Centrifugal cross-flow integrated fan blade and cabinet air conditioner with fresh air function

Abstract

The utility model relates to the technical field of air conditioning equipment, in particular to a centrifugal cross-flow integrated fan blade and a cabinet air conditioner with a fresh air function. According to the technical scheme, the centrifugal and cross-flow integrated fan blade comprises a centrifugal fan blade, and a steel shaft is arranged in the center of the centrifugal fan blade; the cross-flow fan blade comprises a motor shaft disc and a plurality of middle section discs, and the motor shaft disc, the plurality of middle section discs and the centrifugal fan blade are sequentially in axial butt joint and are welded to form an integrated structure; and the single-motor driving device is used for driving the integrated structure to operate. The scheme has the advantages that the structure is simplified, energy is saved, consumption is reduced, and air supply efficiency is improved.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning equipment technology, and in particular to an integrated centrifugal cross-flow fan blade and an air conditioning cabinet unit with fresh air function. Background Technology

[0002] With the increasing demands for air quality in modern building environments, fresh air conditioning systems are playing an increasingly important role in regulating indoor temperature and humidity and achieving efficient ventilation. Traditional fresh air conditioning systems generally employ an independent configuration of centrifugal and cross-flow fan blades: the centrifugal fan blades are responsible for generating high-pressure airflow to achieve long-distance air delivery, while the cross-flow fan blades are used to create a uniform airflow field and reduce noise.

[0003] However, there are significant drawbacks in the existing technology:

[0004] Redundancy in multi-motor drive structures: Conventional designs require separate motors and transmission devices for centrifugal and cross-flow fan blades, leading to increased equipment size and higher installation space requirements. Statistics show that dual-motor systems occupy more than 40% more space than single-motor solutions, severely hindering the development of miniaturized and embedded devices. This structure not only increases the complexity of the equipment but also limits its application in confined spaces or special environments.

[0005] Energy consumption and cost are compounded: the independent drive mode significantly increases the overall power consumption of the machine, while also requiring additional motor control modules and cooling structures. Experimental data shows that the energy consumption of the dual-motor system is 25%-30% higher than the theoretical optimal value, and the motor procurement cost accounts for more than 18% of the total material cost of the machine. This not only increases the initial investment cost of the equipment but also leads to increased energy consumption during long-term operation, which is inconsistent with the current trend of energy conservation and environmental protection.

[0006] Insufficient coordination efficiency: Split-type fan blades are prone to airflow turbulence due to speed mismatch, affecting the stability of air delivery efficiency. Industry case studies show that the actual air volume utilization rate of traditional structures is only 75%-82% of the design value, and performance degradation is exacerbated by differences in motor wear after long-term operation. This efficiency loss not only reduces the overall performance of the equipment, but may also lead to indoor air quality failing to meet expected standards, affecting the user experience.

[0007] Furthermore, existing dual-blade systems also face challenges in maintenance and upkeep. Since two independent blade systems require separate maintenance, the complexity and frequency of maintenance work increase, thereby raising the total life-cycle cost of the equipment. At the same time, vibration and noise issues are more pronounced in dual-system systems, potentially affecting equipment lifespan and user comfort.

[0008] To address the aforementioned issues, existing technologies urgently need improvement. Summary of the Invention

[0009] To address the aforementioned issues, the present invention aims to provide an integrated centrifugal cross-flow fan and an air conditioning unit with a fresh air function, which has the advantages of simplified structure, energy saving and consumption reduction, and improved air delivery efficiency.

[0010] To achieve the above objectives, the present invention adopts the following technical solution:

[0011] A centrifugal cross-flow integrated fan blade, the technical solution of which is as follows: comprising: a centrifugal fan blade with a steel shaft at its center; a cross-flow fan blade including a motor shaft disk and multiple intermediate disks, wherein the motor shaft disk and the multiple intermediate disks are sequentially axially connected to the centrifugal fan blade and are welded to form an integrated structure; and a single motor drive device for driving the integrated structure to operate.

[0012] Furthermore, this application also proposes that the centrifugal fan blade includes: a hub; a centrifugal blade assembly arranged circumferentially along the outer edge of the hub on one side of the hub; and a wind ring connected to the outer edge of the centrifugal blade assembly; wherein the centrifugal blade assembly and the hub form a wind cavity, an air outlet is formed between two adjacent centrifugal blades, and an air inlet is formed inside the wind ring.

[0013] Furthermore, this application also proposes that the center of the hub arches towards the air inlet to form a truncated cone, and the steel shaft is located at the center of the truncated cone.

[0014] Furthermore, this application also proposes that the top surface of the frustum is a plane.

[0015] Furthermore, this application also proposes that the steel shaft and the rubber bushing assembly at the center of the motor shaft disk are concentrically arranged.

[0016] Furthermore, this application also proposes that the motor shaft disk includes a wheel disk and a rubber bushing assembly, the rubber bushing assembly being embedded and fixed in a through hole in the middle of the wheel disk, and the rubber bushing assembly having a shaft hole for connecting the motor shaft.

[0017] Furthermore, this application also proposes that the centrifugal fan blades, motor shaft discs, and multiple intermediate discs have the same outer diameter.

[0018] Furthermore, this application also proposes an air conditioning unit with a fresh air function, comprising: a cabinet; the aforementioned centrifugal cross-flow integrated fan blade; wherein the cross-flow fan blade is aligned with the air conditioning outlet on the cabinet, and the centrifugal fan blade is aligned with the fresh air outlet on the cabinet.

[0019] As can be seen from the above, the centrifugal and cross-flow integrated fan blade and air conditioning cabinet unit with fresh air function provided in this application include a centrifugal fan blade, a cross-flow fan blade and a single motor drive device. By integrating the centrifugal fan blade and the cross-flow fan blade into a single design and using a single motor drive, the problems of redundant multi-motor drive structure, superposition of energy consumption and cost and insufficient collaborative efficiency in traditional fresh air conditioning systems are effectively solved. It has the advantages of simplified structure, energy saving and consumption reduction and improved air supply efficiency. Attached Figure Description

[0020] Figure 1 A side view of the centrifugal cross-flow integrated fan blade provided in this application.

[0021] Figure 2 This is a cross-sectional schematic diagram of the centrifugal cross-flow integrated fan blade provided in this application. Detailed Implementation

[0022] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this utility model, and should not be construed as limiting this utility model.

[0023] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model 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. Therefore, they should not be construed as limitations on this utility model.

[0024] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more, unless otherwise expressly defined.

[0025] In this utility model, unless otherwise explicitly 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 connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0026] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0027] Example 1:

[0028] like Figure 1 and 2 As shown, this embodiment relates to an integrated centrifugal and cross-flow fan blade, including a centrifugal fan blade 1, a cross-flow fan blade 2, and a single-motor drive device. A steel shaft 11 is located at the center of the centrifugal fan blade 1; the cross-flow fan blade 2 includes a motor shaft disc 21 and multiple intermediate discs 22, which are sequentially axially connected to the centrifugal fan blade 1 and welded together to form an integrated structure; the single-motor drive device is used to drive the integrated structure. This technical solution welds the centrifugal fan blade 1 and the cross-flow fan blade 2 into an integral structure, with a single motor synchronously driving both sets of fan blades. The steel shaft 11 of the centrifugal fan blade 1 provides rotational support and positioning, while the motor shaft disc 21 of the cross-flow fan blade 2 is directly connected to the output shaft of the drive motor. This integrated design eliminates the additional motor and transmission components required for a split structure, reducing the overall axial dimension by more than 30%. Because the two sets of fan blades are rigidly connected, their speeds are completely synchronized, avoiding the speed matching deviation problem present in traditional split drives. Simultaneously, the single-motor configuration reduces system power consumption by approximately 25% and reduces the number of motor control modules. This structure is particularly suitable for fresh air conditioning equipment with limited space, achieving structural simplification and energy efficiency improvement while ensuring air pressure and air volume output.

[0029] In a specific implementation, the centrifugal fan 1 includes a hub 12; a centrifugal blade assembly 13 arranged circumferentially along the outer edge of the hub 12 on one side of the hub 12; and a fan ring 14 connected to the outer edge of the centrifugal blade assembly 13. The centrifugal blade assembly 13 and the hub 12 form a wind cavity 15, an air outlet 16 is formed between two adjacent centrifugal blades, and an air inlet 17 is formed within the fan ring 14. The hub 12 can be injection molded from engineering plastic, and the fit tolerance between its outer diameter and the inner edge of the centrifugal blade assembly 13 is controlled within ±0.1mm. The centrifugal blade assembly 13 preferably has 9-15 blades, with a backward-curved aerodynamic design and a blade installation angle ranging from 30° to 45°. The fan ring 14 can adopt a segmented arc-shaped plate splicing structure, with its inner diameter and the radial clearance between the outer edge of the centrifugal blade assembly 13 maintained within the range of 1-3mm. The axial depth of the air cavity 15 can be varied from 5 to 20 mm by adjusting the flange height of the hub 12, and the ratio of the volume of the air cavity 15 to the area of ​​the air inlet 17 is controlled between 1.2 and 1.8. This technical solution uses the hub 12 to provide a rigid support foundation, the centrifugal blade assembly 13 to form an array of flow channels with equal angles, and the air ring 14 to construct an annular constraint boundary. During operation, the airflow enters the air cavity 15 from the axial air inlet 17, is accelerated radially along the blade flow channel by the rotational centrifugal force, and is finally discharged from the air outlet 16 between the blades. The frustum structure of the hub 12 guides the airflow to smoothly transition to the air cavity 15, and the tight fit between the air ring 14 and the outer edge of the blades effectively suppresses the generation of vortices. Compared with conventional centrifugal fan blades, this structure avoids airflow short-circuiting through the spatial isolation design between the air inlet 17 and the air outlet 16.

[0030] Furthermore, the center of the hub 12 arches towards the air inlet 17 to form a truncated cone 18, with the steel shaft 11 positioned at the center of the truncated cone 18. The arch angle of the truncated cone 18 can be adjusted within the range of 30° to 60°, with the specific angle determined based on airflow velocity and pressure requirements. The ratio of the height of the truncated cone 18 to the diameter of the hub 12 is preferably 1:5 to 1:3 to ensure a balance between structural strength and airflow guidance. The connection between the steel shaft 11 and the truncated cone 18 can be achieved through interference fit, welding, or integral injection molding. Guide grooves can be provided on the surface of the truncated cone 18 to refine airflow distribution. As a preferred embodiment, the top surface of the truncated cone 18 is machined with a positioning groove, the diameter of which is 0.05-0.1 mm larger than the diameter of the steel shaft 11, facilitating quick alignment during assembly. This technical solution achieves a dual technical effect through the conical structure of the frustum 18: geometrically, the central symmetry of the frustum 18 provides a stable axial positioning reference for the steel shaft 11, keeping the radial runout within 0.1mm; in terms of fluid dynamics, the inclined surface of the frustum 18 reduces the inlet airflow angle by 15°-25°, effectively reducing the intensity of eddies.

[0031] Furthermore, this application proposes that the top surface of the frustum 18 be a plane. This technical solution, by defining the top surface of the frustum 18 as a plane, provides a stable mechanical reference surface for the installation of the steel shaft 11. The planar structure maximizes the contact area when the steel shaft 11 is installed vertically, avoiding the problem of local stress concentration caused by curved surface contact. During processing, the planar reference surface makes it easier to ensure the positioning accuracy of the mounting holes of the steel shaft 11, controlling the coaxiality error between the hole axis and the center line of the frustum 18 within ±0.01mm. Compared to a curved top surface design, the planar structure makes the force transmission path of the steel shaft 11 more direct, effectively reducing the vibration risk caused by uneven contact during high-speed rotation. At the same time, the planar top surface simplifies the processing requirements while maintaining the overall aerodynamic shape of the hub 12, eliminating the need for additional curved surface positioning fixtures.

[0032] like Figure 2 As shown, the steel shaft 11 and the rubber bushing assembly 211 at the center of the motor shaft disk 21 are concentrically arranged. The rubber bushing assembly 211 can be formed by vulcanization molding, where the rubber layer and the metal bushing are bonded together. The hardness range of the rubber layer is preferably Shore A 50-70 degrees, and the fit tolerance between the inner diameter of the metal bushing and the outer diameter of the steel shaft 11 is controlled at H7 / g6 grade. As a preferred embodiment, the rubber bushing assembly 211 can be designed as a multi-layer composite structure, including an inner wear-resistant nylon bushing, a middle silicone rubber buffer layer, and an outer metal retaining ring. Specifically, the axial length of the rubber bushing assembly 211 should not be less than 1.2 times the diameter of the steel shaft 11 to ensure sufficient radial deformation compensation capacity. This technical solution achieves dynamic self-adjustment function during power transmission through the axial concentric fit between the rigid steel shaft 11 and the elastic rubber bushing 211. When driven by the motor, the shear deformation characteristics of the rubber material can absorb the radial offset of the steel shaft 11 caused by machining tolerances or thermal deformation (typical compensation can reach ±0.15mm), while maintaining the linearity of torque transmission. Compared with existing rigid couplings, the damping characteristics of the rubber bushing 211 can also effectively suppress high-frequency resonance and extend the service life of the bearing.

[0033] like Figure 2As shown, this application also proposes a motor shaft disk 21 comprising a disk 212 and a rubber bushing assembly 211. The rubber bushing assembly 211 is embedded and fixed in a through hole in the middle of the disk 212, and the rubber bushing assembly 211 has a shaft hole 213 for connecting the motor shaft. The rubber bushing assembly 211 can be injection molded together with the disk 212 using a vulcanization process, wherein the rubber material is preferably nitrile rubber or silicone rubber, and the hardness range is controlled within 50-70 Shore A. The inner wall of the shaft hole 213 can be provided with axial anti-slip textures or circumferential grooves to enhance the coefficient of friction with the motor shaft. This technical solution, through the composite design of elastic materials and rigid structures, effectively absorbs high-frequency vibrations during motor operation while ensuring power transmission accuracy. Specifically, the elastic deformation of the rubber bushing assembly 211 can isolate the vibration transmission path between the motor shaft and the disk 212, while the rigid support provided by the disk 212 ensures the stability of torque transmission. Compared to traditional direct welding of metal bushings, this structure reduces axial vibration amplitude by approximately 60% and eliminates the need for additional vibration dampers, simplifying the assembly process. Experimental data shows that at 3000 rpm, the noise level using this structure can be reduced by 8-12 dB, and bearing life can be extended by more than 30%.

[0034] Furthermore, the outer diameters of the motor shaft disk 21 and the multiple intermediate disks 22 of the cross-flow fan blade 2 should be consistent, but the centrifugal fan blade 1 only needs to be concentric with the cross-flow fan blade 2, and its outer diameter can be larger or smaller than that of the cross-flow fan blade 2. However, in a preferred embodiment, the outer diameters of the centrifugal fan blade 1, the motor shaft disk 21, and the multiple intermediate disks 22 are the same. Specifically, the same outer diameter refers to the outer diameter of the blades of the centrifugal fan blade 1, the motor shaft disk 21, and the multiple intermediate disks 22. As a preferred embodiment, the outer diameter tolerance is controlled within ±0.5mm to ensure radial alignment accuracy during assembly. For example, a CNC lathe can be used to machine the outer edge of the hub 12 of the centrifugal fan blade 1, the outer periphery of the disk 212 of the motor shaft disk 21, and the annular end face of the intermediate disk 22 to the same specifications. Furthermore, achieving the same outer diameter also includes ensuring that the inner diameter of the centrifugal fan blade 1's ring 14 is consistent with the inner diameter of the middle section plate 22, and that the coaxiality error between the mounting hole of the rubber bushing assembly 211 of the motor shaft plate 21 and the center hole of each plate does not exceed 0.1mm. Thus, during axial welding assembly, the outer contours of each component can form a continuous cylindrical surface. By designing the centrifugal fan blade 1, motor shaft plate 21, and middle section plate 22 with the same outer diameter, the radial dimension of the airflow channel remains constant, avoiding distortion of the flow velocity distribution caused by abrupt changes in cross-section. Specifically, in the cross-flow fan blade section 2, the airflow is not disturbed by changes in radial dimension when flowing axially, thus effectively suppressing the generation of vortices. Simultaneously, the uniform outer diameter specification allows the use of the same fixture positioning reference during machining of each component, reducing process changeover time. In the assembly stage, since there is no radial misalignment, only axial alignment accuracy needs to be ensured during welding to achieve the coaxiality requirement of the overall structure. This technical solution, through standardized design of geometric parameters, significantly improves production efficiency and assembly reliability while ensuring airflow stability.

[0035] Example 2:

[0036] This embodiment relates to an air conditioning unit with a fresh air function, including a cabinet and a centrifugal cross-flow integrated fan blade. The centrifugal cross-flow integrated fan blade includes a centrifugal fan blade 1, a cross-flow fan blade 2, and a single motor drive device. A steel shaft 11 is set at the center of the centrifugal fan blade 1. The cross-flow fan blade 2 includes a motor shaft disc 21 and multiple intermediate discs 22. The motor shaft disc 21 and the multiple intermediate discs 22 are sequentially axially connected to the centrifugal fan blade 1 and welded to form an integrated structure. The cross-flow fan blade 2 is aligned with the air conditioning outlet on the cabinet, and the centrifugal fan blade 1 is aligned with the fresh air outlet on the cabinet. This technical solution integrates the centrifugal cross-flow integrated fan blade into the air conditioning unit, with the cabinet serving as the basic structure of the equipment, providing installation space and airflow channels. The centrifugal cross-flow integrated fan blade adopts a single-motor driven integrated structure. The axially welded centrifugal fan blade 1 and cross-flow fan blade 2 operate synchronously, eliminating the space occupation and energy consumption problems of traditional dual-motor systems. Cross-flow fan 2 is aligned with the air conditioning outlet to provide regular air supply, while centrifugal fan 1 is aligned with the fresh air outlet to deliver high-pressure fresh air. Both are mechanically connected to ensure synchronized rotation speeds and prevent airflow turbulence. This integrated structure eliminates the need for dual motors, reducing space requirements and energy consumption. The layout of cross-flow fan 2 aligned with the air conditioning outlet and centrifugal fan 1 aligned with the fresh air outlet ensures precise allocation of the two airflow paths. Optimized design of the air chamber 15 and air outlet 16 improves airflow utilization. Compared to traditional fresh air conditioning systems, this solution reduces structural redundancy, improves coordination efficiency, and lowers energy consumption.

[0037] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. 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.

[0038] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention without departing from the principles and spirit of the present invention.

Claims

1. A centrifugal through-flow integrated fan blade, characterized in that, The application relates to a centrifugal-penetration integrated fan blade. The centrifugal fan blade (1) comprises: - a hub (12); - a centrifugal blade group (13) arranged on one side of the hub (12) along the outer edge of the hub (12); 2. The centrifugal cross-flow integrated blade of claim 1, wherein, - a wind ring (14) connected to the outer edge of the centrifugal blade group (13); wherein the centrifugal blade group (13) and the hub (12) form a wind cavity (15), and an air outlet (16) is formed between two adjacent centrifugal blades, and an air inlet (17) is formed in the wind ring (14). The hub (12) is arched to form a circular table (18) towards the air inlet (17), and the steel shaft (11) is arranged at the center of the circular table (18). The top surface of the circular table (18) is a plane. The steel shaft (11) is arranged concentrically with a rubber shaft sleeve assembly (211) at the center of the motor shaft disc (21).

3. The centrifugal cross-flow integrated blade of claim 2, wherein, The motor shaft disc (21) comprises a disc (212) and the rubber shaft sleeve assembly (211), the rubber shaft sleeve assembly (211) is embedded and fixed in the through hole in the middle of the disc (212), and a shaft hole (213) for connecting a motor shaft is arranged in the rubber shaft sleeve assembly (211).

4. The centrifugal cross-flow integrated blade of claim 3, wherein, The outer diameters of the centrifugal fan blade (1), the motor shaft disc (21) and the plurality of middle section discs (22) are the same.

5. The centrifugal cross-flow integrated blade of claim 4, wherein, The application further relates to a cabinet air conditioner.

6. The centrifugal cross-flow integrated blade of claim 1, wherein, The penetration fan blade (2) is aligned with an air outlet of the cabinet air conditioner, and the centrifugal fan blade (1) is aligned with a fresh air outlet of the cabinet air conditioner.

7. The centrifugal cross-flow integrated impeller blade according to any one of claims 1 to 6, characterized in that, ​ 8. An air conditioner cabinet machine with fresh air function, characterized in that, ​ ​ ​ ​

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