~90°, which allows the airflow to enter smoothly and reduces local resistance. If it is less than 75°, the excessive curvature will lead to increased airflow impact and resistance. The central angle of the arc on the inner wall of the outlet is limited to 21°~27°, which guides the orderly diffusion of airflow. If it is greater than 27°, it will cause separation and noise due to excessive expansion, while if it is less than 21°, insufficient diffusion will lead to turbulent flow. Optimizing the inlet and outlet angles makes the airflow smoother, reduces noise and power consumption, ensures stable air volume and uniform downstream airflow, and is beneficial to condenser heat exchange. Furthermore, the ratio of the inner wall radius of the outlet to that of the inlet is limited to 1.6~2, balancing the airflow characteristics at both the inlet and outlet, optimizing outlet diffusion while avoiding insufficient inlet volume. The ratio of the inner wall radius of the outlet to that of the inner wall on the side of the outlet furthest from the throat is limited to 0.16~0.17, matching the outlet expansion scale with the airflow diffusion capacity, avoiding energy loss caused by excessive steepness or over-expansion, and further optimizing the outlet aerodynamic performance.

[0008] In some embodiments of this application, the housing is connected to a fan shroud frame via a positioning post. The fan shroud frame is located on one side of the airflow discharge direction of the axial fan, and an air outlet shroud is provided inside the fan shroud frame. The drive motor is mounted inside the housing via a motor bracket, which is located on the side of the axial fan away from the fan cover frame.

[0009] In the above embodiments, this application connects the fan shroud frame to the housing using positioning posts, positioning it in the direction of the axial fan's airflow discharge. Simultaneously, the drive motor is mounted on the side of the axial fan away from the fan shroud frame via a motor bracket, clearly defining the relative positional relationships between the fan shroud frame, the motor bracket, the axial fan, and the air guide ring. The fan shroud frame provides support for the exhaust fan shroud, which in turn protects the axial fan. The motor bracket provides stable support for the drive motor and the axial fan, ensuring the coaxiality and relative positional accuracy of the axial fan and the air guide ring. This avoids airflow turbulence caused by installation misalignment and further guarantees the smooth airflow guidance effect of the air guide ring, laying a structural foundation for subsequent optimization of the matching relationship between the air guide ring and the fan.

[0010] In some embodiments of this application, a notch is provided at each apex corner of the assembly part, and the positioning post passes through the notch.

[0011] In the above embodiments, the notch at the apex of the assembly part of this application is used to avoid the positioning post, making the air guide ring fit more snugly with the housing and reducing airflow leakage or vibration transmission problems caused by excessive assembly gaps. This design ensures that the air guide ring is stable in position during operation, avoids profile deviation caused by assembly interference, and thus ensures that the profile design of the inlet, throat, and outlet can continuously play a guiding role, maintain the smoothness of airflow, and indirectly reduce noise and energy loss caused by structural instability.

[0012] In some embodiments of this application, the ratio between the minimum diameter of the inner wall of the throat and the diameter of the axial fan is 1.03 to 1.04.

[0013] In the above embodiments, the ratio of the minimum diameter of the inner wall of the throat to the diameter of the axial fan is limited to 1.03 to 1.04. This ratio ensures that the throat channel and the flow field at the fan blade tip are highly matched, which avoids airflow blockage caused by the channel being too narrow and prevents airflow leakage caused by the channel being too wide, thus ensuring stable airflow in the throat.

[0014] In some embodiments of this application, the ratio between the height of the throat and the height of the air guide ring is 0.24 to 0.26.

[0015] In the above embodiments, the ratio of throat height to guide ring height is limited to 0.24~0.26. This design makes the throat height moderate, which guides the airflow to achieve a smooth transition with sufficient height and reduces flow disturbance; it also avoids the formation of vortices by the airflow detaching from the wall due to an excessively long throat, thereby reducing local energy loss and aerodynamic noise.

[0016] In some embodiments of this application, the axial fan includes a hub and a plurality of fan blades arranged circumferentially along the hub, the fan blades including blade tips and blade apexes; The vertical distance between the side of the air guide ring closest to the motor bracket and the blade tip is 15mm to 20mm.

[0017] In the above embodiments, this application limits the vertical distance between the side of the air guide ring closest to the motor bracket and the blade tip to 15mm~20mm. This design clearly defines the relative positional relationship between the air guide ring and the fan blade tip. A reasonable spacing setting reduces airflow leakage and secondary flow losses between the blade tip and the air guide ring, and also avoids structural interference between the two, ensuring smooth airflow along the air guide ring inlet. Therefore, the compatibility between the air guide ring and the axial fan is further improved, energy loss during airflow is reduced, and operating noise is lowered.

[0018] In some embodiments of this application, the vertical distance between the side of the air guide ring closest to the motor bracket and the motor bracket is 90 mm to 95 mm.

[0019] In the above embodiments, this application limits the vertical distance between the side of the air guide ring closest to the motor bracket and the motor bracket to 90mm~95mm. This design clarifies the relative positional relationship between the air guide ring and the motor bracket. A reasonable spacing setting avoids structural interference between the two, ensuring that airflow can smoothly enter along the inlet of the air guide ring. Therefore, the compatibility between the air guide ring and the axial fan is further improved, energy loss during airflow is reduced, and operating noise is lowered. Simultaneously, under constant speed conditions, the airflow output is significantly increased, and input power consumption is reduced, achieving an overall improvement in system efficiency.

[0020] In some embodiments of this application, the vertical distance between the side of the air guide ring near the air cover frame and the side of the air cover frame near the air guide ring is 48 mm to 53 mm.

[0021] In the above embodiments, the vertical distance between the side of the air guide ring closest to the shroud frame and the shroud frame is 48mm-53mm, optimizing the relative position between the air guide ring outlet and the shroud frame. This design ensures that the airflow at the air guide ring outlet can flow smoothly out of the outdoor unit, reducing the diffusion resistance of the airflow at the outlet, while avoiding airflow disturbance caused by unreasonable spacing between the blade tip and the air guide ring, further improving the stability of airflow output and system efficiency.

[0022] In some embodiments of this application, the vertical distance between the air guide ring on the side near the wind shield frame and the blade tip is 20 mm to 25 mm.

[0023] In the above embodiments, the vertical distance between the side of the air guide ring closest to the fan housing frame and the blade tip is 20mm~25mm, optimizing the relative position between the air guide ring outlet and the fan blade tip. This design ensures that the airflow at the air guide ring outlet can flow smoothly out of the outdoor unit, reducing the diffusion resistance of the airflow at the outlet, while avoiding airflow disturbance caused by unreasonable spacing between the blade tip and the air guide ring, further improving the stability of airflow output and system efficiency.

[0024] In some embodiments of this application, the vertical distance between the side of the wheel hub closest to the drive motor and the motor bracket is 125 mm to 130 mm.

[0025] The vertical distance between the side of the hub closest to the drive motor and the motor bracket is limited to 125mm~130mm. This design optimizes the axial positional relationship between the fan and the air guide ring, which not only ensures the dynamic balance of the fan during rotation and reduces noise caused by vibration, but also ensures that the airflow continuously matches the air guide ring profile and maintains smooth flow. This significantly improves the air volume output under constant speed conditions, while reducing input power consumption, achieving an overall improvement in system efficiency, and ultimately enhancing the operational stability and comprehensive performance of the outdoor unit of the air conditioner.

[0026] It should be understood that the above general description and the following detailed description are exemplary and explanatory only, and do not limit this application. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0028] Figure 1 This is a schematic diagram of the overall structure of the outdoor unit of the air conditioner provided in the embodiment of this application; Figure 2 This is a schematic diagram of the overall structure of the outdoor unit (hidden air outlet cover) of the air conditioner provided in the embodiment of this application; Figure 3 This is a schematic diagram of the overall structure of the outdoor unit (hidden part of the outer casing) of the air conditioner provided in the embodiment of this application; Figure 4 yes Figure 3 Enlarged view of part A in the image; Figure 5 This is a front-view schematic diagram of the outdoor unit (hidden part of the casing) of an air conditioner provided in an embodiment of this application; Figure 6 This is a side view schematic diagram of the outdoor unit (hidden part of the casing) of an air conditioner provided in an embodiment of this application; Figure 7 This is a three-dimensional schematic diagram of the air guide ring and axial fan provided in the embodiments of this application; Figure 8 This is a front-view schematic diagram of the air guide ring and axial fan provided in the embodiments of this application; Figure 9 This is a top-view schematic diagram of the air guide ring and axial fan provided in the embodiments of this application; Figure 10 yes Figure 9 Schematic diagram of the BB cross section; Figure 11 This is a top-view schematic diagram of the air guide ring and axial fan provided in the embodiments of this application; Figure 12 This is a top-view schematic diagram of an axial fan provided in an embodiment of this application; Figure 13 This is a front-view schematic diagram of the air guide ring provided in an embodiment of this application; Figure 14 This is a top-view schematic diagram of the air guide ring provided in the embodiment of this application; Figure 15 yes Figure 14 Schematic diagram of CC section in the image; Figure 16 This is a comparison diagram of the airflow-power of the embodiments of this application and existing air guide rings; Figure 17 This is a comparison diagram of airflow and noise between the embodiment of this application and existing air guide rings.

[0029] In the above figures: a represents the width of the assembly part, and b represents the length of the assembly part; Projecting onto the plane containing the guide vane axis, θ1 represents the central angle corresponding to the arc formed by the projection of the inner wall of the inlet, θ2 represents the central angle corresponding to the arc formed by the projection of the inner wall of the outlet, R4 represents the radius of the arc formed by the projection of the inner wall of the outlet, and R5 represents the radius of the arc formed by the projection of the inner wall of the inlet. R represents the diameter of the axial fan, R1 represents the minimum diameter of the inner wall of the throat, R2 represents the radius of the inner wall of the outlet on the side away from the throat (i.e., the inner radius at the outlet of the air guide ring), and R3 represents the radius of the outer wall of the outlet on the side away from the throat (i.e., the outer radius at the outlet of the air guide ring). H represents the height of the air guide ring, H1 represents the height of the assembly section, H2 represents the height of the throat, S represents the vertical distance between the side of the shroud frame facing the air guide ring and the side of the motor bracket facing the air guide ring, S1 represents the vertical distance between the side of the air guide ring near the shroud frame and the blade tip, S2 represents the vertical distance between the side of the air guide ring near the motor bracket and the blade tip, S3 represents the vertical distance between the side of the air guide ring near the shroud frame and the side of the shroud frame near the air guide ring, S4 represents the vertical distance between the side of the air guide ring near the motor bracket and the motor bracket, and S5 represents the vertical distance between the side of the hub 310 near the drive motor and the motor bracket.

[0030] In the above figures: 100, housing; 110, motor bracket; 120, positioning post; 130, fan shroud frame; 131, air outlet shroud; 140, air outlet; 200, drive motor; 300, axial fan; 310, hub; 320, fan blade; 321, blade tip; 322, blade tip; 400, air guide ring; 410, assembly part; 411, notch; 412, positioning hole; 420, inlet; 430, throat; 440, outlet; 450, airflow channel. Detailed Implementation

[0031] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application. In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between components; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication between two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0032] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0033] In this application, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0034] Additionally, if the meaning of "and / or" in the text is that it includes three parallel options, taking "A and / or B" as an example, it includes option A, option B, or an option that satisfies both A and B.

[0035] The present application will now be described in detail through exemplary embodiments. However, it should be understood that, without further description, elements, structures, and features in one embodiment may be advantageously incorporated into other embodiments.

[0036] The outdoor unit of an air conditioner, as the core device for heat exchange and refrigerant circulation in an air conditioning system, integrates important components such as a compressor, condenser, cooling fan, refrigerant piping, gas-liquid separator, and four-way valve. Within the outdoor unit, the fan and air guide ring form a crucial structure affecting airflow efficiency. The fan, installed in the outdoor unit, drives air axially through high-speed rotation, creating forced airflow circulation and propelling outside air rapidly across the condenser surface, accelerating heat exchange. The air guide ring, surrounding the fan, plays a decisive role in guiding and rectifying the airflow. By streamlining the fan-driven airflow, it regulates turbulent airflow, reduces local eddies, and minimizes energy loss during circulation, thereby improving overall airflow efficiency and providing crucial support for maintaining the condenser's high-efficiency heat exchange performance. However, existing technologies have significant shortcomings in the matching between the fan and the air guide ring. On the one hand, the structural parameters between the air guide ring and the fan blades, such as gaps, profiles, and relative positions, are not adequately matched, causing airflow to easily separate, form eddies, and become turbulent when passing through the air guide ring, resulting in significant aerodynamic noise. On the other hand, improper matching can cause airflow leakage and energy loss, requiring the fan to consume more power to maintain the required airflow, thus reducing the overall energy efficiency of the system. Simultaneously, uneven airflow distribution affects the fan's effective air delivery capacity, leading to insufficient or unstable airflow output, ultimately resulting in a decline in air conditioning performance.

[0037] Based on this, this application proposes an outdoor air conditioning unit. By optimizing the structural design of the air guide ring 400, the inlet 420 and outlet 440 of the air guide ring 400 are set as arcs. By reasonably controlling the size of the throat 430 of the air guide ring 400, the ratio of the central angle to the radius of the inlet and outlet arcs, and the relative position parameters of the air guide ring 400 with components such as the axial fan 300, the fan cover frame 130, and the motor bracket 110, the airflow is smoothly contracted, stably guided, and orderly diffused along the inner wall of the air guide ring 400. This solves the problems of high noise, high power consumption, and insufficient air volume output caused by unreasonable matching between the air guide ring 400 and the fan in the prior art.

[0038] In the following, embodiments of this application will be described in detail with reference to the accompanying drawings.

[0039] As attached Figures 1 to 15 As shown in an illustrative embodiment of this application, the outdoor unit of the air conditioner includes a housing 100, wherein the side of the housing 100 facing the ground is the bottom of the outdoor unit of the air conditioner, and the side away from the ground is its top; in addition, the top or bottom of the housing 100 and the components inside the housing 100 are the same as the top or bottom of the outdoor unit of the air conditioner, which is the same throughout the text and will not be repeated.

[0040] To clearly illustrate the specific structure of this application, the following description uses a top-discharge air conditioner outdoor unit as an example; however, it should be noted that the 400-type air guide ring and positional constraint relationship disclosed in this application are not limited to top-discharge air conditioner outdoor units, and can also be applied to side-discharge air conditioner outdoor units or other types of air conditioner outdoor units without creative effort.

[0041] In some embodiments, a compressor is provided inside the housing 100; the compressor is a gas pressurization device used to compress the refrigerant from a low-pressure and low-temperature state to a high-pressure and high-temperature state; the compressor compresses the incoming low-pressure gaseous refrigerant by driving internal moving parts (such as pistons, rotors, scrolls, etc.) to make mechanical movements through a motor, so as to convert it into a high-pressure gaseous refrigerant. The specific process mainly includes three typical stages: intake, compression, and exhaust.

[0042] It is worth noting that the refrigerant mentioned in this application (also known as a refrigerant, such as R32, R410A, etc.) is a medium for heat transfer, and the same applies throughout the application, so it will not be repeated here.

[0043] In cooling mode, the air conditioner transfers indoor heat to the outdoor unit. The refrigerant circulation path is: indoor heat exchanger (evaporator) → gas-liquid separator → compressor → outdoor heat exchanger (condenser) → throttling device → indoor heat exchanger (evaporator). Specifically, in the indoor heat exchanger, low-pressure liquid refrigerant absorbs indoor heat and evaporates into low-pressure, low-temperature gaseous refrigerant. This gaseous refrigerant returns to the outdoor unit via a low-pressure pipeline, first passing through a gas-liquid separator to filter out residual liquid components before entering the compressor. The compressor compresses this gaseous refrigerant into high-pressure, high-temperature gaseous refrigerant, which is then discharged into the outdoor heat exchanger via a high-pressure pipeline. There, it releases heat through heat exchange with outdoor air driven by a fan, condensing into high-pressure, medium-temperature liquid refrigerant. Subsequently, the pressure is reduced to a low-pressure gas-liquid mixture by the throttling device before re-entering the indoor heat exchanger, completing the cycle.

[0044] In heating mode, the air conditioner switches the refrigerant flow direction through a four-way valve to transfer outdoor heat to the indoor unit. The circulation path is: outdoor heat exchanger (evaporator) → gas-liquid separator → compressor → indoor heat exchanger (condenser) → throttling device → outdoor heat exchanger (evaporator). Specifically, the four-way valve switches, temporarily turning the outdoor heat exchanger into an evaporator. The low-pressure liquid refrigerant absorbs heat from the outdoor air and evaporates into a low-pressure, low-temperature gaseous refrigerant, which is then filtered by the gas-liquid separator and enters the compressor. The high-pressure, high-temperature gaseous refrigerant compressed by the compressor is sent to the indoor heat exchanger (temporarily acting as a condenser) through a high-pressure pipeline, where it releases heat through heat exchange with the indoor air (heating the indoor air) and condenses into a high-pressure, medium-temperature liquid refrigerant. Subsequently, the pressure is reduced to a low-pressure gas-liquid mixture by the throttling device and returns to the outdoor heat exchanger, completing the cycle.

[0045] It should be noted that the specific structure of the compressor (including the compressor's motor, cylinder, piston and other core components, as well as the connection relationship between the suction valve, exhaust valve and gas-liquid separator) and the compressor's operating principle (such as the process of achieving the suction-compression-exhaust cycle by driving the internal components to rotate / reciprocate through the motor, compressing the low-pressure, low-temperature gaseous refrigerant into a high-pressure, high-temperature gaseous refrigerant, etc.) are all prior art, and their technical details are well known to those skilled in the art. Therefore, they need not be described in detail in this application.

[0046] In some embodiments, a condenser is provided inside the casing 100. The condenser is used for heat exchange between the refrigerant and the outdoor air. Its main body is composed of multiple sets of parallel copper (or aluminum) heat exchange tubes and dense metal heat dissipation fins (usually aluminum fins). The heat exchange tubes are inserted into and fixed in the preset holes of the fins to form a tube-fin integrated heat exchange matrix. At the same time, the condenser is fixed inside the outdoor unit casing 100 by a bracket, and an air circulation channel is reserved on the side corresponding to the cooling fan. Some condensers are also provided with manifolds at the pipe inlet and outlet (for collecting / distributing refrigerant) to ensure that the refrigerant can flow evenly through each heat exchange tube, and finally achieve efficient heat exchange between the refrigerant and the outdoor air.

[0047] It should be noted that the specific structure of the condenser (including the copper / aluminum heat exchange tubes, metal heat dissipation fins, manifolds, and other components, as well as the connection relationship between the condenser inlet and compressor outlet pipes, and between the condenser outlet and throttling component pipes) and the operating principle of the condenser (such as transferring heat from the high-pressure, high-temperature gaseous refrigerant to the outdoor air through the heat exchange tubes and fins during cooling, causing the refrigerant to condense into a high-pressure liquid state; and switching to evaporator function during heating, absorbing heat from the outdoor air through the heat exchange tubes and fins, causing the refrigerant to evaporate into a low-pressure gaseous state, etc.) are all prior art, and their technical details are well known to those skilled in the art. Therefore, they need not be elaborated upon in this application.

[0048] In some embodiments, an axial fan 300 is provided inside the housing 100, and the axial fan 300 is arranged inside the housing 100 in conjunction with the condenser. Specifically, the axial fan 300 is located at the top of the housing 100, and an air outlet 140 is correspondingly provided at the top of the housing 100. The core function of the axial fan 300 is to drive outdoor air to flow directionally along the heat exchange surface of the condenser (e.g., the outer wall of the fins and heat exchange tubes) through its own operation, and finally cause the air to be discharged from the air outlet 140 at the top of the housing 100. By forcing airflow, heat on the heat exchange surface of the condenser can be quickly removed (in cooling mode) or the transfer of outdoor air heat to the condenser can be accelerated (in heating mode), thereby accelerating the heat exchange rate between the refrigerant inside the condenser and the outdoor air, improving the heat exchange efficiency of the condenser, and ensuring the stable and efficient operation of the air conditioning system's cooling or heating functions.

[0049] Furthermore, in order to better adapt to the air guide ring 400 disclosed in this application, the diameter of the axial fan 300 is between 740 mm and 750 mm, and the blade height is between 215 mm and 230 mm.

[0050] In some embodiments, a drive motor 200 is provided inside the housing 100. The output shaft of the drive motor 200 is connected to the axial fan 300 through a bushing. The drive motor 200 is used to drive the axial fan 300 to rotate.

[0051] Furthermore, the bushing diameter is 23mm.

[0052] In some embodiments, a guide ring 400 is provided inside the housing 100. The guide ring 400 is sleeved on the outer periphery of the axial fan 300 and is coaxial with the axial fan 300. The guide ring 400 guides the airflow, making the airflow direction more regular and reducing the energy loss of the airflow.

[0053] In some embodiments, the air guide ring 400 is disposed on the sheet metal parts on both sides of the motor bracket 110, connected by screws, with a certain gap allowance to avoid vibration transmission caused by excessively small assembly gap.

[0054] In some embodiments, the air guide ring 400 is arranged along the airflow discharge direction and includes an assembly part 410, an inlet part 420, a throat part 430 and an outlet part 440, which are integrally formed.

[0055] In some embodiments, the assembly part 410 provides support for the overall structure of the air guide ring 400, and an air guide hole is provided at the center of the assembly part 410.

[0056] In some embodiments, one side of the inlet 420 is smoothly connected to the outer edge of the air guide hole of the assembly 410; when projected onto the plane containing the axis of the air guide ring 400, the projection of the inner sidewall of the inlet 420 is arc-shaped, and the center of the arc-shaped projection is located outside the air guide ring 400.

[0057] In some embodiments, one side of the throat 430 is smoothly connected to the side of the inlet 420 away from the assembly part 410.

[0058] In some embodiments, one side of the outlet 440 is smoothly connected to the side of the throat 430 away from the inlet 420; the projection of the inner wall of the outlet 440 onto the plane containing the axis of the guide ring 400 is arc-shaped, and the center of the arc-shaped projection is located outside the guide ring 400.

[0059] The axial fan 300 drives the airflow, which gradually contracts along the inner wall of the inlet 420 and smoothly enters the throat 430. It flows steadily along the throat 430 and then flows to the outlet 440, gradually spreading along the inner wall of the outlet 440, and finally exits the air guide ring 400.

[0060] Specifically, the projections of the inner walls of the inlet 420 and outlet 440 of the air guide ring 400 in this application are both arc-shaped with the center located outside the air guide ring 400. This profile design is more compatible with the airflow characteristics of the axial fan 300. The airflow gradually contracts along the inner wall of the inlet 420 and smoothly enters the throat 430. After being stably guided by the throat 430, it gradually diffuses and exits along the inner wall of the outlet 440. This process reduces airflow impact, separation, and turbulence. Because the airflow is smoother and energy loss is reduced, the fan does not need to consume too much power to maintain the required airflow, thus solving the problems of high noise, high power consumption, and insufficient airflow output caused by the unreasonable matching between the air guide ring 400 and the fan in the prior art, and improving the overall performance of the outdoor unit of the air conditioner.

[0061] In some embodiments, such as Figures 3-6 As shown, the housing 100 is connected to the fan shroud frame 130 via the positioning post 120. The fan shroud frame 130 is located on the top of the housing 100, that is, the fan shroud frame 130 is located on one side of the airflow discharge direction of the axial fan 300. The air outlet 140 of the housing 100 is located between the fan shroud frames 130. An air outlet shroud 131 is provided inside the fan shroud frame 130. The air outlet shroud 131 is used to protect the axial fan 300.

[0062] Furthermore, four positioning posts 120 are used in total.

[0063] In some embodiments, the drive motor 200 is disposed inside the housing 100 via a motor bracket 110, which is located on the side of the axial fan 300 away from the fan cover frame 130; specifically, the drive motor 200 is located directly below the axial fan 300, and the motor bracket 110 is located directly below the drive motor 200.

[0064] Specifically, this application connects the fan shroud frame 130 to the housing 100 via the positioning post 120, positioning it in the direction of the airflow discharge of the axial fan 300. Simultaneously, the drive motor 200 is positioned on the side of the axial fan 300 away from the fan shroud frame 130 via the motor bracket 110, clearly defining the relative positional relationship between the fan shroud frame 130, the motor bracket 110, the axial fan 300, and the air guide ring 400. The fan shroud frame 130 provides support for the outlet fan shroud 131, which protects the axial fan 300. The motor bracket 110 provides stable support for the drive motor 200 and the axial fan 300, ensuring the coaxiality and relative positional accuracy of the axial fan 300 and the air guide ring 400. This avoids airflow turbulence caused by installation misalignment and further guarantees the smooth airflow guidance effect of the air guide ring 400, laying a structural foundation for subsequent optimization of the matching relationship between the air guide ring 400 and the fan.

[0065] In some embodiments, such as Figure 11 As shown, the projection of the assembly part 410 onto a plane perpendicular to the axis of the air guide ring 400 is rectangular, and the assembly part 410 is fixed to the top of the housing 100.

[0066] In some embodiments, each of the top corners of the assembly part 410 is provided with a notch 411, through which the positioning post 120 passes, and the notch 411 is used to avoid the positioning post 120.

[0067] Furthermore, each side of the assembly part 410 is provided with a notch 411 at both ends.

[0068] Furthermore, the projection onto a plane perpendicular to the axis of the air guide ring 400 results in a rectangular projection shape for the notch 411.

[0069] Furthermore, the vertical distance between the side of the assembly part 410 and the bottom of the notch 411 opened on this side is 4 mm to 8 mm.

[0070] Specifically, the notch 411 at the apex of the assembly section 410 in this application is used to avoid the positioning post 120, making the assembly of the air guide ring 400 and the housing 100 more closely fit, reducing airflow leakage or vibration transmission problems caused by excessive assembly gaps. This design ensures that the air guide ring 400 is stable in position during operation, avoiding profile deviation caused by assembly interference, thereby ensuring that the profile design of the inlet section 420, throat section 430, and outlet section 440 can continuously play a guiding role, maintaining smooth airflow, and indirectly reducing noise and energy loss caused by structural instability.

[0071] In some embodiments, the height H1 of the assembly part 410 is 45 mm in the direction of airflow discharge.

[0072] In some embodiments, such as Figure 11As shown, the ratio of the length b to the width a of the assembly part 410 is 1.14.

[0073] In some embodiments, such as Figure 11 As shown, two positioning holes 412 are provided near each of the four corners of the assembly part 410. There are a total of eight positioning holes 412, and the diameter of each positioning hole 412 is 6 mm. The positioning holes 412 are used to assist in the assembly of the air guide ring 400.

[0074] In some embodiments, such as Figure 15 As shown, when the plane containing the axis of the guide ring 400 is projected, the central angle θ1 corresponding to the arc formed by the projection of the inner wall of the inlet 420 is 75°. The arc shape at this angle allows the airflow to enter the guide ring 400 in a relatively gentle flow state, reducing the impact force between the airflow and the inner wall of the inlet 420, reducing local resistance, thereby reducing the energy loss of the airflow in the inlet stage, and laying the foundation for the stable flow of the subsequent airflow in the throat 430. In some embodiments, such as Figure 15 As shown, when the plane containing the axis of the guide vane 400 is projected, the central angle θ1 corresponding to the arc formed by the projection of the inner sidewall of the inlet 420 is 90°. In some embodiments, such as Figure 15 As shown, when the plane containing the axis of the guide vane 400 is projected, the central angle θ2 corresponding to the arc formed by the projection of the inner sidewall of the outlet 440 is 21°. This arc shape can guide the airflow to diffuse fully at the outlet of the guide vane 400, while avoiding turbulence in the downstream flow field. In some embodiments, such as Figure 15 As shown, when the plane containing the axis of the guide ring 400 is projected, the central angle θ2 corresponding to the arc formed by the projection of the inner sidewall of the outlet 440 is 27°. The arc design at this angle ensures that the airflow is fully diffused at the outlet of the guide ring 400 while avoiding airflow separation.

[0075] In some embodiments, such as Figure 15 As shown, when the plane containing the axis of the guide vane 400 is projected, the central angle θ1 corresponding to the arc formed by the projection of the inner wall of the inlet 420 is in the range of 75°~90°, and / or the central angle θ2 corresponding to the arc formed by the projection of the inner wall of the outlet 440 is in the range of 21°~27°.

[0076] Specifically, this application limits the central angle θ1 of the arc of the inner sidewall of the inlet 420 of the guide ring 400 to 75°~90°. The arc shape within this angle range allows the airflow to transition more smoothly when entering the guide ring 400, which can effectively reduce local resistance and avoid excessive airflow impact. If the central angle θ1 of the arc of the inner sidewall of the inlet 420 is less than 75°, the arc curvature is too large and the inlet section contracts too quickly. A large amount of high-speed airflow will directly hit the inner sidewall of the inlet of the guide ring 400, causing a significant increase in local resistance, disrupting the smooth entry of the airflow, and even forming vortices that lead to energy loss.

[0077] Meanwhile, the central angle θ2 of the inner wall arc of the outlet section 440 is limited to 21°~27°. This angle design can guide the airflow to diffuse orderly along the arc shape at the outlet, avoiding airflow separation caused by unreasonable expansion angle, and reducing pressure loss and flow separation. If the central angle θ2 of the inner wall arc of the outlet section 440 is greater than 27°, the expansion angle of the outlet section is too large, which will cause the airflow to suddenly expand at the outlet due to inertia and fail to adhere to the wall surface, resulting in increased pressure loss and flow separation, aggravating energy loss. At the same time, the turbulent airflow will generate greater noise and reduce the aerodynamic performance of the guide ring 400. If the central angle θ2 of the inner wall arc of the outlet section 440 is less than 21°, the expansion angle of the outlet section is too small, which will cause insufficient diffusion of the airflow at the outlet, resulting in turbulent downstream flow field, reducing the aerodynamic performance of the guide ring 400, and indirectly increasing system energy consumption.

[0078] By optimizing the inlet and outlet fillet angles, the airflow at the 400mm inlet and outlet of the air guide ring is smoother, turbulence dissipation is reduced, which in turn reduces aerodynamic noise, reduces fan power consumption, improves the stability of airflow output, and ensures the uniformity of the downstream airflow field, providing favorable conditions for efficient heat exchange of the condenser.

[0079] In some embodiments, such as Figure 15 As shown, when projecting onto the plane containing the axis of the guide vane 400, the ratio between the radius R4 of the arc formed by the projection of the inner wall of the outlet 440 and the radius R5 of the arc formed by the projection of the inner wall of the inlet 420 is 1.6. Under this ratio, the increase in the radius R4 of the inner wall of the outlet 440 relative to that of the inlet 420 is moderate. This allows the outlet 440 to effectively guide the airflow to diffuse slowly, reducing flow separation and local resistance at the outlet. It also prevents the radius of the inner wall of the inlet 420 from being excessively compressed due to the proportional relationship, resulting in insufficient inlet flow volume. Thus, while reducing separation losses, it ensures a stable airflow output.

[0080] In some embodiments, such as Figure 15As shown, when projecting onto the plane containing the axis of the guide vane 400, the ratio between the radius R4 of the arc formed by the projection of the inner wall of the outlet 440 and the radius R5 of the arc formed by the projection of the inner wall of the inlet 420 is 2. Under this ratio, the radius R4 of the arc on the inner wall of the outlet 440 is increased to a certain extent, which can further optimize the diffusion effect of the airflow at the outlet, reduce energy loss caused by poor airflow diffusion, and help increase airflow. At the same time, although the radius R5 of the arc on the inner wall of the inlet 420 is relatively small, it still meets the basic requirements for airflow entry and will not cause a significant decrease in airflow due to excessively small area, thus achieving a balance between optimized outlet diffusion and inlet flow capacity.

[0081] In some embodiments, such as Figure 15 As shown, when projecting onto the plane containing the axis of the guide vane 400, the radius R4 of the arc formed by the projection of the inner wall of the outlet 440 is 0.16 compared to the radius R2 of the inner wall of the outlet 440 on the side away from the throat 430. This ratio ensures a reasonable match between the arc radius R4 of the inner wall of the outlet 440 and the radius R2 of the inner wall of the outlet 440 on the side away from the throat 430. The profile design of the outlet 440 guides the airflow to diffuse at a suitable angle, avoiding airflow congestion caused by insufficient diffusion angle due to an excessively small ratio. This ensures smooth airflow at the outlet 440 and reduces turbulent dissipation.

[0082] In some embodiments, such as Figure 15 As shown, when projecting onto the plane containing the axis of the guide vane 400, the radius R4 of the arc formed by the projection of the inner wall of the outlet 440 is 0.17 compared to the radius R2 of the inner wall of the outlet 440 on the side away from the throat 430. At this ratio, the radius R4 of the arc of the inner wall of the outlet 440 is slightly increased, which allows for smoother airflow diffusion at the outlet 440, further reducing airflow separation at the outlet, lowering local resistance, and helping to improve airflow discharge efficiency. Simultaneously, it avoids power and noise increases due to excessive expansion, maintaining the system's efficient and stable operation.

[0083] In some embodiments, such as Figure 15 As shown, when projecting onto the plane containing the axis of the guide vane 400, the ratio between the radius R4 of the arc formed by the projection of the inner wall of the outlet 440 and the radius R5 of the arc formed by the projection of the inner wall of the inlet 420 is 1.6 to 2; and / or, the ratio between the radius R4 of the arc formed by the projection of the inner wall of the outlet 440 and the radius R2 of the inner wall of the outlet 440 on the side away from the throat 430 is 0.16 to 0.17.

[0084] Specifically, this application limits the ratio of the arc radius R4 formed by the projection of the inner wall of the outlet 440 to the arc radius R5 formed by the projection of the inner wall of the inlet 420 to 1.6~2. This range is set based on the need for balancing the characteristics of the inlet and outlet airflow. Specifically, while increasing the arc radius R5 formed by the projection of the inner wall of the inlet 420 can reduce inlet flow separation and turbulence loss, and reduce power and noise, an excessively large arc radius R5 of the inner wall of the inlet 420 will reduce the inlet flow volume, resulting in a decrease in airflow. On the other hand, a moderate increase in the arc radius R4 formed by the projection of the inner wall of the outlet 440 can guide the airflow to diffuse slowly, reduce outlet separation and local resistance, and increase airflow. However, an excessively large arc radius R4 of the inner wall of the outlet 440 may cause new energy losses due to excessive expansion, or even increase power and noise due to excessive increase in airflow. By controlling the ratio of the arc radius R4 formed by the projection of the inner wall of the outlet section 440 to the arc radius R5 formed by the projection of the inner wall of the inlet section 420 at 1.6~2, it is possible to ensure that the arc radius R4 of the inner wall of the outlet section 440 is reasonably increased relative to the arc radius R5 of the inner wall of the inlet section 420 to optimize the outlet diffusion effect, while avoiding the insufficient inlet volume caused by the excessive compression of the arc radius R5 of the inner wall of the inlet section 420 due to the proportional relationship. This achieves a balance between reducing separation loss and maintaining stable air volume.

[0085] The ratio of the inner arc radius R5 of the outlet section 440 to the inner arc radius R2 of the side of the outlet section 440 away from the throat 430 is limited to 0.16~0.17. The rationale for this ratio is to match the scale of the outlet expansion with the airflow diffusion capacity. If the ratio is too small, the inner arc radius R5 of the outlet section 440 is insufficient relative to the inner arc radius R2 of the side of the outlet section 440 away from the throat 430, resulting in an overly steep transition of the outlet rounding, which can easily lead to airflow separation and pressure loss. If the ratio is too large, the inner arc radius R5 of the outlet section 440 approaches or exceeds the reasonable proportion of the inner arc radius R2 of the side of the outlet section 440 away from the throat 430, which will lead to excessive expansion of the outlet channel, disrupting the stable diffusion state of the airflow and increasing energy loss. By controlling the ratio between 0.16 and 0.17, it can be ensured that the rounded outlet can provide sufficiently smooth diffusion guidance for the airflow without interfering with the mainstream field due to excessive expansion. This not only increases the air volume but also avoids the increase in power and noise due to the intensification of turbulence, further optimizing the aerodynamic performance of the outlet area.

[0086] In some embodiments, such as Figure 12 , 15 As shown, the ratio between the minimum diameter R1 of the inner wall of the throat 430 and the diameter R of the axial fan 300 is 1.03. This ratio ensures that the flow field of the throat 430 channel is highly matched with that of the fan blade tip 320, which avoids airflow blockage caused by the channel being too narrow and ensures stable airflow in the throat 430.

[0087] In some embodiments, such as Figure 12 , 15 As shown, the ratio between the minimum diameter R1 of the inner wall of the throat 430 and the diameter R of the axial fan 300 is 1.04. This ratio ensures that the flow field of the throat 430 channel is highly matched with that of the fan blade tip 320, avoiding both airflow blockage caused by an excessively narrow channel and airflow leakage caused by an excessively wide channel.

[0088] In some embodiments, such as Figure 12 , 15 As shown, the ratio between the minimum diameter R1 of the inner wall of the throat 430 and the diameter R of the axial fan 300 is 1.03~1.04.

[0089] Specifically, the ratio of the minimum diameter of the inner wall of the throat 430 to the diameter of the axial fan 300 is limited to 1.03 to 1.04. This ratio ensures that the flow field of the throat 430 channel is highly matched with that of the fan blade tip 320, which avoids airflow blockage caused by the channel being too narrow and prevents airflow leakage caused by the channel being too wide, thus ensuring stable airflow in the throat 430.

[0090] In some embodiments, such as Figure 15 As shown, along the airflow discharge direction, the ratio between the height H2 of the throat 430 and the height H of the guide ring 400 is 0.24. This design ensures that the throat 430 height H2 is moderate, guiding the airflow smoothly with sufficient height and reducing flow disturbance.

[0091] In some embodiments, such as Figure 15 As shown, along the airflow discharge direction, the ratio between the height H2 of the throat 430 and the height H of the guide ring 400 is 0.26. This design ensures that the height H2 of the throat 430 is moderate, while avoiding an excessively long throat 430 that would cause the airflow to detach from the wall and form vortices, thereby reducing local energy loss and aerodynamic noise.

[0092] In some embodiments, such as Figure 15 As shown, along the exhaust direction of the airflow, the ratio between the height H2 of the throat 430 and the height H of the guide ring 400 is 0.24~0.26.

[0093] Specifically, the ratio of the throat height H2 (430mm) to the guide ring height H (400mm) is limited to 0.24~0.26. This design ensures that the throat height H2 (430mm) is moderate, providing sufficient height to guide airflow smoothly and reduce flow disturbance. It also prevents the throat from being too long, which could cause airflow to detach from the wall and form vortices, thus reducing local energy loss and aerodynamic noise. In summary, by optimizing the proportions of the throat (430mm), its guiding effect and overall aerodynamic performance are significantly improved.

[0094] In some embodiments, the vertical distance S between the side of the shroud frame 130 facing the air guide ring 400 and the side of the motor bracket 110 facing the air guide ring 400 is 376 mm.

[0095] In some embodiments, such as Figures 9-12 As shown, the axial flow fan 300 includes a hub 310 and a plurality of fan blades 320 arranged circumferentially along the hub 310. The fan blades 320 include blade tips 322 and blade apex 321.

[0096] Among them, blade tip 321 refers to the end of fan blade 320 that is radially away from hub 310, that is, the outermost edge of fan blade 320; blade tip 322 refers to the highest point of trailing edge of fan blade 320, that is, the highest point of fan blade 320 above the ground.

[0097] In some embodiments, such as Figure 8 As shown, the vertical distance S2 between the side of the air guide ring 400 near the motor bracket 110 and the blade tip 321 is 15 mm. Under the premise of avoiding structural interference between the two and ensuring that the airflow can smoothly enter along the inlet 420 of the air guide ring 400, the compatibility between the air guide ring 400 and the axial fan 300 is further improved, and the energy loss during the airflow process is reduced.

[0098] In some embodiments, such as Figure 8 As shown, the vertical distance S2 between the side of the air guide ring 400 near the motor bracket 110 and the blade tip 321 is 20 mm. Under the premise of avoiding structural interference between the two and ensuring that the airflow can smoothly enter along the inlet 420 of the air guide ring 400, the compatibility between the air guide ring 400 and the axial fan 300 is further improved, and the energy loss during the airflow process is reduced.

[0099] In some embodiments, such as Figure 8 As shown, the vertical distance S4 between the side of the air guide ring 400 near the motor bracket 110 and the motor bracket 110 is 90 mm. Under the premise of avoiding structural interference between the two and ensuring that the airflow can smoothly enter along the inlet 420 of the air guide ring 400, the compatibility between the air guide ring 400 and the axial fan 300 is further improved, and the energy loss during the airflow process is reduced.

[0100] In some embodiments, such as Figure 8 As shown, the vertical distance S4 between the side of the air guide ring 400 near the motor bracket 110 and the motor bracket 110 is 95 mm. Under the premise of avoiding structural interference between the two and ensuring that the airflow can smoothly enter along the inlet 420 of the air guide ring 400, the compatibility between the air guide ring 400 and the axial fan 300 is further improved, and the energy loss during the airflow process is reduced.

[0101] In some embodiments, such as Figure 8As shown, the vertical distance S2 between the side of the air guide ring 400 near the motor bracket 110 and the blade tip 321 is 15 mm to 20 mm; and / or, the vertical distance S4 between the side of the air guide ring 400 near the motor bracket 110 and the motor bracket 110 is 90 mm to 95 mm.

[0102] Specifically, this application limits the vertical distance S2 between the side of the air guide ring 400 near the motor bracket 110 and the blade tip 321 to 15mm~20mm, and simultaneously limits the vertical distance S4 between this side and the motor bracket 110 to 90mm~95mm. This design clarifies the relative positional relationship between the air guide ring 400, the tip of the fan blade 320, and the motor bracket 110. The reasonable spacing reduces airflow leakage and secondary flow losses between the blade tip 321 and the air guide ring 400, and also avoids structural interference, ensuring smooth airflow along the inlet 420 of the air guide ring 400. As a result, the compatibility between the air guide ring 400 and the axial fan 300 is further improved, energy loss during airflow is reduced, and operating noise is lowered. Simultaneously, under constant speed conditions, the airflow output is significantly increased, and the input power consumption is reduced, achieving an overall improvement in system efficiency.

[0103] In some embodiments, such as Figure 8 As shown, the vertical distance S3 between the side of the air guide ring 400 near the air cover frame 130 and the side of the air cover frame 130 near the air guide ring 400 is 48 mm. This design ensures that the airflow at the outlet of the air guide ring 400 can flow smoothly out of the outdoor unit, reducing the diffusion resistance of the airflow at the outlet, while avoiding airflow disturbance caused by unreasonable spacing between the blade tip 322 and the air guide ring 400, further improving the stability of airflow output and system efficiency.

[0104] In some embodiments, such as Figure 8 As shown, the vertical distance S3 between the side of the air guide ring 400 near the air cover frame 130 and the side of the air cover frame 130 near the air guide ring 400 is 53 mm. This design ensures that the airflow at the outlet of the air guide ring 400 can flow smoothly out of the outdoor unit, reducing the diffusion resistance of the airflow at the outlet, while avoiding airflow disturbance caused by unreasonable spacing between the blade tip 322 and the air guide ring 400, further improving the stability of airflow output and system efficiency.

[0105] In some embodiments, such as Figure 10 As shown, the vertical distance S1 between the air guide ring 400 and the blade tip 322 on the side close to the air cover frame 130 is 20 mm. This design ensures that the airflow at the outlet of the air guide ring 400 can flow smoothly out of the outdoor unit, reducing the diffusion resistance of the airflow at the outlet, while avoiding airflow disturbance caused by unreasonable spacing between the blade tip 322 and the air guide ring 400, further improving the stability of airflow output and system efficiency.

[0106] In some embodiments, such as Figure 10 As shown, the vertical distance S1 between the air guide ring 400 and the blade tip 322 on the side close to the fan cover frame 130 is 25 mm. This design ensures that the airflow at the outlet of the air guide ring 400 can flow smoothly out of the outdoor unit, reducing the diffusion resistance of the airflow at the outlet, while avoiding airflow disturbance caused by unreasonable spacing between the blade tip 322 and the air guide ring 400, further improving the stability of airflow output and system efficiency.

[0107] In some embodiments, such as Figure 8 , 10 As shown, the vertical distance S3 between the side of the air guide ring 400 near the air cover frame 130 and the side of the air cover frame 130 near the air guide ring 400 is 48 mm to 53 mm; and / or, the vertical distance S1 between the side of the air guide ring 400 near the air cover frame 130 and the blade tip 322 is 20 mm to 25 mm.

[0108] In the above embodiments, the vertical distance S3 between the side of the air guide ring 400 near the fan shroud frame 130 and the fan shroud frame 130 is 48 mm-53 mm, and the vertical distance S1 between the air guide ring 400 and the blade tip 322 is 20 mm-25 mm. This optimizes the relative position of the outlet of the air guide ring 400 with the fan shroud frame 130 and the top of the fan blade 320. This design ensures that the airflow at the outlet of the air guide ring 400 can flow smoothly out of the outdoor unit, reducing the diffusion resistance of the airflow at the outlet, while avoiding airflow disturbance caused by unreasonable spacing between the blade tip 322 and the air guide ring 400, further improving the stability of airflow output and system efficiency.

[0109] In some embodiments, such as Figure 10 As shown, the vertical distance S5 between the side of the wheel hub 310 closest to the drive motor 200 and the motor bracket 110 is 125 mm.

[0110] In some embodiments, such as Figure 10 As shown, the vertical distance S5 between the side of the wheel hub 310 closest to the drive motor 200 and the motor bracket 110 is 130 mm.

[0111] In some embodiments, such as Figure 10 As shown, the vertical distance S5 between the side of the wheel hub 310 closest to the drive motor 200 and the motor bracket 110 is 125 mm to 130 mm.

[0112] The vertical distance between the side of the hub 310 closest to the drive motor 200 and the motor bracket 110 is limited to 125mm~130mm. This design, by optimizing the axial positional relationship between the fan and the air guide ring 400, not only ensures the dynamic balance of the fan during rotation and reduces noise caused by vibration, but also ensures that the airflow continuously matches the profile of the air guide ring 400, maintaining smooth flow. This significantly improves the air volume output under constant speed conditions, while reducing input power consumption, achieving an overall improvement in system efficiency, and ultimately enhancing the operational stability and comprehensive performance of the outdoor unit of the air conditioner.

[0113] Significant technical results have been achieved through the implementation of the above technical solutions. For example... Figure 16 , 17 As shown, at a target airflow of 12300 m³ / h 3 At / h, compared to existing mass-produced air guide rings, the air guide ring 400 of this application reduces the power of the fan system by 36W, improves the efficiency of the fan system, reduces fan power consumption, and improves the overall energy efficiency of the system; at the same time, the aerodynamic noise of the fan system is reduced by 0.7dB(A), effectively reducing operating noise; in addition, by optimizing the profile of the air guide ring 400 and its relative position to the fan, smooth airflow guidance is achieved, reducing airflow separation and eddies, improving airflow distribution, enhancing the effective air delivery capacity of the fan, solving the problem of insufficient or unstable airflow output, and ensuring air conditioning performance.

[0114] Although embodiments of this application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting this application. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of this application.

Claims

1. An outdoor unit for an air conditioner, characterized in that, Includes a housing, and the housing contains: Axial fan; A drive motor, which is used to drive the axial fan to rotate; An air guide ring is fitted around the outer periphery of the axial flow fan; wherein the air guide ring includes: The assembly section has an air guide hole at its center; The inlet is connected to the outer edge of the air guide hole of the assembly part on one side; when projected onto the plane where the axis of the air guide ring is located, the projection of the inner wall of the inlet is an arc shape, the center of the arc formed by the projection of the inner wall of the inlet is located outside the air guide ring, and the central angle corresponding to the arc formed by the projection of the inner wall of the inlet is in the range of 75°~90°. The throat, one side of which is connected to the side of the inlet portion away from the assembly portion; The outlet section has one side connected to the throat section away from the inlet section; when projected onto the plane containing the axis of the air guide ring, the projection of the inner wall of the outlet section is an arc shape, the center of the arc formed by the projection of the inner wall of the outlet section is located outside the air guide ring, and the central angle corresponding to the arc formed by the projection of the inner wall of the outlet section is in the range of 21°~27°. Specifically, when projecting onto the plane containing the axis of the air guide ring, the ratio between the radius of the arc formed by the projection of the inner wall of the outlet and the radius of the arc formed by the projection of the inner wall of the inlet is 1.6 to 2; the ratio between the radius of the arc formed by the projection of the inner wall of the outlet and the radius of the inner wall of the outlet on the side away from the throat is 0.16 to 0.

17.

2. An outdoor unit for an air conditioner according to claim 1, characterized in that, The housing is connected to a fan shroud frame via a positioning post. The fan shroud frame is located on one side of the airflow discharge direction of the axial fan, and an air outlet shroud is provided inside the fan shroud frame. The drive motor is mounted inside the housing via a motor bracket, which is located on the side of the axial fan away from the fan cover frame.

3. An outdoor unit for an air conditioner according to claim 2, characterized in that, A notch is provided at each apex corner of the assembly part, and the positioning post passes through the notch.

4. An outdoor unit for an air conditioner according to claim 3, characterized in that, The ratio between the minimum diameter of the inner wall of the throat and the diameter of the axial fan is 1.03 to 1.

04.

5. An outdoor unit for an air conditioner according to claim 4, characterized in that, The ratio between the height of the throat and the height of the air guide ring is 0.24 to 0.

26.

6. An outdoor unit for an air conditioner according to any one of claims 2 to 5, characterized in that, The axial flow fan includes a hub and a plurality of fan blades arranged circumferentially along the hub, the fan blades including blade tips and blade apexes; The vertical distance between the side of the air guide ring closest to the motor bracket and the blade tip is 15mm to 20mm.

7. An outdoor unit for an air conditioner according to claim 6, characterized in that, The vertical distance between the side of the air guide ring closest to the motor bracket and the motor bracket is 90mm~95mm.

8. An outdoor unit for an air conditioner according to claim 6, characterized in that, The vertical distance between the side of the air guide ring near the air cover frame and the side of the air cover frame near the air guide ring is 48mm-53mm.

9. An outdoor unit for an air conditioner according to claim 6, characterized in that, The vertical distance between the air guide ring on the side near the wind shield frame and the blade tip is 20mm~25mm.

10. An outdoor unit for an air conditioner according to claim 6, characterized in that, The vertical distance between the side of the wheel hub closest to the drive motor and the motor bracket is 125mm to 130mm.

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